Collapse to view only § 430.24 - [Reserved]

§ 430.21 - Purpose and scope.

This subpart contains test procedures required to be prescribed by DOE pursuant to section 323 of the Act.

§ 430.23 - Test procedures for the measurement of energy and water consumption.

When the test procedures of this section call for rounding off of test results, and the results fall equally between two values of the nearest dollar, kilowatt-hour, or other specified nearest value, the result shall be rounded up to the nearest higher value.

(a) Refrigerators and refrigerator-freezers. (1) The estimated annual operating cost for models without an anti-sweat heater switch shall be the product of the following three factors, with the resulting product then being rounded to the nearest dollar per year:

(i) The representative average-use cycle of 365 cycles per year;

(ii) The average per-cycle energy consumption for the standard cycle in kilowatt-hours per cycle, determined according to appendix A of this subpart; and

(iii) The representative average unit cost of electricity in dollars per kilowatt-hour as provided by the Secretary.

(2) The estimated annual operating cost for models with an anti-sweat heater switch shall be the product of the following three factors, with the resulting product then being rounded to the nearest dollar per year:

(i) The representative average-use cycle of 365 cycles per year;

(ii) Half the sum of the average per-cycle energy consumption for the standard cycle and the average per-cycle energy consumption for a test cycle type with the anti-sweat heater switch in the position set at the factory just before shipping, each in kilowatt-hours per cycle, determined according to appendix A of this subpart; and

(iii) The representative average unit cost of electricity in dollars per kilowatt-hour as provided by the Secretary.

(3) The estimated annual operating cost for any other specified cycle type shall be the product of the following three factors, the resulting product then being rounded to the nearest dollar per year:

(i) The representative average-use cycle of 365 cycles per year;

(ii) The average per-cycle energy consumption for the specified cycle type, determined according to appendix A of this subpart; and

(iii) The representative average unit cost of electricity in dollars per kilowatt-hour as provided by the Secretary.

(4) The energy factor, expressed in cubic feet per kilowatt-hour per cycle, shall be:

(i) For models without an anti-sweat heater switch, the quotient of:

(A) The adjusted total volume in cubic feet, determined according to appendix A of this subpart, divided by—

(B) The average per-cycle energy consumption for the standard cycle in kilowatt-hours per cycle, determined according to appendix A of this subpart, the resulting quotient then being rounded to the second decimal place; and

(ii) For models having an anti-sweat heater switch, the quotient of:

(A) The adjusted total volume in cubic feet, determined according to appendix A of this subpart, divided by—

(B) Half the sum of the average per-cycle energy consumption for the standard cycle and the average per-cycle energy consumption for a test cycle type with the anti-sweat heater switch in the position set at the factory just before shipping, each in kilowatt-hours per cycle, determined according to appendix A of this subpart, the resulting quotient then being rounded to the second decimal place.

(5) The annual energy use, expressed in kilowatt-hours per year and rounded to the nearest kilowatt-hour per year, shall be determined according to appendix A of this subpart.

(6) Other useful measures of energy consumption shall be those measures of energy consumption that the Secretary determines are likely to assist consumers in making purchasing decisions which are derived from the application of appendix A of this subpart.

(7) The following principles of interpretation shall be applied to the test procedure. The intent of the energy test procedure is to simulate typical room conditions (72 °F (22.2 °C)) with door openings, by testing at 90 °F (32.2 °C) without door openings. Except for operating characteristics that are affected by ambient temperature (for example, compressor percent run time), the unit, when tested under this test procedure, shall operate in a manner equivalent to the unit's operation while in typical room conditions.

(i) The energy used by the unit shall be calculated when a calculation is provided by the test procedure. Energy consuming components that operate in typical room conditions (including as a result of door openings, or a function of humidity), and that are not excluded by this test procedure, shall operate in an equivalent manner during energy testing under this test procedure, or be accounted for by all calculations as provided for in the test procedure. Examples:

(A) Energy saving features that are designed to operate when there are no door openings for long periods of time shall not be functional during the energy test.

(B) The defrost heater shall neither function nor turn off differently during the energy test than it would when in typical room conditions. Also, the product shall not recover differently during the defrost recovery period than it would in typical room conditions.

(C) Electric heaters that would normally operate at typical room conditions with door openings shall also operate during the energy test.

(D) Energy used during adaptive defrost shall continue to be measured and adjusted per the calculation provided in this test procedure.

(ii) DOE recognizes that there may be situations that the test procedures do not completely address. In such cases, a manufacturer must obtain a waiver in accordance with the relevant provisions of 10 CFR part 430 if:

(A) A product contains energy consuming components that operate differently during the prescribed testing than they would during representative average consumer use; and

(B) Applying the prescribed test to that product would evaluate it in a manner that is unrepresentative of its true energy consumption (thereby providing materially inaccurate comparative data).

(b) Freezers. (1) The estimated annual operating cost for freezers without an anti-sweat heater switch shall be the product of the following three factors, with the resulting product then being rounded to the nearest dollar per year:

(i) The representative average-use cycle of 365 cycles per year;

(ii) The average per-cycle energy consumption for the standard cycle in kilowatt-hours per cycle, determined according to appendix B of this subpart; and

(iii) The representative average unit cost of electricity in dollars per kilowatt-hour as provided by the Secretary.

(2) The estimated annual operating cost for freezers with an anti-sweat heater switch shall be the product of the following three factors, with the resulting product then being rounded to the nearest dollar per year:

(i) The representative average-use cycle of 365 cycles per year;

(ii) Half the sum of the average per-cycle energy consumption for the standard cycle and the average per-cycle energy consumption for a test cycle type with the anti-sweat heater switch in the position set at the factory just before shipping, each in kilowatt-hours per cycle, determined according to appendix B of this subpart; and

(iii) The representative average unit cost of electricity in dollars per kilowatt-hour as provided by the Secretary.

(3) The estimated annual operating cost for any other specified cycle type for freezers shall be the product of the following three factors, with the resulting product then being rounded to the nearest dollar per year:

(i) The representative average-use cycle of 365 cycles per year;

(ii) The average per-cycle energy consumption for the specified cycle type, determined according to appendix B of this subpart; and

(iii) The representative average unit cost of electricity in dollars per kilowatt-hour as provided by the Secretary.

(4) The energy factor, expressed in cubic feet per kilowatt-hour per cycle, shall be:

(i) For models without an anti-sweat heater switch, the quotient of:

(A) The adjusted total volume in cubic feet, determined according to appendix B of this subpart, divided by—

(B) The average per-cycle energy consumption for the standard cycle in kilowatt-hours per cycle, determined according to appendix B of this subpart, the resulting quotient then being rounded to the second decimal place; and

(ii) For models having an anti-sweat heater switch, the quotient of:

(A) The adjusted total volume in cubic feet, determined according to appendix B of this subpart, divided by—

(B) Half the sum of the average per-cycle energy consumption for the standard cycle and the average per-cycle energy consumption for a test cycle type with the anti-sweat heater switch in the position set at the factory just before shipping, each in kilowatt-hours per cycle, determined according to appendix B of this subpart, the resulting quotient then being rounded to the second decimal place.

(5) The annual energy use, expressed in kilowatt-hours per year and rounded to the nearest kilowatt-hour per year, shall be determined according to appendix B of this subpart.

(6) Other useful measures of energy consumption for freezers shall be those measures the Secretary determines are likely to assist consumers in making purchasing decisions and are derived from the application of appendix B of this subpart.

(7) The following principles of interpretation shall be applied to the test procedure. The intent of the energy test procedure is to simulate typical room conditions (72 °F (22.2 °C)) with door openings by testing at 90 °F (32.2 °C) without door openings. Except for operating characteristics that are affected by ambient temperature (for example, compressor percent run time), the unit, when tested under this test procedure, shall operate in a manner equivalent to the unit's operation while in typical room conditions.

(i) The energy used by the unit shall be calculated when a calculation is provided by the test procedure. Energy consuming components that operate in typical room conditions (including as a result of door openings, or a function of humidity), and that are not excluded by this test procedure, shall operate in an equivalent manner during energy testing under this test procedure, or be accounted for by all calculations as provided for in the test procedure. Examples:

(A) Energy saving features that are designed to operate when there are no door openings for long periods of time shall not be functional during the energy test.

(B) The defrost heater shall neither function nor turn off differently during the energy test than it would when in typical room conditions. Also, the product shall not recover differently during the defrost recovery period than it would in typical room conditions.

(C) Electric heaters that would normally operate at typical room conditions with door openings shall also operate during the energy test.

(D) Energy used during adaptive defrost shall continue to be measured and adjusted per the calculation provided for in this test procedure.

(ii) DOE recognizes that there may be situations that the test procedures do not completely address. In such cases, a manufacturer must obtain a waiver in accordance with the relevant provisions of this part if:

(A) A product contains energy consuming components that operate differently during the prescribed testing than they would during representative average consumer use; and

(B) Applying the prescribed test to that product would evaluate it in a manner that is unrepresentative of its true energy consumption (thereby providing materially inaccurate comparative data).

(c) Dishwashers. (1) The Estimated Annual Operating Cost (EAOC) for dishwashers must be rounded to the nearest dollar per year and is defined as follows:

(i) When cold water (50 °F) is used,

EAOC = (De × ETLP) + (De × N × (M + MWS + MDO + MCO + EF−(ED/2))). Where, De = the representative average unit cost of electrical energy, in dollars per kilowatt-hour, as provided by the Secretary, ETLP = the annual combined low-power mode energy consumption in kilowatt-hours per year and determined according to section 5 of appendix C1 or appendix C2 to this subpart, as applicable, N = the representative average dishwasher use of 215 cycles per year when EAOC is determined pursuant to appendix C1 to this subpart, and 184 cycles per year when EAOC is determined pursuant to appendix C2 to this subpart, M = the machine energy consumption per cycle, in kilowatt-hours and determined according to section 5 of appendix C1 or appendix C2 to this subpart, as applicable, MWS = the machine energy consumption per cycle for water softener regeneration, in kilowatt-hours and determined pursuant to section 5 of appendix C1 or appendix C2 to this subpart, as applicable, MDO = for water re-use system dishwashers, the machine energy consumption per cycle during a drain out event in kilowatt-hours and determined according to section 5 of appendix C1 or appendix C2 to this subpart, as applicable, MCO = for water re-use system dishwashers, the machine energy consumption per cycle during a clean out event, in kilowatt-hours and determined according to section 5 of appendix C1 or appendix C2 to this subpart, as applicable, EF = the fan-only mode energy consumption per cycle, in kilowatt-hours and determined according to section 5 of appendix C1 or appendix C2 to this subpart, as applicable, and ED = the drying energy consumption, in kilowatt-hours and determined according to section 5 of appendix C1 or appendix C2 to this subpart, as applicable.

(ii) When electrically heated water (120 °F or 140 °F) is used,

EAOC = (De × ETLP) + (De × N × (M + MWS + MDO + MCO + EF−(ED/2))) + (De × N × (W + WWS + WDO + WCO)). Where, De, ETLP, N, M, MWS, MDO, MCO, EF, and ED, are defined in paragraph (c)(1)(i) of this section, W = the water energy consumption per cycle, in kilowatt-hours and determined according to section 5 of appendix C1 or appendix C2 to this subpart, as applicable, WWS = the water softener regeneration water energy consumption per cycle in kilowatt-hours and determined according to section 5 of appendix C1 or appendix C2 to this subpart, as applicable, WDO = The drain out event water energy consumption per cycle in kilowatt-hours and determined according to section 5 of appendix C1 or appendix C2 to this subpart, as applicable, and WCO = The clean out event water energy consumption per cycle in kilowatt-hours and determined according to section 5 of appendix C1 or appendix C2 to this subpart, as applicable.

(iii) When gas-heated or oil-heated water is used,

EAOCg = (De × ETLP) + (De × N × (M + MWS + MDO + MCO + EF−(ED/2))) + (Dg × N × (Wg + WWSg + WDOg + WCOg)). Where, De, ETLP, N, M, MWS, MDO, MCO, EF, and ED, are defined in paragraph (c)(1)(i) of this section, Dg = the representative average unit cost of gas or oil, as appropriate, in dollars per BTU, as provided by the Secretary, Wg = the water energy consumption per cycle, in Btus and determined according to section 5 of appendix C1 or appendix C2 to this subpart, as applicable. WWSg = the water softener regeneration energy consumption per cycle in Btu per cycle and determined according to section 5 of appendix C1 or appendix C2 to this subpart, as applicable, WDOg = the drain out water energy consumption per cycle in kilowatt-hours and determined according to section 5 of appendix C1 or appendix C2 to this subpart, as applicable, and WCOg = the clean out water energy consumption per cycle in kilowatt-hours and determined according to section 5 of appendix C1 or appendix C2 to this subpart, as applicable.

(2) The estimated annual energy use, EAEU, expressed in kilowatt-hours per year must be rounded to the nearest kilowatt-hour per year and is defined as follows:

EAEU = (M + MWS + MDO + MCO + EF−(ED/2) + W + WWS + WDO + WCO) × N + ETLP Where, M, MWS, MDO, MCO, EF, ED, ETLP are all defined in paragraph (c)(1)(i) of this section and W, WWS, WDO, WCO are defined in paragraph (c)(1)(ii) of this section.

(3) The sum of the water consumption, V, the water consumption during water softener regeneration, VWS, the water consumption during drain out events for dishwashers equipped with a water re-use system, VDO, and the water consumption during clean out events for dishwashers equipped with a water re-use system, VCO, expressed in gallons per cycle and defined pursuant to section 5 of appendix C1 or appendix C2 to this subpart, as applicable, must be rounded to one decimal place.

(4) Other useful measures of energy consumption for dishwashers are those which the Secretary determines are likely to assist consumers in making purchasing decisions and which are derived from the application of appendix C1 to this subpart or appendix C2 to this subpart, as applicable.

(d) Clothes dryers. (1) The estimated annual energy consumption for clothes dryers, expressed in kilowatt-hours per year, shall be the product of the annual representative average number of clothes dryer cycles as specified in appendix D1 or D2 to this subpart, as appropriate, and the per-cycle combined total energy consumption in kilowatt-hours per cycle, determined according to section 4.6 of appendix D1 or section 4.6 of appendix D2 to this subpart, as appropriate.

(2) The estimated annual operating cost for clothes dryers shall be—

(i) For an electric clothes dryer, the product of the following three factors, with the resulting product then being rounded off to the nearest dollar per year:

(A) The annual representative average number of clothes dryer cycles as specified in appendix D1 or appendix D2 to this subpart, as appropriate;

(B) The per-cycle combined total energy consumption in kilowatt-hours per cycle, determined according to section 4.6 of appendix D1 or section 4.6 of appendix D2 to this subpart, as appropriate; and

(C) The representative average unit cost of electrical energy in dollars per kilowatt-hour as provided by the Secretary; and

(ii) For a gas clothes dryer, the product of the annual representative average number of clothes dryer cycles as specified in appendix D1 or D2 to this subpart, as appropriate, times the sum of the following three factors, with the resulting product then being rounded off to the nearest dollar per year:

(A) The product of the per-cycle gas dryer electric energy consumption in kilowatt-hours per cycle, determined according to section 4.2 of appendix D1 or section 4.2 of appendix D2 to this subpart, as appropriate, times the representative average unit cost of electrical energy in dollars per kilowatt-hour as provided by the Secretary; plus,

(B) The product of the per-cycle gas dryer gas energy consumption, in Btus per cycle, determined according to section 4.3 of appendix D1 or section 4.3 of appendix D2 to this subpart, as appropriate, times the representative average unit cost for natural gas or propane, as appropriate, in dollars per Btu as provided by the Secretary; plus,

(C) The product of the per-cycle standby mode and off mode energy consumption in kilowatt-hours per cycle, determined according to section 4.5 of appendix D1 or section 4.5 of appendix D2 to this subpart, as appropriate, times the representative average unit cost of electrical energy in dollars per kilowatt-hour as provided by the Secretary.

(3) The combined energy factor, expressed in pounds per kilowatt-hour is determined in accordance with section 4.7 of appendix D1 or section 4.7 of appendix D2 to this subpart, as appropriate, the result then being rounded off to the nearest hundredth (0.01).

(4) Other useful measures of energy consumption for clothes dryers shall be those measures of energy consumption for clothes dryers which the Secretary determines are likely to assist consumers in making purchasing decisions and which are derived from the application of appendix D1 or D2 to this subpart, as appropriate.

(e) Water heaters. (1) The estimated annual operating cost is calculated as:

(i) For a gas-fired or oil-fired water heater, the sum of:

(A) The product of the annual gas or oil energy consumption, determined according to section 6.3.11 or 6.4.7 of appendix E to this subpart, times the representative average unit cost of gas or oil, as appropriate, in dollars per Btu as provided by the Secretary; plus

(B) The product of the annual electric energy consumption, determined according to section 6.3.10 or 6.4.6 of appendix E to this subpart, times the representative average unit cost of electricity in dollars per kilowatt-hour as provided by the Secretary. Round the resulting sum to the nearest dollar per year.

(ii) For an electric water heater, the product of the annual energy consumption, determined according to section 6.3.10 or 6.4.6 of appendix E to this subpart, times the representative average unit cost of electricity in dollars per kilowatt-hour as provided by the Secretary. Round the resulting product to the nearest dollar per year.

(2) For an individual unit, the uniform energy factor is rounded to the nearest 0.01 and determined in accordance with section 6.3.8 or section 6.4.4 of appendix E to this subpart.

(f) Room air conditioners. (1) Determine cooling capacity, expressed in British thermal units per hour (Btu/h), as follows:

(i) For a single-speed room air conditioner, determine the cooling capacity in accordance with section 4.1.2 of appendix F of this subpart.

(ii) For a variable-speed room air conditioner, determine the cooling capacity in accordance with section 4.1.2 of appendix F of this subpart for test condition 1 in Table 1 of appendix F of this subpart.

(2) Determine electrical power input, expressed in watts (W) as follows:

(i) For a single-speed room air conditioner, determine the electrical power input in accordance with section 4.1.2 of appendix F of this subpart.

(ii) For a variable-speed room air conditioner, determine the electrical power input in accordance with section 4.1.2 of appendix F of this subpart, for test condition 1 in Table 1 of appendix F of this subpart.

(3) Determine the combined energy efficiency ratio (CEER), expressed in British thermal units per watt-hour (Btu/Wh) and as follows:

(i) For a single-speed room air conditioner, determine the CEER in accordance with section 5.2.2 of appendix F of this subpart.

(ii) For a variable-speed room air conditioner, determine the CEER in accordance with section 5.3.11 of appendix F of this subpart.

(4) Determine the estimated annual operating cost for a room air conditioner, expressed in dollars per year, by multiplying the following two factors and rounding as directed:

(i) For single-speed room air conditioners, the sum of AECcool and AECia/om, determined in accordance with section 5.2.1 and section 5.1, respectively, of appendix F of this subpart. For variable-speed room air conditioners, the sum of AECwt and AECia/om, determined in accordance with section 5.3.4 and section 5.1, respectively, of appendix F of this subpart; and

(ii) A representative average unit cost of electrical energy in dollars per kilowatt-hour as provided by the Secretary. Round the resulting product to the nearest dollar per year.

(g) Unvented home heating equipment. (1) The estimated annual operating cost for primary electric heaters, shall be the product of:

(i) The average annual electric energy consumption in kilowatt-hours per year, determined according to section 3.1 of appendix G of this subpart and

(ii) the representative average unit cost in dollars per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act, the resulting product then being rounded off to the nearest dollar per year.

(2) The estimated regional annual operating cost for primary electric heaters, shall be the product of: (i) The regional annual electric energy consumption in kilowatt-hours per year for primary heaters determined according to section 3.2 of appendix G of this subpart and (ii) the representative average unit cost in dollars per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act, the resulting product then being rounded off to the nearest dollar per year.

(3) The estimated operating cost per million Btu output shall be—

(i) For primary and supplementary electric heaters and unvented gas and oil heaters without an auxiliary electric system, the product of:

(A) One million; and

(B) The representative unit cost in dollars per Btu for natural gas, propane, or oil, as provided pursuant to section 323(b)(2) of the Act as appropriate, or the quotient of the representative unit cost in dollars per kilowatt-hour, as provided pursuant to section 323(b)(2) of the Act, divided by 3,412 Btu per kilowatt hour, the resulting product then being rounded off to the nearest 0.01 dollar per million Btu output; and

(ii) For unvented gas and oil heaters with an auxiliary electric system, the product of: (A) The quotient of one million divided by the rated output in Btu's per hour as determined in 3.4 of appendix G of this subpart; and (B) the sum of: (1) The product of the maximum fuel input in Btu's per hour as determined in 2.2. of this appendix times the representative unit cost in dollars per Btu for natural gas, propane, or oil, as appropriate, as provided pursuant to section 323(b)(2) of the Act, plus (2) the product of the maximum auxiliary electric power in kilowatts as determined in 2.1 of appendix G of this subpart times the representative unit cost in dollars per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act, the resulting quantity shall be rounded off to the nearest 0.01 dollar per million Btu output.

(4) The rated output for unvented heaters is the rated output as determined according to either sections 3.3 or 3.4 of appendix G of this subpart, as appropriate, with the result being rounded to the nearest 100 Btu per hour.

(5) Other useful measures of energy consumption for unvented home heating equipment shall be those measures of energy consumption for unvented home heating equipment which the Secretary determines are likely to assist consumers in making purchasing decisions and which are derived from the application of appendix G of this subpart.

(h) Television sets. The power consumption of a television set, expressed in watts, including on and standby modes, shall be determined in accordance with sections 3 and 4 of appendix H of this subpart respectively. The annual energy consumption, expressed in kilowatt-hours per year, shall be determined in accordance with section 4 of appendix H of this subpart.

(i) Cooking products. (1) Determine the standby power for microwave ovens, excluding any microwave oven component of a combined cooking product, according to section 3.2.3 of appendix I to this subpart. Round standby power to the nearest 0.1 watt.

(2)(i) Determine the integrated annual energy consumption of a conventional electric cooking top, including any conventional cooking top component of a combined cooking product, according to section 4.3.1 of appendix I1 to this subpart. Round the result to the nearest 1 kilowatt-hour (kWh) per year.

(ii) Determine the integrated annual energy consumption of a conventional gas cooking top, including any conventional cooking top component of a combined cooking product, according to section 4.3.2 of appendix I1 to this subpart. Round the result to the nearest 1 kilo-British thermal unit (kBtu) per year.

(3) Determine the total annual gas energy consumption of a conventional gas cooking top, including any conventional cooking top component of a combined cooking product, according to section 4.1.2.2.1 of appendix I1 to this subpart. Round the result to the nearest 1 kBtu per year.

(4)(i) Determine the total annual electrical energy consumption of a conventional electric cooking top, including any conventional cooking top component of a combined cooking product, as the integrated annual energy consumption of the conventional electric cooking top, as determined in paragraph (i)(2)(i) of this section.

(ii) Determine the total annual electrical energy consumption of a conventional gas cooking top, including any conventional cooking top component of a combined cooking product, as follows, rounded to the nearest 1 kWh per year:

ETGE = EAGE + ETLP Where: EAGE is the conventional gas cooking top annual active mode electrical energy consumption as defined in section 4.1.2.2.2 of appendix I1 to this subpart, and ETLP is the combined low-power mode energy consumption as defined in section 4.1 of appendix I1 to this subpart.

(5) Determine the estimated annual operating cost corresponding to the energy consumption of a conventional cooking top, including any conventional cooking top component of a combined cooking product, as follows, rounded to the nearest dollar per year:

(ETGE × CKWH) + (ETGG × CKBTU) Where: ETGE is the total annual electrical energy consumption for any electric energy usage, in kilowatt-hours (kWh) per year, as determined in accordance with paragraph (i)(4) of this section; CKWH is the representative average unit cost for electricity, in dollars per kWh, as provided pursuant to section 323(b)(2) of the Act; ETGG is the total annual gas energy consumption, in kBtu per year, as determined in accordance with paragraph (i)(3) of this section; and CKBTU is the representative average unit cost for natural gas or propane, in dollars per kBtu, as provided pursuant to section 323(b)(2) of the Act, for conventional gas cooking tops that operate with natural gas or with LP-gas, respectively.

(6) Other useful measures of energy consumption for conventional cooking tops shall be the measures of energy consumption that the Secretary determines are likely to assist consumers in making purchasing decisions and that are derived from the application of appendix I1 to this subpart.

(j) Clothes washers. (1) The estimated annual operating cost for automatic and semi-automatic clothes washers must be rounded off to the nearest dollar per year and is defined as follows:

(i) When using appendix J (see the note at the beginning of appendix J),

(A) When electrically heated water is used,

(N × (MET + HET + ETLP) × CKWH) Where: N = the representative average residential clothes washer use of 234 cycles per year according to appendix J, MET = the total weighted per-cycle machine electrical energy consumption, in kilowatt-hours per cycle, determined according to section 4.1.6 of appendix J, HET = the total weighted per-cycle hot water energy consumption using an electrical water heater, in kilowatt-hours per cycle, determined according to section 4.1.3 of appendix J, ETLP = the per-cycle combined low-power mode energy consumption, in kilowatt-hours per cycle, determined according to section 4.6.2 of appendix J, and CKWH = the representative average unit cost, in dollars per kilowatt-hour, as provided by the Secretary.

(B) When gas-heated or oil-heated water is used,

(N × (((MET + ETLP) × CKWH) + (HETG × CBTU))) Where: N, MET, ETLP, and CKWH are defined in paragraph (j)(1)(i)(A) of this section, HETG = the total per-cycle hot water energy consumption using gas-heated or oil-heated water, in Btu per cycle, determined according to section 4.1.4 of appendix J, and CBTU = the representative average unit cost, in dollars per Btu for oil or gas, as appropriate, as provided by the Secretary.

(ii) When using appendix J2 (see the note at the beginning of appendix J2),

(A) When electrically heated water is used

(N2 × (ETE2 + ETLP2) × CKWH) Where: N2 = the representative average residential clothes washer use of 295 cycles per year according to appendix J2, ETE2 = the total per-cycle energy consumption when electrically heated water is used, in kilowatt-hours per cycle, determined according to section 4.1.7 of appendix J2, ETLP2 = the per-cycle combined low-power mode energy consumption, in kilowatt-hours per cycle, determined according to section 4.4 of appendix J2, and CKWH = the representative average unit cost, in dollars per kilowatt-hour, as provided by the Secretary

(B) When gas-heated or oil-heated water is used,

(N2 × (((MET2 + ETLP2) × CKWH) + (HETG2 × CBTU))) Where: N2, ETLP2, and CKWH are defined in paragraph (j)(1)(ii)(A) of this section, MET2 = the total weighted per-cycle machine electrical energy consumption, in kilowatt-hours per cycle, determined according to section 4.1.6 of appendix J2, HETG2 = the total per-cycle hot water energy consumption using gas-heated or oil-heated water, in Btu per cycle, determined according to section 4.1.4 of appendix J2, and CBTU = the representative average unit cost, in dollars per Btu for oil or gas, as appropriate, as provided by the Secretary.

(2)(i) The integrated modified energy factor for automatic and semi-automatic clothes washers is determined according to section 4.6 of appendix J2 (when using appendix J2). The result shall be rounded off to the nearest 0.01 cubic foot per kilowatt-hour per cycle.

(ii) The energy efficiency ratio for automatic and semi-automatic clothes washers is determined according to section 4.9 of appendix J (when using appendix J). The result shall be rounded to the nearest 0.01 pound per kilowatt-hour per cycle.

(3) The annual water consumption of a clothes washer must be determined as:

(i) When using appendix J, the product of the representative average-use of 234 cycles per year and the total weighted per-cycle water consumption in gallons per cycle determined according to section 4.2.4 of appendix J.

(ii) When using appendix J2, the product of the representative average-use of 295 cycles per year and the total weighted per-cycle water consumption for all wash cycles, in gallons per cycle, determined according to section 4.2.11 of appendix J2.

(4)(i) The integrated water factor must be determined according to section 4.2.12 of appendix J2, with the result rounded to the nearest 0.1 gallons per cycle per cubic foot.

(ii) The water efficiency ratio for automatic and semi-automatic clothes washers is determined according to section 4.7 of appendix J (when using appendix J). The result shall be rounded to the nearest 0.01 pound per gallon per cycle.

(5) Other useful measures of energy consumption for automatic or semi-automatic clothes washers shall be those measures of energy consumption that the Secretary determines are likely to assist consumers in making purchasing decisions and that are derived from the application of appendix J or appendix J2, as appropriate.

(k)-(l) [Reserved]

(m) Central air conditioners and heat pumps. See the note at the beginning of appendix M and M1 to determine the appropriate test method. Determine all values discussed in this section using a single appendix.

(1) Determine cooling capacity from the steady-state wet-coil test (A or A2 Test), as described in section 3.2 of appendix M or M1 to this subpart, and rounded off to the nearest

(i) To the nearest 50 Btu/h if cooling capacity is less than 20,000 Btu/h;

(ii) To the nearest 100 Btu/h if cooling capacity is greater than or equal to 20,000 Btu/h but less than 38,000 Btu/h; and

(iii) To the nearest 250 Btu/h if cooling capacity is greater than or equal to 38,000 Btu/h and less than 65,000 Btu/h.

(2) Determine seasonal energy efficiency ratio (SEER) as described in section 4.1 of appendix M to this subpart or seasonal energy efficiency ratio 2 (SEER2) as described in section 4.1 of appendix M1 to this subpart, and round off to the nearest 0.025 Btu/W-h.

(3) Determine energy efficiency ratio (EER) as described in section 4.6 of appendix M or M1 to this subpart, and round off to the nearest 0.025 Btu/W-h. The EER from the A or A2 test, whichever applies, when tested in accordance with appendix M1 to this subpart, is referred to as EER2.

(4) Determine heating seasonal performance factors (HSPF) as described in section 4.2 of appendix M to this subpart or heating seasonal performance factors 2 (HSPF2) as described in section 4.2 of appendix M1 to this subpart, and round off to the nearest 0.025 Btu/W-h.

(5) Determine average off mode power consumption as described in section 4.3 of appendix M or M1 to this subpart, and round off to the nearest 0.5 W.

(6) Determine all other measures of energy efficiency or consumption or other useful measures of performance using appendix M or M1 of this subpart.

(n) Furnaces. (1) The estimated annual operating cost for furnaces is the sum of:

(i) The product of the average annual fuel energy consumption, in Btu's per year for gas or oil furnaces or in kilowatt-hours per year for electric furnaces, determined according to section 10.2.2 or 10.3 of appendix N of this subpart, respectively, (for furnaces, excluding low pressure steam or hot water boilers and electric boilers) or section 10.2.2 or 10.3 of appendix EE of this subpart, respectively (for low pressure steam or hot water boilers and electric boilers), and the representative average unit cost in dollars per Btu for gas or oil, or dollars per kilowatt-hour for electric, as appropriate, as provided pursuant to section 323(b)(2) of the Act; plus

(ii) The product of the average annual auxiliary electric energy consumption in kilowatt-hours per year determined according to section 10.2.3 of appendix N of this subpart (for furnaces, excluding low pressure steam or hot water boilers and electric boilers) or section 10.2.3 of appendix EE of this subpart (for low pressure steam or hot water boilers and electric boilers) of this subpart, and the representative average unit cost in dollars per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act.

(iii) Round the resulting sum to the nearest dollar per year.

(2) The annual fuel utilization efficiency (AFUE) for furnaces, expressed in percent, is the ratio of the annual fuel output of useful energy delivered to the heated space to the annual fuel energy input to the furnace.

(i) For gas and oil furnaces, determine AFUE according to section 10.1 of appendix N (for furnaces, excluding low pressure steam or hot water boilers and electric boilers) or section 10.1 of appendix EE (for low pressure steam or hot water boilers and electric boilers) of this subpart, as applicable.

(ii) For electric furnaces, excluding electric boilers, determine AFUE in accordance with section 11.1 of ANSI/ASHRAE 103-1993 (incorporated by reference, see § 430.3); for electric boilers, determine AFUE in accordance with section 11.1 of ANSI/ASHRAE 103-2017 (incorporated by reference, see § 430.3).

(iii) Round the AFUE to one-tenth of a percentage point.

(3) The estimated regional annual operating cost for furnaces is calculated as follows:

(i) When using appendix N of this subpart for furnaces excluding low pressure steam or hot water boilers and electric boilers (see the note at the beginning of appendix N of this subpart),

(A) For gas or oil-fueled furnaces,

(EFR × CBTU) + (EAER × CKWH) Where: EFR = the regional annual fuel energy consumption in Btu per year, determined according to section 10.7.1 of appendix N of this subpart; CBTU = the representative average unit cost in dollars per Btu of gas or oil, as provided pursuant to section 323(b)(2) of the Act; EAER = the regional annual auxiliary electrical energy consumption in kilowatt-hours per year, determined according to section 10.7.2 of appendix N of this subpart; and CKWH = the representative average unit cost in dollars per kilowatt-hour of electricity, as provided pursuant to section 323(b)(2) of the Act.

(B) For electric furnaces,

(EER × CKWH) Where: EER = the regional annual fuel energy consumption in kilowatt-hours per year, determined according to section 10.7.3 of appendix N of this subpart; and CKWH is as defined in paragraph (n)(3)(i)(A) of this section.

(ii) When using appendix EE of this subpart for low pressure steam or hot water boilers and electric boilers (see the note at the beginning of appendix EE of this subpart),

(A) For gas or oil-fueled boilers,

(EER × CBTU) + (EAER × CKWH) Where: EFR = the regional annual fuel energy consumption in Btu per year, determined according to section 10.5.1 of appendix EE of this subpart; CBTU and CKWH are as defined in paragraph (n)(3)(i)(A) of this section; and EAER = the regional annual auxiliary electrical energy consumption in kilowatt-hours per year, determined according to section 10.5.2 of appendix EE of this subpart.

(B) For electric boilers,

(EER × CKWH) Where: EER = the regional annual fuel energy consumption in kilowatt-hours per year, determined according to section 10.5.3 of appendix EE of this subpart; and CKWH is as defined in paragraph (n)(3)(i)(A) of this section.

(iii) Round the estimated regional annual operating cost to the nearest dollar per year.

(4) The energy factor for furnaces, expressed in percent, is the ratio of annual fuel output of useful energy delivered to the heated space to the total annual energy input to the furnace determined according to either section 10.6 of appendix N of this subpart (for furnaces, excluding low pressure steam or hot water boilers and electric boilers) or section 10.4 of appendix EE of this subpart (for low pressure steam or hot water boilers and electric boilers), as applicable.

(5) The average standby mode and off mode electrical power consumption for furnaces shall be determined according to section 8.10 of appendix N of this subpart (for furnaces, excluding low pressure steam or hot water boilers and electric boilers) or section 8.9 of appendix EE of this subpart (for low pressure steam or hot water boilers and electric boilers), as applicable. Round the average standby mode and off mode electrical power consumption to the nearest tenth of a watt.

(6) Other useful measures of energy consumption for furnaces shall be those measures of energy consumption which the Secretary determines are likely to assist consumers in making purchasing decisions and which are derived from the application of appendix N of this subpart (for furnaces, excluding low pressure steam or hot water boilers and electric boilers) or appendix EE of this subpart (for low pressure steam or hot water boilers and electric boilers).

(o) Vented home heating equipment. (1) When determining the annual fuel utilization efficiency (AFUE) of vented home heating equipment (see the note at the beginning of appendix O), expressed in percent (%), calculate AFUE in accordance with section 4.1.17 of appendix O of this subpart for vented heaters without either manual controls or thermal stack dampers; in accordance with section 4.2.6 of appendix O of this subpart for vented heaters equipped with manual controls; or in accordance with section 4.3.7 of appendix O of this subpart for vented heaters equipped with thermal stack dampers.

(2) When estimating the annual operating cost for vented home heating equipment, calculate the sum of:

(i) The product of the average annual fuel energy consumption, in Btus per year for natural gas, propane, or oil fueled vented home heating equipment, determined according to section 4.6.2 of appendix O of this subpart, and the representative average unit cost in dollars per Btu for natural gas, propane, or oil, as appropriate, as provided pursuant to section 323(b)(2) of the Act; plus

(ii) The product of the average annual auxiliary electric energy consumption in kilowatt-hours per year determined according to section 4.6.3 of appendix O of this subpart, and the representative average unit cost in dollars per kilowatt-hours as provided pursuant to section 323(b)(2) of the Act. Round the resulting sum to the nearest dollar per year.

(3) When estimating the operating cost per million Btu output for gas or oil vented home heating equipment with an auxiliary electric system, calculate the product of:

(i) The quotient of one million Btu divided by the sum of:

(A) The product of the maximum fuel input in Btus per hour as determined in sections 3.1.1 or 3.1.2 of appendix O of this subpart times the annual fuel utilization efficiency in percent as determined in sections 4.1.17, 4.2.6, or 4.3.7 of this appendix (as appropriate) divided by 100, plus

(B) The product of the maximum electric power in watts as determined in section 3.1.3 of appendix O of this subpart times the quantity 3.412; and

(ii) The sum of:

(A) the product of the maximum fuel input in Btus per hour as determined in sections 3.1.1 or 3.1.2 of this appendix times the representative unit cost in dollars per Btu for natural gas, propane, or oil, as appropriate, as provided pursuant to section 323(b)(2) of the Act; plus

(B) the product of the maximum auxiliary electric power in kilowatts as determined in section 3.1.3 of appendix O of this subpart times the representative unit cost in dollars per kilowatt-hour as provided pursuant to section 323(b)(2) of the Act. Round the resulting quantity to the nearest 0.01 dollar per million Btu output.

(p) Pool heaters. (1) Determine the thermal efficiency (Et) of a pool heater expressed as a percent (%) in accordance with section 5.1 of appendix P to this subpart.

(2) Determine the integrated thermal efficiency (TEI) of a pool heater expressed as a percent (%) in accordance with section 5.4 of appendix P to this subpart.

(3) When estimating the annual operating cost of pool heaters, calculate the sum of:

(i) The product of the average annual fossil fuel energy consumption, in Btus per year, determined according to section 5.2 of appendix P to this subpart, and the representative average unit cost in dollars per Btu for natural gas or oil, as appropriate, as provided pursuant to section 323(b)(2) of the Act; plus

(ii) The product of the average annual electrical energy consumption in kilowatt-hours per year determined according to section 5.3 of appendix P to this subpart and converted to kilowatt-hours using a conversion factor of 3412 Btus = 1 kilowatt-hour, and the representative average unit cost in dollars per kilowatt-hours as provided pursuant to section 323(b)(2) of the Act. Round the resulting sum to the nearest dollar per year.

(q) Fluorescent lamp ballasts. (1) Calculate ballast luminous efficiency (BLE) using appendix Q to this subpart.

(2) Calculate power factor using appendix Q to this subpart.

(r) General service fluorescent lamps, general service incandescent lamps, and incandescent reflector lamps. Measure initial lumen output, initial input power, initial lamp efficacy, color rendering index (CRI), correlated color temperature (CCT), and time to failure of GSFLs, IRLs, and GSILs, as applicable, in accordance with appendix R to this subpart.

(s) Faucets. Measure the water use for lavatory faucets, lavatory replacement aerators, kitchen faucets, and kitchen replacement aerators, in gallons or liters per minute (gpm or L/min), in accordance to section 2.1 of appendix S of this subpart. Measure the water use for metering faucets, in gallons or liters per cycle (gal/cycle or L/cycle), in accordance to section 2.1 of appendix S of this subpart.

(t) Showerheads. Measure the water use for showerheads, in gallons or liters per minute (gpm or L/min), in accordance to section 2.2 of appendix S of this subpart.

(u) Water closets. Measure the water use for water closets, expressed in gallons or liters per flush (gpf or Lpf), in accordance with section 3(a) of appendix T to this subpart.

(v) Urinals. Measure the water use for urinals, expressed in gallons or liters per flush (gpf or Lpf), in accordance with section 3(b) of appendix T to this subpart.

(w) Ceiling fans. Measure the following attributes of a single ceiling fan in accordance with appendix U to this subpart: airflow; power consumption; ceiling fan efficiency, as applicable; ceiling fan energy index (CFEI), as applicable; standby power, as applicable; distance between the ceiling and lowest point of fan blades; blade span; blade edge thickness; and blade revolutions per minute (RPM).

(x) Ceiling fan light kits.

(1) For each ceiling fan light kit that requires compliance with the January 21, 2020 energy conservation standards:

(i) For a ceiling fan light kit packaged with compact fluorescent lamps, measure lamp efficacy, lumen maintenance at 1,000 hours, lumen maintenance at 40 percent of lifetime, rapid cycle stress test, and time to failure in accordance with paragraph (y) of this section for each lamp basic model.

(ii) For a ceiling fan light kit packaged with general service fluorescent lamps, measure lamp efficacy in accordance with paragraph (r) of this section for each lamp basic model.

(iii) For a ceiling fan light kit packaged with incandescent lamps, measure lamp efficacy in accordance with paragraph (r) of this section for each lamp basic model.

(iv) For a ceiling fan light kit packaged with integrated LED lamps, measure lamp efficacy in accordance with paragraph (ee) of this section for each lamp basic model.

(v) For a ceiling fan light kit packaged with other fluorescent lamps (not compact fluorescent lamps or general service fluorescent lamps), packaged with consumer-replaceable SSL (not integrated LED lamps), packaged with non-consumer-replaceable SSL, or packaged with other SSL lamps that have an ANSI standard base (not integrated LED lamps), measure efficacy in accordance with section 3 of appendix V of this subpart for each lamp basic model, consumer-replaceable SSL basic model, or non-consumer-replaceable SSL basic model.

(2) [Reserved]

(y) Compact fluorescent lamps. (1) Measure initial lumen output, input power, initial lamp efficacy, lumen maintenance at 1,000 hours, lumen maintenance at 40 percent of lifetime of a compact fluorescent lamp (as defined in 10 CFR 430.2), color rendering index (CRI), correlated color temperature (CCT), power factor, start time, standby mode energy consumption, and time to failure in accordance with appendix W of this subpart. Express time to failure in hours.

(2) Conduct the rapid cycle stress test in accordance with section 3.3 of appendix W of this subpart.

(z) Dehumidifiers. (1) Determine the capacity, expressed in pints/day, according to section 5.2 of appendix X1 to this subpart.

(2) Determine the integrated energy factor, expressed in L/kWh, according to section 5.4 of appendix X1 to this subpart.

(3) Determine the case volume, expressed in cubic feet, for whole-home dehumidifiers in accordance with section 5.7 of appendix X1 of this subpart.

(aa) Battery Chargers. (1) For battery chargers subject to compliance with the relevant standard at § 430.32(z) as that standard appeared in the January 1, 2022, edition of 10 CFR parts 200-499:

(i) Measure the maintenance mode power, standby power, off mode power, battery discharge energy, 24-hour energy consumption and measured duration of the charge and maintenance mode test for a battery charger other than uninterruptible power supplies in accordance with appendix Y to this subpart;

(ii) Calculate the unit energy consumption of a battery charger other than uninterruptible power supplies in accordance with appendix Y to this subpart;

(iii) Calculate the average load adjusted efficiency of an uninterruptible power supply in accordance with appendix Y to this subpart.

(2) For a battery charger subject to compliance with any amended relevant standard provided in § 430.32 that is published after September 8, 2022:

(i) Measure active mode energy, maintenance mode power, no-battery mode power, off mode power and battery discharge energy for a battery charger other than uninterruptible power supplies in accordance with appendix Y1 to this subpart.

(ii) Calculate the standby power of a battery charger other than uninterruptible power supplies in accordance with appendix Y1, to this subpart.

(iii) Calculate the average load adjusted efficiency of an uninterruptible power supply in accordance with appendix Y1 to this subpart.

(bb) External Power Supplies. The energy consumption of an external power supply, including active-mode efficiency expressed as a percentage and the no-load, off, and standby mode energy consumption levels expressed in watts, shall be measured in accordance with appendix Z of this subpart.

(cc) Furnace Fans. The energy consumption of a single unit of a furnace fan basic model expressed in watts per 1000 cubic feet per minute (cfm) to the nearest integer shall be calculated in accordance with Appendix AA of this subpart.

(dd) Portable air conditioners.

(1) When using appendix CC to this subpart, measure the seasonally adjusted cooling capacity (“SACC”) in British thermal units per hour (Btu/h), and the combined energy efficiency ratio, in British thermal units per watt-hour (Btu/Wh) in accordance with sections 5.2 and 5.4 of appendix CC to this subpart, respectively. When using appendix CC1 to this subpart, measure the SACC in Btu/h, and the combined energy efficiency ratio, in Btu/Wh in accordance with sections 5.2 and 5.4, respectively, of appendix CC1 to this subpart.

(2) When using appendix CC to this subpart, determine the estimated annual operating cost for portable air conditioners, in dollars per year and rounded to the nearest whole number, by multiplying a representative average unit cost of electrical energy in dollars per kilowatt-hour as provided by the Secretary by the total annual energy consumption (“AEC”), determined as follows:

(i) For dual-duct single-speed portable air conditioners, the sum of AECDD_95 multiplied by 0.2, AECDD_83 multiplied by 0.8, and AECT as measured in accordance with section 5.3 of appendix CC to this subpart.

(ii) For single-duct single-speed portable air conditioners, the sum of AECSD and AECT as measured in accordance with section 5.3 of appendix CC to this subpart.

(iii) For dual-duct variable-speed portable air conditioners the overall sum of

(A) The sum of AECDD_95_Full and AECia/om, multiplied by 0.2, and

(B) The sum of AECDD_83_Low and AECia/om, multiplied by 0.8, as measured in accordance with section 5.3 of appendix CC to this subpart.

(iv) For single-duct variable-speed portable air conditioners, the overall sum of

(A) The sum of AECSD_Full and AECia/om, multiplied by 0.2, and

(B) The sum of AECSD_Low and AECia/om, multiplied by 0.8, as measured in accordance with section 5.3 of appendix CC to this subpart.

(3) When using appendix CC1 to this subpart, determine the estimated annual operating cost for portable air conditioners, in dollars per year and rounded to the nearest whole number, by multiplying a representative average unit cost of electrical energy in dollars per kilowatt-hour as provided by the Secretary by the total AEC. The total AEC is the sum of AEC95, AEC83, AECoc, and AECia, as measured in accordance with section 5.3 of appendix CC1 to this subpart.

(ee) Integrated light-emitting diode lamp. (1) The input power of an integrated light-emitting diode lamp must be measured in accordance with section 3 of appendix BB of this subpart.

(2) The lumen output of an integrated light-emitting diode lamp must be measured in accordance with section 3 of appendix BB of this subpart.

(3) The lamp efficacy of an integrated light-emitting diode lamp must be calculated in accordance with section 3 of appendix BB of this subpart.

(4) The correlated color temperature of an integrated light-emitting diode lamp must be measured in accordance with section 3 of appendix BB of this subpart.

(5) The color rendering index of an integrated light-emitting diode lamp must be measured in accordance with section 3 of appendix BB of this subpart.

(6) The power factor of an integrated light-emitting diode lamp must be measured in accordance with section 3 of appendix BB of this subpart.

(7) The time to failure of an integrated light-emitting diode lamp must be measured in accordance with section 4 of appendix BB of this subpart.

(8) The standby mode power must be measured in accordance with section 5 of appendix BB of this subpart.

(ff) Coolers and combination cooler refrigeration products. (1) The estimated annual operating cost for models without an anti-sweat heater switch shall be the product of the following three factors, with the resulting product then being rounded to the nearest dollar per year:

(i) The representative average-use cycle of 365 cycles per year;

(ii) The average per-cycle energy consumption for the standard cycle in kilowatt-hours per cycle, determined according to appendix A of this subpart; and

(iii) The representative average unit cost of electricity in dollars per kilowatt-hour as provided by the Secretary.

(2) The estimated annual operating cost for models with an anti-sweat heater switch shall be the product of the following three factors, with the resulting product then being rounded to the nearest dollar per year:

(i) The representative average-use cycle of 365 cycles per year;

(ii) Half the sum of the average per-cycle energy consumption for the standard cycle and the average per-cycle energy consumption for a test cycle type with the anti-sweat heater switch in the position set at the factory just before shipping, each in kilowatt-hours per cycle, determined according to appendix A of this subpart; and

(iii) The representative average unit cost of electricity in dollars per kilowatt-hour as provided by the Secretary.

(3) The estimated annual operating cost for any other specified cycle type shall be the product of the following three factors, with the resulting product then being rounded to the nearest dollar per year:

(i) The representative average-use cycle of 365 cycles per year;

(ii) The average per-cycle energy consumption for the specified cycle type, determined according to appendix A of this subpart; and

(iii) The representative average unit cost of electricity in dollars per kilowatt-hour as provided by the Secretary.

(4) The energy factor, expressed in cubic feet per kilowatt-hour per cycle, shall be:

(i) For models without an anti-sweat heater switch, the quotient of:

(A) The adjusted total volume in cubic feet, determined according to appendix A of this subpart, divided by—

(B) The average per-cycle energy consumption for the standard cycle in kilowatt-hours per cycle, determined according to appendix A of this subpart, the resulting quotient then being rounded to the second decimal place; and

(ii) For models having an anti-sweat heater switch, the quotient of:

(A) The adjusted total volume in cubic feet, determined according to appendix A of this subpart, divided by—

(B) Half the sum of the average per-cycle energy consumption for the standard cycle and the average per-cycle energy consumption for a test cycle type with the anti-sweat heater switch in the position set at the factory just before shipping, each in kilowatt-hours per cycle, determined according to appendix A of this subpart, the resulting quotient then being rounded to the second decimal place.

(5) The annual energy use, expressed in kilowatt-hours per year and rounded to the nearest kilowatt-hour per year, shall be determined according to appendix A of this subpart.

(6) Other useful measures of energy consumption shall be those measures of energy consumption that the Secretary determines are likely to assist consumers in making purchasing decisions which are derived from the application of appendix A of this subpart.

(7) The following principles of interpretation shall be applied to the test procedure. The intent of the energy test procedure is to simulate operation in typical room conditions (72 °F (22.2 °C)) with door openings by testing at 90 °F (32.2 °C) ambient temperature without door openings. Except for operating characteristics that are affected by ambient temperature (for example, compressor percent run time), the unit, when tested under this test procedure, shall operate in a manner equivalent to the unit's operation while in typical room conditions.

(i) The energy used by the unit shall be calculated when a calculation is provided by the test procedure. Energy consuming components that operate in typical room conditions (including as a result of door openings, or a function of humidity), and that are not excluded by this test procedure, shall operate in an equivalent manner during energy testing under this test procedure, or be accounted for by all calculations as provided for in the test procedure. Examples:

(A) Energy saving features that are designed to operate when there are no door openings for long periods of time shall not be functional during the energy test.

(B) The defrost heater shall neither function nor turn off differently during the energy test than it would when in typical room conditions. Also, the product shall not recover differently during the defrost recovery period than it would in typical room conditions.

(C) Electric heaters that would normally operate at typical room conditions with door openings shall also operate during the energy test.

(D) Energy used during adaptive defrost shall continue to be measured and adjusted per the calculation provided for in this test procedure.

(ii) DOE recognizes that there may be situations that the test procedures do not completely address. In such cases, a manufacturer must obtain a waiver in accordance with the relevant provisions of this part if:

(A) A product contains energy consuming components that operate differently during the prescribed testing than they would during representative average consumer use; and

(B) Applying the prescribed test to that product would evaluate it in a manner that is unrepresentative of its true energy consumption (thereby providing materially inaccurate comparative data).

(8) For non-compressor models, “compressor” and “compressor cycles” as used in appendix A of this subpart shall be interpreted to mean “refrigeration system” and “refrigeration system cycles,” respectively.

(gg) General Service Lamps. (1) For general service incandescent lamps, use paragraph (r) of this section.

(2) For compact fluorescent lamps, use paragraph (y) of this section.

(3) For integrated LED lamps, use paragraph (ee) of this section.

(4) For other incandescent lamps, measure initial light output, input power, lamp efficacy, power factor, and standby mode power in accordance with appendix DD of this subpart.

(5) For other fluorescent lamps, measure initial light output, input power, lamp efficacy, power factor, and standby mode power in accordance with appendix DD of this subpart.

(6) For OLED and non-integrated LED lamps, measure initial light output, input power, lamp efficacy, power factor, and standby mode power in accordance with appendix DD of this subpart.

(hh) Air cleaners. (1) The pollen clean air delivery rate (CADR), smoke CADR, and dust CADR, expressed in cubic feet per minute (cfm), for conventional room air cleaners shall be measured in accordance with section 5 of appendix FF of this subpart.

(2) The PM2.5 CADR, expressed in cfm, for conventional room air cleaners, shall be measured in accordance with section 5 of appendix FF of this subpart.

(3) The active mode and standby mode power consumption, expressed in watts, shall be measured in accordance with sections 5 and 6, respectively, of appendix FF of this subpart.

(4) The annual energy consumption, expressed in kilowatt-hours per year, and the integrated energy factor, expressed in CADR per watts (CADR/W), for conventional room air cleaners, shall be measured in accordance with section 7 of appendix FF of this subpart.

(5) The estimated annual operating cost for conventional room air cleaners, expressed in dollars per year, shall be determined by multiplying the following two factors:

(i) The annual energy consumption as calculated in accordance with section 7 of appendix FF of this subpart, and

(ii) A representative average unit cost of electrical energy in dollars per kilowatt-hour as provided by the Secretary, the resulting product then being rounded off to the nearest dollar per year.

(ii) Portable electric spas. Measure the standby loss in watts and the fill volume in gallons of a portable electric spa in accordance with appendix GG to this subpart.

[42 FR 27898, June 1, 1977] Editorial Note:For Federal Register citations affecting § 430.23, see the List of CFR Sections Affected, which appears in the Finding Aids section of the printed volume and at www.govinfo.gov.

§ 430.24 - [Reserved]

§ 430.25 - Laboratory Accreditation Program.

The testing for general service fluorescent lamps, general service incandescent lamps (with the exception of lifetime testing), general service lamps (with the exception of applicable lifetime testing), incandescent reflector lamps, compact fluorescent lamps, and fluorescent lamp ballasts, and integrated light-emitting diode lamps must be conducted by test laboratories accredited by an Accreditation Body that is a signatory member to the International Laboratory Accreditation Cooperation (ILAC) Mutual Recognition Arrangement (MRA). A manufacturer's or importer's own laboratory, if accredited, may conduct the applicable testing.

[81 FR 72504, Oct. 20, 2016]

§ 430.27 - Petitions for waiver and interim waiver.

(a) General information. This section provides a means for seeking waivers of the test procedure requirements of this subpart for basic models that meet the requirements of paragraph (a)(1) of this section. In granting a waiver or interim waiver, DOE will not change the energy use or efficiency metric that the manufacturer must use to certify compliance with the applicable energy conservation standard and to make representations about the energy use or efficiency of the covered product. The granting of a waiver or interim waiver by DOE does not exempt such basic models from any other regulatory requirement contained in this part or the certification and compliance requirements of 10 CFR part 429 and specifies an alternative method for testing the basic models addressed in the waiver.

(1) Any interested person may submit a petition to waive for a particular basic model any requirements of § 430.23 or of any appendix to this subpart, upon the grounds that the basic model contains one or more design characteristics which either prevent testing of the basic model according to the prescribed test procedures or cause the prescribed test procedures to evaluate the basic model in a manner so unrepresentative of its true energy and/or water consumption characteristics as to provide materially inaccurate comparative data.

(2) Manufacturers of basic model(s) subject to a waiver or interim waiver are responsible for complying with the other requirements of this subpart and with the requirements of 10 CFR part 429 regardless of the person that originally submitted the petition for waiver and/or interim waiver. The filing of a petition for waiver and/or interim waiver shall not constitute grounds for noncompliance with any requirements of this subpart.

(3) All correspondence regarding waivers and interim waivers must be submitted to DOE either electronically to [email protected] (preferred method of transmittal) or by mail to U.S. Department of Energy, Building Technologies Program, Test Procedure Waiver, 1000 Independence Avenue SW., Mailstop EE-5B, Washington, DC 20585-0121.

(b) Petition content and publication. (1) Each petition for interim waiver and waiver must:

(i) Identify the particular basic model(s) for which a waiver is requested, each brand name under which the identified basic model(s) will be distributed in commerce, the design characteristic(s) constituting the grounds for the petition, and the specific requirements sought to be waived, and must discuss in detail the need for the requested waiver;

(ii) Identify manufacturers of all other basic models distributed in commerce in the United States and known to the petitioner to incorporate design characteristic(s) similar to those found in the basic model that is the subject of the petition;

(iii) Include any alternate test procedures known to the petitioner to evaluate the performance of the product type in a manner representative of the energy and/or water consumption characteristics of the basic model; and

(iv) Be signed by the petitioner or an authorized representative. In accordance with the provisions set forth in 10 CFR 1004.11, any request for confidential treatment of any information contained in a petition or in supporting documentation must be accompanied by a copy of the petition, application or supporting documentation from which the information claimed to be confidential has been deleted. DOE will publish in the Federal Register the petition and supporting documents from which confidential information, as determined by DOE, has been deleted in accordance with 10 CFR 1004.11 and will solicit comments, data and information with respect to the determination of the petition.

(2) In addition to the requirements in paragraph (b)(1) of this section, each petition for interim waiver must reference the related petition for waiver, demonstrate likely success of the petition for waiver, and address what economic hardship and/or competitive disadvantage is likely to result absent a favorable determination on the petition for interim waiver.

(c) Notification to other manufacturers. (1) Each petitioner for interim waiver must, upon publication of a grant of an interim waiver in the Federal Register, notify in writing all known manufacturers of domestically marketed basic models of the same product class (as specified in 10 CFR 430.32) and of other product classes known to the petitioner to use the technology or have the characteristic at issue in the waiver. The notice must include a statement that DOE has published the interim waiver and petition for waiver in the Federal Register and the date the petition for waiver was published. The notice must also include a statement that DOE will receive and consider timely written comments on the petition for waiver. Within five working days, each petitioner must file with DOE a statement certifying the names and addresses of each person to whom a notice of the petition for waiver has been sent.

(2) If a petitioner does not request an interim waiver and notification has not been provided pursuant to paragraph (c)(1) of this section, each petitioner, after filing a petition for waiver with DOE, and after the petition for waiver has been published in the Federal Register, must, within five working days of such publication, notify in writing all known manufacturers of domestically marketed units of the same product class (as listed in 10 CFR 430.32) and of other product classes known to the petitioner to use the technology or have the characteristic at issue in the waiver. The notice must include a statement that DOE has published the petition in the Federal Register and the date the petition for waiver was published. Within five working days of the publication of the petition in the Federal Register, each petitioner must file with DOE a statement certifying the names and addresses of each person to whom a notice of the petition for waiver has been sent.

(d) Public comment and rebuttal. (1) Any person submitting written comments to DOE with respect to an interim waiver must also send a copy of the comments to the petitioner by the deadline specified in the notice.

(2) Any person submitting written comments to DOE with respect to a petition for waiver must also send a copy of such comments to the petitioner.

(3) A petitioner may, within 10 working days of the close of the comment period specified in the Federal Register, submit a rebuttal statement to DOE. A petitioner may rebut more than one comment in a single rebuttal statement.

(e) Provisions specific to interim waivers. (1) DOE will post a petition for interim waiver on its website within 5 business days of receipt of a complete petition. DOE will make best efforts to review a petition for interim waiver within 90 business days of receipt of a complete petition.

(2) A petition for interim waiver that does not meet the content requirements of paragraph (b) of this section will be considered incomplete. DOE will notify the petitioner of an incomplete petition via email.

(3) DOE will grant an interim waiver from the test procedure requirements if it appears likely that the petition for waiver will be granted and/or if DOE determines that it would be desirable for public policy reasons to grant immediate relief pending a determination on the petition for waiver. Notice of DOE's determination on the petition for interim waiver will be published in the Federal Register.

(f) Provisions specific to waivers—(1) Disposition of application. The petitioner shall be notified in writing as soon as practicable of the disposition of each petition for waiver. DOE shall issue a decision on the petition as soon as is practicable following receipt and review of the Petition for Waiver and other applicable documents, including, but not limited to, comments and rebuttal statements.

(2) Criteria for granting. DOE will grant a waiver from the test procedure requirements if DOE determines either that the basic model(s) for which the waiver was requested contains a design characteristic that prevents testing of the basic model according to the prescribed test procedures, or that the prescribed test procedures evaluate the basic model in a manner so unrepresentative of its true energy or water consumption characteristics as to provide materially inaccurate comparative data. Waivers may be granted subject to conditions, which may include adherence to alternate test procedures specified by DOE. DOE will consult with the Federal Trade Commission prior to granting any waiver, and will promptly publish in the Federal Register notice of each waiver granted or denied, and any limiting conditions of each waiver granted.

(g) Extension to additional basic models. A petitioner may request that DOE extend the scope of a waiver or an interim waiver to include additional basic models employing the same technology as the basic model(s) set forth in the original petition. The petition for extension must identify the particular basic model(s) for which a waiver extension is requested, each brand name under which the identified basic model(s) will be distributed in commerce, and documentation supporting the claim that the additional basic models employ the same technology as the basic model(s) set forth in the original petition. DOE will publish any such extension in the Federal Register.

(h) Duration. (1) Within one year of issuance of an interim waiver, DOE will either:

(i) Publish in the Federal Register a determination on the petition for waiver; or

(ii) Publish in the Federal Register a new or amended test procedure that addresses the issues presented in the waiver.

(2) When DOE publishes a decision and order on a petition for waiver in the Federal Register pursuant to paragraph (f) of this section, the interim waiver will terminate upon the data specified in the decision and order, in accordance with paragraph (i) of this section.

(3) When DOE amends the test procedure to address the issues presented in a waiver, the waiver or interim waiver will automatically terminate on the date on which use of that test procedure is required to demonstrate compliance.

(4) When DOE publishes a decision and order in the Federal Register to modify a waiver pursuant to paragraph (k) of this section, the existing waiver will terminate 180 days after the publication date of the decision and order.

(i) Compliance certification and representations. (1) If the interim waiver test procedure methodology is different than the decision and order test procedure methodology, certification reports to DOE required under 10 CFR 429.12 and any representations must be based on either of the two methodologies until 180 days after the publication date of the decision and order. Thereafter, certification reports and any representations must be based on the decision and order test procedure methodology, unless otherwise specified by DOE. Once a manufacturer uses the decision and order test procedure methodology in a certification report or any representation, all subsequent certification reports and any representations must be made using the decision and order test procedure methodology while the waiver is valid.

(2) When DOE publishes a new or amended test procedure, certification reports to DOE required under 10 CFR 429.12 and any representations must be based on the testing methodology of an applicable waiver or interim waiver, or the new or amended test procedure until the date on which use of such test procedure is required to demonstrate compliance, unless otherwise specified by DOE in the test procedure final rule. Thereafter, certification reports and any representations must be based on the test procedure final rule methodology. Once a manufacturer uses the test procedure final rule methodology in a certification report or any representation, all subsequent certification reports and any representations must be made using the test procedure final rule methodology.

(3) If DOE publishes a decision and order modifying an existing waiver, certification reports to DOE required under 10 CFR 429.12 and any representations must be based on either of the two methodologies until 180 days after the publication date of the decision and order modifying the waiver. Thereafter, certification reports and any representations must be based on the modified test procedure methodology unless otherwise specified by DOE. Once a manufacturer uses the modified test procedure methodology in a certification report or any representation, all subsequent certification reports and any representations must be made using the modified test procedure methodology while the modified waiver is valid.

(j) Petition for waiver required of other manufactures. Any manufacturer of a basic model employing a technology or characteristic for which a waiver was granted for another basic model and that results in the need for a waiver (as specified by DOE in a published decision and order in the Federal Register) must petition for and be granted a waiver for that basic model. Manufacturers may also submit a request for interim waiver pursuant to the requirements of this section.

(k) Rescission or modification. (1) DOE may rescind or modify a waiver or interim waiver at any time upon DOE's determination that the factual basis underlying the petition for waiver or interim waiver is incorrect, upon a determination that the results from the alternate test procedure are unrepresentative of the basic model(s)' true energy consumption characteristics, or for other appropriate reason. Waivers and interim waivers are conditioned upon the validity of statements, representations, and documents provided by the requestor; any evidence that the original grant of a waiver or interim waiver was based upon inaccurate information will weigh against continuation of the waiver. DOE's decision will specify the basis for its determination and, in the case of a modification, will also specify the change to the authorized test procedure.

(2) A person may request that DOE rescind or modify a waiver or interim waiver issued to that person if the person discovers an error in the information provided to DOE as part of its petition, determines that the waiver is no longer needed, or for other appropriate reasons. In a request for rescission, the requestor must provide a statement explaining why it is requesting rescission. In a request for modification, the requestor must explain the need for modification to the authorized test procedure and detail the modifications needed and the corresponding impact on measured energy consumption.

(3) DOE will publish a proposed rescission or modification (DOE-initiated or at the request of the original requestor) in the Federal Register for public comment. A requestor may, within 10 working days of the close of the comment period specified in the proposed rescission or modification published in the Federal Register, submit a rebuttal statement to DOE. A requestor may rebut more than one comment in a single rebuttal statement.

(4) DOE will publish its decision in the Federal Register. DOE's determination will be based on relevant information contained in the record and any comments received.

(5) After the effective date of a rescission, any basic model(s) previously subject to a waiver must be tested and certified using the applicable DOE test procedure in 10 CFR part 430.

(l) Revision of regulation. As soon as practicable after the granting of any waiver, DOE will publish in the Federal Register a notice of proposed rulemaking to amend its regulations so as to eliminate any need for the continuation of such waiver. As soon thereafter as practicable, DOE will publish in the Federal Register a final rule.

(m) To exhaust administrative remedies, any person aggrieved by an action under this section must file an appeal with the DOE's Office of Hearings and Appeals as provided in 10 CFR part 1003, subpart C.

[79 FR 26599, May 9, 2014, as amended at 85 FR 79820, Dec. 11, 2020; 86 FR 70959, Dec. 14, 2021]

Appendix A - Appendix A to Subpart B of Part 430—Uniform Test Method for Measuring the Energy Consumption of Refrigerators, Refrigerator-Freezers, and Miscellaneous Refrigeration Products

Note:

Prior to April 11, 2022, any representations of volume and energy use of refrigerators, refrigerator-freezers, and miscellaneous refrigeration products must be based on the results of testing pursuant to either this appendix or the procedures in appendix A as it appeared at 10 CFR part 430, subpart B, appendix A, in the 10 CFR parts 200 to 499 edition revised as of January 1, 2019. Any representations of volume and energy use must be in accordance with whichever version is selected. On or after April 11, 2022, any representations of volume and energy use must be based on the results of testing pursuant to this appendix.

For refrigerators and refrigerator-freezers, the rounding requirements specified in sections 4 and 5 of this appendix are not required for use until the compliance date of any amendment of energy conservation standards for these products published after October 12, 2021.

1. Referenced Materials

DOE incorporated by reference AHAM HRF-1-2019, Energy and Internal Volume of Consumer Refrigeration Products (“HRF-1-2019”), and AS/NZS 4474.1:2007, Performance of Household Electrical Appliances—Refrigerating Appliances; Part 1: Energy Consumption and Performance, Second Edition (“AS/NZS 4474.1:2007”), in their entirety in § 430.3; however, only enumerated provisions of these documents are applicable to this appendix. If there is any conflict between HRF-1-2019 and this appendix or between AS/NZS 4474.1:2007 and this appendix, follow the language of the test procedure in this appendix, disregarding the conflicting industry standard language.

(a) AHAM HRF-1-2019, (“HRF-1-2019”), Energy and Internal Volume of Consumer Refrigeration Products:

(i) Section 3—Definitions, as specified in section 3 of this appendix;

(ii) Section 4—Method for Determining the Refrigerated Volume of Consumer Refrigeration Products, as specified in section 4.1 of this appendix;

(iii) Section 5—Method for Determining the Energy Consumption of Consumer Refrigeration Products (excluding Table 5-1 and sections 5.5.6.5, 5.8.2.1.2, 5.8.2.1.3, 5.8.2.1.4, 5.8.2.1.5, and 5.8.2.1.6), as specified in section 5 of this appendix; and

(iv) Section 6—Method for Determining the Adjusted Volume of Consumer Refrigeration Products, as specified in section 4.2 of this appendix;

(b) AS/NZS 4474.1:2007, (“AS/NZS 4474.1:2007”), Performance of Household Electrical Appliances—Refrigerating Appliances; Part 1: Energy Consumption and Performance, Second Edition:

(i) Appendix M—Method of Interpolation When Two Controls are Adjusted, as specified in sections 5.2(b) and 5.5 of this appendix.

(ii) [Reserved]

2. Scope

This appendix provides the test procedure for measuring the annual energy use in kilowatt-hours per year (kWh/yr), the total refrigerated volume in cubic feet (ft 3), and the total adjusted volume in cubic feet (ft 3) of refrigerators, refrigerator-freezers, and miscellaneous refrigeration products.

3. Definitions

Section 3, Definitions, of HRF-1-2019 applies to this test procedure. In case of conflicting terms between HRF-1-2019 and DOE's definitions in this appendix or in § 430.2, DOE's definitions take priority.

Door-in-door means a set of doors or an outer door and inner drawer for which—

(a) Both doors (or both the door and the drawer) must be opened to provide access to the interior through a single opening;

(b) Gaskets for both doors (or both the door and the drawer) are exposed to external ambient conditions on the outside around the full perimeter of the respective openings; and

(c) The space between the two doors (or between the door and the drawer) achieves temperature levels consistent with the temperature requirements of the interior compartment to which the door-in-door provides access.

Through-the-door ice/water dispenser means a device incorporated within the cabinet, but outside the boundary of the refrigerated space, that delivers to the user on demand ice and may also deliver water from within the refrigerated space without opening an exterior door. This definition includes dispensers that are capable of dispensing ice and water or ice only.

Transparent door means an external fresh food compartment door which meets the following criteria:

(a) The area of the transparent portion of the door is at least 40 percent of the area of the door.

(b) The area of the door is at least 50 percent of the sum of the areas of all the external doors providing access to the fresh food compartments and cooler compartments.

(c) For the purposes of this evaluation, the area of a door is determined as the product of the maximum height and maximum width dimensions of the door, not considering potential extension of flaps used to provide a seal to adjacent doors.

4. Volume

Determine the refrigerated volume and adjusted volume for refrigerators, refrigerator-freezers, and miscellaneous refrigeration products in accordance with the following sections of HRF-1-2019, respectively:

4.1. Section 4, Method for Determining the Refrigerated Volume of Consumer Refrigeration Products; and

4.2. Section 6, Method for Determining the Adjusted Volume of Consumer Refrigeration Products.

5. Energy Consumption

Determine the annual energy use (“AEU”) in kilowatt-hours per year (kWh/yr), for refrigerators, refrigerator-freezers, and miscellaneous refrigeration products in accordance with section 5, Method for Determining the Energy Consumption of Consumer Refrigeration Products, of HRF-1-2019, except as follows.

5.1. Test Setup and Test Conditions

(a) In section 5.3.1 of HRF-1-2019, the top of the unit shall be determined by the refrigerated cabinet height, excluding any accessories or protruding components on the top of the unit.

(b) The ambient temperature and vertical ambient temperature gradient requirements specified in section 5.3.1 of HRF-1-2019 shall be maintained during both the stabilization period and the test period.

(c) The power supply requirements as specified in section 5.5.1 of HRF-1-2019 shall be maintained based on measurement intervals not to exceed one minute.

(d) The ice storage compartment temperature requirement as specified in section 5.5.6.5 in HRF-1-2019 is not required.

(e) For cases in which setup is not clearly defined by this test procedure, manufacturers must submit a petition for a waiver (See section 6 of this appendix).

(f) If the interior arrangements of the unit under test do not conform with those shown in Figures 5-1 or 5-2 of HRF-1-2019, as appropriate, the unit must be tested by relocating the temperature sensors from the locations specified in the figures to avoid interference with hardware or components within the unit, in which case the specific locations used for the temperature sensors shall be noted in the test data records maintained by the manufacturer in accordance with 10 CFR 429.71, and the certification report shall indicate that non-standard sensor locations were used. If any temperature sensor is relocated by any amount from the location prescribed in Figure 5-1 or 5-2 of HRF-1-2019 in order to maintain a minimum 1-inch air space from adjustable shelves or other components that could be relocated by the consumer, except in cases in which the Figures prescribe a temperature sensor location within 1 inch of a shelf or similar feature (e.g., sensor T3 in Figure 5-1), this constitutes a relocation of temperature sensors that must be recorded in the test data and reported in the certification report as described in this paragraph.

5.2. Test Conduct

(a) Standard Approach

(i) For the purposes of comparing compartment temperatures with standardized temperatures, as described in section 5.6 of HRF-1-2019, the freezer compartment temperature shall be as specified in section 5.8.1.2.5 of HRF-1-2019, the fresh food compartment temperature shall be as specified in section 5.8.1.2.4 of HRF-1-2019, and the cooler compartment temperature shall be as specified in section 5.8.1.2.6 of HRF-1-2019.

(ii) In place of Table 5-1 in HRF-1-2019, refer to Table 1 of this section.

Table 1—Temperature Settings: General Chart for All Products

First test Second test Energy
calculation based on:
Setting Results Setting Results Mid for all CompartmentsAll compartments below standard reference temperatureWarmest for all CompartmentsAll compartments below standard reference temperatureSecond Test Only. One or more compartments above standard reference temperatureFirst and Second Test. One or more compartments above standard reference temperatureColdest for all CompartmentsAll compartments below standard reference temperatureFirst and Second Test. One or more compartments above standard reference temperatureModel may not be certified as compliant with energy conservation standards based on testing of this unit. Confirm that unit meets product definition. If so, see section 6 of this appendix.

(b) Three-Point Interpolation Method (Optional Test for Models with Two Compartments and User-Operable Controls). As specified in section 5.6.3(6) of HRF-1-2019, and as an optional alternative to section 5.2(a) of this appendix, perform three tests such that the set of tests meets the “minimum requirements for interpolation” of AS/NZS 4474.1:2007 appendix M, section M3, paragraphs (a) through (c) and as illustrated in Figure M1. The target temperatures txA and txB defined in section M4(a)(i) of AS/NZ 4474.1:2007 shall be the standardized temperatures defined in section 5.6 of HRF-1-2019.

5.3. Test Cycle Energy Calculations

Section 5.8.2, Energy Consumption, of HRF-1-2019 applies to this test procedure, except as follows:

(a) In place of section 5.8.2.1.2 of HRF-1-2019, use the calculations provided in this section. For units with long-time automatic defrost control using the two-part test period, the test cycle energy shall be calculated as:

Where: ET = test cycle energy expended in kilowatt-hours per day; 1440 = conversion factor to adjust to a 24-hour average use cycle in minutes per day; K = dimensionless correction factor of 1.0 for refrigerators and refrigerator-freezers and 0.55 for miscellaneous refrigeration products. EP1 = energy expended in kilowatt-hours during the first part of the test; EP2 = energy expended in kilowatt-hours during the second part of the test; T1 and T2 = length of time in minutes of the first and second test parts, respectively; CT = defrost timer run time or compressor run time between defrosts in hours required to go through a complete cycle, rounded to the nearest tenth of an hour; 12 = factor to adjust for a 50-percent run time of the compressor in hours per day.

(b) In place of sections 5.8.2.1.3 and 5.8.2.1.4 of HRF-1-2019, use the calculations provided in this section. For units with variable defrost control, the test cycle energy shall be calculated as set forth in section 5.3(a) of this appendix with the following addition:

CT shall be calculated equivalent to:

Where: CTL = the least or shortest compressor run time between defrosts used in the variable defrost control algorithm (greater than or equal to 6 but less than or equal to 12 hours), or the shortest compressor run time between defrosts observed for the test (if it is shorter than the shortest run time used in the control algorithm and is greater than 6 hours), or 6 hours (if the shortest observed run time is less than 6 hours), in hours rounded to the nearest tenth of an hour; CTM = the maximum compressor run time between defrosts in hours rounded to the nearest tenth of an hour (greater than CTL but not more than 96 hours); For variable defrost models with no values of CTL and CTM in the algorithm, the default values of 6 and 96 shall be used, respectively. F = ratio of per day energy consumption in excess of the least energy and the maximum difference in per-day energy consumption and is equal to 0.20.

(c) In place of section 5.8.2.1.5 of HRF-1-2019, use the calculations provided in this section. For multiple-compressor products with automatic defrost, the two-part test method in section 5.7.2.1 of HRF-1-2019 shall be used, and the test cycle energy shall be calculated as:

Where: ET, 1440, 12, and K are defined in section 5.3(a) of this appendix; EP1, and T1 are defined in section 5.3(a) of this appendix; i = a subscript variable that can equal 1, 2, or more that identifies each individual compressor system that has automatic defrost; D = the total number of compressor systems with automatic defrost; EP2i = energy expended in kilowatt-hours during the second part of the test for compressor system i; T2i = length of time in minutes of the second part of the test for compressor system i; CTi = compressor run time between defrosts of compressor system i, rounded to the nearest tenth of an hour, for long-time automatic defrost control equal to a fixed time in hours, and for variable defrost control equal to: Where: CTL,i = for compressor system i, the shortest cumulative compressor-on time between defrost heater-on events used in the variable defrost control algorithm (CTL for the compressor system with the longest compressor run time between defrosts must be greater than or equal to 6 but less than or equal to 12 hours), in hours rounded to the nearest tenth of an hour; CTM,i = for compressor system i, the maximum compressor-on time between defrost heater-on events used in the variable defrost control algorithm (greater than CTL,i but not more than 96 hours), in hours rounded to the nearest tenth of an hour; For defrost cycle types with no values of CTL and CTM in the algorithm, the default values of 6 and 96 shall be used, respectively. F = ratio of per day energy consumption in excess of the least energy and the maximum difference in per-day energy consumption and is equal to 0.20.

(d) In place of section 5.8.2.1.6 of HRF-1-2019, use the calculations provided in this section. For units with long-time automatic defrost control and variable defrost control with multiple defrost cycle types, the two-part test method in section 5.7.2.1 of HRF-1-2019 shall be used, and the test cycle energy shall be calculated as:

Where: ET, 1440, 12, and K are defined in section 5.3(a) of this appendix; EP1, and T1 are defined in section 5.3(a) of this appendix; i = a subscript variable that can equal 1, 2, or more that identifies the distinct defrost cycle types applicable for the product; D = the total number of defrost cycle types; EP2i = energy expended in kilowatt-hours during the second part of the test for defrost cycle type i; T2i = length of time in minutes of the second part of the test for defrost cycle type i; CTi = defrost timer run time or compressor run time between instances of defrost cycle type i, rounded to the nearest tenth of an hour; 12 = factor to adjust for a 50-percent run time of the compressor in hours per day.

(i) For long-time automatic defrost control, CTi shall be equal to a fixed time in hours rounded to the nearest tenth of an hour. For cases in which there are more than one fixed CT value for a given defrost cycle type, an average fixed CT value shall be selected for this cycle type.

(ii) For variable defrost control, CTi shall be calculated equivalent to:

Where: CTL,i = the least or shortest compressor run time between instances of the defrost cycle type i in hours rounded to the nearest tenth of an hour (CTL for the defrost cycle type with the longest compressor run time between defrosts must be greater than or equal to 6 but less than or equal to 12 hours); CTM,i = the maximum compressor run time between instances of defrost cycle type i in hours rounded to the nearest tenth of an hour (greater than CTL,i but not more than 96 hours); For cases in which there are more than one CTM and/or CTL value for a given defrost cycle type, an average of the CTM and CTL values shall be selected for this defrost cycle type. For defrost cycle types with no values of CTL and CTM in the algorithm, the default values of 6 and 96 shall be used, respectively. F = ratio of per day energy consumption in excess of the least energy and the maximum difference in per-day energy consumption and is equal to 0.20. 5.4. Icemaker Energy Use

(a) For refrigerators and refrigerator-freezers: To demonstrate compliance with the energy conservation standards at § 430.32(a) applicable to products manufactured on or after September 15, 2014, but before the compliance date of any amended standards published after January 1, 2022, IET, expressed in kilowatt-hours per cycle, equals 0.23 for a product with one or more automatic icemakers and otherwise equals 0 (zero). To demonstrate compliance with any amended standards published after January 1, 2022, IET, expressed in kilowatt-hours per cycle, is as defined in section 5.9.2.1 of HRF-1-2019.

(b) For miscellaneous refrigeration products: To demonstrate compliance with the energy conservation standards at § 430.32(aa) applicable to products manufactured on or after October 28, 2019, IET, expressed in kilowatt-hours per cycle, equals 0.23 for a product with one or more automatic icemakers and otherwise equals 0 (zero).

5.5. Triangulation Method

If the three-point interpolation method of section 5.2(b) of this appendix is used for setting temperature controls, the average per-cycle energy consumption shall be defined as follows:

E = EX + IET Where: E is defined in section 5.9.1.1 of HRF-1-2019; IET is defined in section 5.4 of this appendix; and EX is defined and calculated as described in appendix M, section M4(a) of AS/NZS 4474.1:2007. The target temperatures txA and txB defined in section M4(a)(i) of AS/NZS 4474.1:2007 shall be the standardized temperatures defined in section 5.6 of HRF-1-2019. 6. Test Procedure Waivers

To the extent that the procedures contained in this appendix do not provide a means for determining the energy consumption of a basic model, a manufacturer must obtain a waiver under § 430.27 to establish an acceptable test procedure for each such basic model. Such instances could, for example, include situations where the test setup for a particular basic model is not clearly defined by the provisions of this appendix. For details regarding the criteria and procedures for obtaining a waiver, please refer to § 430.27.

[86 FR 56821, Oct. 12, 2021, as amended at 89 FR 3112, Jan. 17, 2024]

Appendix B - Appendix B to Subpart B of Part 430—Uniform Test Method for Measuring the Energy Consumption of Freezers

Note:

Prior to April 11, 2022, any representations of volume and energy use of freezers must be based on the results of testing pursuant to either this appendix or the procedures in appendix B as it appeared at 10 CFR part 430, subpart B, appendix B, in the 10 CFR parts 200 to 499 edition revised as of January 1, 2019. Any representations of volume and energy use must be in accordance with whichever version is selected. On or after April 11, 2022, any representations of volume and energy use must be based on the results of testing pursuant to this appendix.

For freezers, the rounding requirements specified in sections 4 and 5 of this appendix are not required for use until the compliance date of any amendment of energy conservation standards for these products published after October 12, 2021.

1. Referenced Materials

DOE incorporated by reference HRF-1-2019, Energy and Internal Volume of Consumer Refrigeration Products (“HRF-1-2019”) in its entirety in § 430.3; however, only enumerated provisions of this document are applicable to this appendix. If there is any conflict between HRF-1-2019 and this appendix, follow the language of the test procedure in this appendix, disregarding the conflicting industry standard language.

(a) AHAM HRF-1-2019, (“HRF-1-2019”), Energy and Internal Volume of Consumer Refrigeration Products:

(i) Section 3—Definitions, as specified in section 3 of this appendix;

(ii) Section 4—Method for Determining the Refrigerated Volume of Consumer Refrigeration Products, as specified in section 4.1 of this appendix;

(iii) Section 5—Method for Determining the Energy Consumption of Consumer Refrigeration Products (excluding Table 5-1 and sections 5.5.6.5, 5.8.2.1.2, 5.8.2.1.3, 5.8.2.1.4, 5.8.2.1.5, and 5.8.2.1.6), as specified in section 5 of this appendix; and

(iv) Section 6—Method for Determining the Adjusted Volume of Consumer Refrigeration Products, as specified in section 4.2 of this appendix.

(b) Reserved.

If there is any conflict between HRF-1—2019 and this appendix, follow the language of the test procedure in this appendix, disregarding the conflicting industry standard language.

2. Scope

This appendix provides the test procedure for measuring the annual energy use in kilowatt-hours per year (kWh/yr), the total refrigerated volume in cubic feet (ft 3), and the total adjusted volume in cubic feet (ft 3) of freezers.

3. Definitions

Section 3, Definitions, of HRF-1-2019 applies to this test procedure. In case of conflicting terms between HRF-1-2019 and DOE's definitions in this appendix or in § 430.2, DOE's definitions take priority.

Through-the-door ice/water dispenser means a device incorporated within the cabinet, but outside the boundary of the refrigerated space, that delivers to the user on demand ice and may also deliver water from within the refrigerated space without opening an exterior door. This definition includes dispensers that are capable of dispensing ice and water or ice only.

4. Volume

Determine the refrigerated volume and adjusted volume for freezers in accordance with the following sections of HRF-1-2019, respectively:

4.1. Section 4, Method for Determining the Refrigerated Volume of Consumer Refrigeration Products; and

4.2. Section 6, Method for Determining the Adjusted Volume of Consumer Refrigeration Products.

5. Energy Consumption

Determine the annual energy use (“AEU”) in kilowatt-hours per year (kWh/yr), for freezers in accordance with section 5, Method for Determining the Energy Consumption of Consumer Refrigeration Products, of HRF-1-2019, except as follows.

5.1. Test Setup and Test Conditions

(a) In section 5.3.1 of HRF-1-2019, the top of the unit shall be determined by the refrigerated cabinet height, excluding any accessories or protruding components on the top of the unit.

(b) The ambient temperature and vertical ambient temperature gradient requirements specified in section 5.3.1 of HRF-1-2019 shall be maintained during both the stabilization period and the test period.

(c) The power supply requirements as specified in section 5.5.1 of HRF-1-2019 shall be maintained based on measurement intervals not to exceed one minute.

(d) The ice storage compartment temperature requirement as specified in section 5.5.6.5 in HRF-1-2019 is not required.

(e) For cases in which setup is not clearly defined by this test procedure, manufacturers must submit a petition for a waiver (See section 6 of this appendix).

(f) If the interior arrangements of the unit under test do not conform with those shown in Figure 5-2 of HRF-1-2019, as appropriate, the unit must be tested by relocating the temperature sensors from the locations specified in the figures to avoid interference with hardware or components within the unit, in which case the specific locations used for the temperature sensors shall be noted in the test data records maintained by the manufacturer in accordance with 10 CFR 429.71, and the certification report shall indicate that non-standard sensor locations were used. If any temperature sensor is relocated by any amount from the location prescribed in Figure 5-2 of HRF-1- 2019 in order to maintain a minimum 1-inch air space from adjustable shelves or other components that could be relocated by the consumer, except in cases in which the Figure prescribes a temperature sensor location within 1 inch of a shelf or similar feature, this constitutes a relocation of temperature sensors that must be recorded in the test data and reported in the certification report as described in this paragraph.

5.2. Test Conduct

(a) For the purposes of comparing compartment temperatures with standardized temperatures, as described in section 5.6 of HRF-1-2019, the freezer compartment temperature shall be as specified in section 5.8.1.2.5 of HRF-1-2019.

(b) In place of Table 5-1 in HRF-1-2019, refer to Table 1 of this section.

Table 1—Temperature Settings for Freezers

First test Second test Energy calculation based on: Setting Results Setting Results MidBelow standard reference temperatureWarmestBelow standard reference temperatureSecond Test Only. Above standard reference temperatureFirst and Second Test. Above standard reference temperatureColdestBelow standard reference temperatureFirst and Second Test. Above standard reference temperatureModel may not be certified as compliant with energy conservation standards based on testing of this unit. Confirm that unit meets product definition. If so, see section 6 of this appendix.
5.3. Test Cycle Energy Calculations

Section 5.8.2, Energy Consumption, of HRF-1-2019 applies to this test procedure, except as follows:

(a) In place of section 5.8.2.1.2 of HRF-1-2019, use the calculations provided in this section. For units with long-time automatic defrost control using the two-part test period, the test cycle energy shall be calculated as:

Where: ET = test cycle energy expended in kilowatt-hours per day; 1440 = conversion factor to adjust to a 24-hour average use cycle in minutes per day; K = dimensionless correction factor of 0.7 for chest freezers and 0.85 for upright freezers. EP1 = energy expended in kilowatt-hours during the first part of the test; EP2 = energy expended in kilowatt-hours during the second part of the test; T1 and T2 = length of time in minutes of the first and second test parts, respectively; CT = defrost timer run time or compressor run time between defrosts in hours required to go through a complete cycle, rounded to the nearest tenth of an hour; 12 = factor to adjust for a 50-percent run time of the compressor in hours per day.

(b) In place of sections 5.8.2.1.3 and 5.8.2.1.4 of HRF-1-2019, use the calculations provided in this section. For units with variable defrost control, the test cycle energy shall be calculated as set forth in section 5.3(a) of this appendix with the following addition:

CT shall be calculated equivalent to:

Where: CTL = the least or shortest compressor run time between defrosts used in the variable defrost control algorithm (greater than or equal to 6 but less than or equal to 12 hours), or the shortest compressor run time between defrosts observed for the test (if it is shorter than the shortest run time used in the control algorithm and is greater than 6 hours), or 6 hours (if the shortest observed run time is less than 6 hours), in hours rounded to the nearest tenth of an hour; CTM = the maximum compressor run time between defrosts in hours rounded to the nearest tenth of an hour (greater than CTL but not more than 96 hours); For variable defrost models with no values of CTL and CTM in the algorithm, the default values of 6 and 96 shall be used, respectively. F = ratio of per day energy consumption in excess of the least energy and the maximum difference in per-day energy consumption and is equal to 0.20. 6. Test Procedure Waivers

To the extent that the procedures contained in this appendix do not provide a means for determining the energy consumption of a basic model, a manufacturer must obtain a waiver under § 430.27 to establish an acceptable test procedure for each such basic model. Such instances could, for example, include situations where the test setup for a particular basic model is not clearly defined by the provisions of this appendix. For details regarding the criteria and procedures for obtaining a waiver, please refer to § 430.27.

5.4. Icemaker Energy Use

For freezers: To demonstrate compliance with the energy conservation standards at § 430.32(a) applicable to products manufactured on or after September 15, 2014, but before the compliance date of any amended standards published after January 1, 2022, IET, expressed in kilowatt-hours per cycle, equals 0.23 for a product with one or more automatic icemakers and otherwise equals 0 (zero). To demonstrate compliance with any amended standards published after January 1, 2022, IET, expressed in kilowatt-hours per cycle, is as defined in section 5.9.2.1 of HRF-1-2019.

[86 FR 56824, Oct. 12, 2021, as amended at 89 FR 3113, Jan. 17, 2024]

Appendix C1 - Appendix C1 to Subpart B of Part 430—Uniform Test Method for Measuring the Energy Consumption of Dishwashers

Note:

Manufacturers must use the results of testing under this appendix to determine compliance with the relevant standards provided at § 430.32(f)(1).

Manufacturers must use the results of testing under appendix C2 to this subpart to determine compliance with the amended standards for dishwashers provided at § 430.32(f)(2). Manufacturers may use appendix C2 to certify compliance with the standards provided at § 430.32(f)(2) prior to the applicable compliance date for those standards.

Any representations related to energy or water consumption of dishwashers must be made in accordance with the appropriate appendix that applies (i.e., appendix C1 or appendix C2) when determining compliance with the relevant standards.

The regulation at 10 CFR 429.19(b)(3) provides instructions regarding the combination of detergent and detergent dosing, specified in section 2.5 of this appendix, used for certification.

0. Incorporation by Reference

In § 430.3, DOE incorporated by reference the entire standard for AHAM DW-1-2020 and AHAM DW-2-2020; however, only enumerated provision of AHAM DW-1-2020, AHAM DW-2-2020, and IEC 62301 are applicable as follows:

0.1 AHAM DW-1-2020

(a) Sections 1.1 through 1.30 as referenced in section 1 of this appendix;

(b) Section 2.1 as referenced in sections 2 and 2.1 of this appendix;

(c) Sections 2.2 through 2.3.3, sections 2.5 through 2.7, sections 2.7.2 through 2.8, and section 2.11, as referenced in section 2 of this appendix;

(d) Section 2.4 as referenced in sections 2 and 2.2 of this appendix;

(e) Section 2.7.1 as referenced in sections 2 and 2.3 of this appendix;

(f) Section 2.9 as referenced in sections 2 and 2.4 of this appendix;

(g) Section 2.10 as referenced in sections 2 and 2.5 of this appendix;

(h) Sections 3.1 through 3.2 and sections 3.5 through 3.7 as referenced in section 3 of this appendix;

(i) Section 3.3 as referenced in sections 3 and 3.1 of this appendix;

(j) Section 3.4 as referenced in sections 3 and 3.2 of this appendix;

(k) Sections 4.1 through 4.1.2 and sections 4.1.4 through 4.2 as referenced in section 4 of this appendix;

(l) Section 4.1.4 as referenced in sections 4 and 4.1 of this appendix; and

(m) Section 5 as referenced in section 5 of this appendix.

0.2 AHAM DW-2-2020: Household Electric Dishwashers

(a) Section 3.4 as referenced in sections 2 and 2.3 of this appendix, and through reference to sections 1.5 and 1.22 of AHAM DW-1-2020 in section 1 of this appendix.

(b) Section 3.5 through reference to sections 1.5 and 1.22 of AHAM DW-1-2020 in section 1 of this appendix.

(c) Section 4.1 as referenced in section 2 of this appendix.

(d) Sections 5.3 through 5.8 as referenced in section 2 of this appendix, and through reference to sections 1.18, 1.19, and 1.20 of AHAM DW-1-2020 in section 1 of this appendix.

0.3 IEC 62301

(a) Sections 4.2, 4.3.2, and 5.2 as referenced in section 2 of this appendix; and

(b) Sections 5.1, note 1, and 5.3.2 as referenced in section 4 of this appendix.

1. Definitions

The definitions in sections 1.1 through 1.30 of AHAM DW-1-2020 apply to this test procedure, including the applicable provisions of AHAM DW-2-2020 as referenced in sections 1.5, 1.18, 1.19. 1.20, and 1.22 of AHAM DW-1-2020.

2. Testing Conditions

The testing conditions in sections 2.1 through 2.11 of AHAM DW-1-2020 apply to this test procedure, including the following provisions of:

(a) Sections 5.2, 4.3.2, and 4.2 of IEC 62301 as referenced in sections 2.1, 2.2.4, and 2.5.2 of AHAM DW-1-2020, respectively, and

(b) Sections 5.3 through 5.8 of AHAM DW-2-2020 as referenced in sections 2.6.3.1, 2.6.3.2, and 2.6.3.3 of AHAM DW-1-2020; section 3.4 of AHAM DW-2-2020, excluding the accompanying Note, as referenced in section 2.7.1 of AHAM DW-1-2020; section 5.4 of AHAM DW-2-2020 as referenced in section 2.7.4 of AHAM DW-1-2020; section 5.5 of AHAM DW-2-2020 as referenced in section 2.7.5 of AHAM DW-1-2020, and section 4.1 of AHAM DW-2-2020 as referenced in section 2.10.1 of AHAM DW-1-2020. Additionally, the following requirements are also applicable.

2.1 Installation Requirements.

The installation requirements described in section 2.1 of AHAM DW-1-2020 are applicable to all dishwashers, with the following additions:

2.1.1 In-Sink Dishwashers.

For in-sink dishwashers, the requirements pertaining to the rectangular enclosure for under-counter or under-sink dishwashers are not applicable. For such dishwashers, the rectangular enclosure must consist of a front, a back, two sides, and a bottom. The front, back, and sides of the enclosure must be brought into the closest contact with the appliance that the configuration of the dishwasher will allow. The height of the enclosure shall be as specified in the manufacturer's instructions for installation height. If no instructions are provided, the enclosure height shall be 36 inches. The dishwasher must be installed from the top and mounted to the edges of the enclosure.

2.1.2 Dishwashers without a Direct Water Line.

Manually fill the built-in water reservoir to the full capacity reported by the manufacturer, using water at a temperature in accordance with section 2.3 of AHAM DW-1-2020.

2.2 Water pressure.

The water pressure requirements described in section 2.4 of AHAM DW-1-2020 are applicable to all dishwashers except dishwashers that do not have a direct water line.

2.3 Test load items.

The test load items described in section 2.7.1 of AHAM DW-1-2020 apply to this test procedure, including the applicable provisions of section 3.4 of AHAM DW-2-2020, as referenced in section 2.7.1 of AHAM DW-1-2020. The following test load items may be used in the alternative.

Dishware/glassware/flatware item Primary source Description Primary No. Alternate source Alternate source No. Dinner PlateCorning Comcor®/Corelle®10 inch Dinner Plate6003893 Bread and Butter PlateCorning Comcor®/Corelle®6.75 inch Bread & Butter6003887Arzberg8500217100 or 2000-00001-0217-1. Fruit BowlCorning Comcor®/Corelle®10 oz. Dessert Bowl6003899Arzberg3820513100. CupCorning Comcor®/Corelle®8 oz. Ceramic Cup6014162Arzberg1382-00001-4732. SaucerCorning Comcor®/Corelle®6 inch Saucer6010972Arzberg1382-00001-4731. Serving BowlCorning Comcor®/Corelle®1 qt. Serving Bowl6003911 PlatterCorning Comcor®/Corelle®9.5 inch Oval Platter6011655 Glass—Iced TeaLibbey551 HT Flatware—KnifeOneida®—Accent2619KPVFWMF—Gastro 080012.0803.6047. Flatware—Dinner ForkOneida®—Accent2619FRSFWMF—Signum 190012.1905.6040. Flatware—Salad ForkOneida®—Accent2619FSLFWMF—Signum 190012.1964.6040. Flatware—TeaspoonOneida®—Accent2619STSFWMF—Signum 190012.1910.6040. Flatware—Serving ForkOneida®—Flight2865FCMWMF—Signum 190012.1902.6040. Flatware—Serving SpoonOneida®—Accent2619STBFWMF—Signum 190012.1904.6040.

2.4 Preconditioning requirements.

The preconditioning requirements described in section 2.9 of AHAM DW-1-2020 are applicable to all dishwashers. For dishwashers that do not have a direct water line, measurement of the prewash fill water volume, Vpw, if any, and measurement of the main wash fill water volume, Vmw, are not taken.

2.5 Detergent.

2.5.1 Detergent Formulation. Either Cascade with the Grease Fighting Power of Dawn or Cascade Complete Powder may be used.

2.5.2 Detergent Dosage.

2.5.2.1 Dosage for any dishwasher other than water re-use system dishwashers.

If Cascade with the Grease Fighting Power of Dawn detergent is used, the detergent dosing specified in section 2.5.2.1.1 of this appendix must be used.

If Cascade Complete Powder detergent is used, consult the introductory note to this appendix regarding use of the detergent dosing specified in either section 2.5.2.1.1 or section 2.5.2.1.2 of this appendix.

2.5.2.1.1 Dosage based on fill water volumes. Determine detergent dosage as follows:

Prewash Detergent Dosing. If the cycle setting for the test cycle includes prewash, determine the quantity of dry prewash detergent, Dpw, in grams (g) that results in 0.25 percent concentration by mass in the prewash fill water as:

Dpw = Vpw × ρ × k × 0.25/100 where, Vpw = the prewash fill volume of water in gallons, ρ = water density = 8.343 pounds (lb)/gallon for dishwashers to be tested at a nominal inlet water temperature of 50 °F (10 °C), 8.250 lb/gallon for dishwashers to be tested at a nominal inlet water temperature of 120 °F (49 °C), and 8.205 lb/gallon for dishwashers to be tested at a nominal inlet water temperature of 140 °F (60 °C), and k = conversion factor from lb to g = 453.6 g/lb.

Main Wash Detergent Dosing. Determine the quantity of dry main wash detergent, Dmw, in grams (g) that results in 0.25 percent concentration by mass in the main wash fill water as:

Dmw = Vmw × ρ × k × 0.25/100 where, Vmw = the main wash fill volume of water in gallons, and ρ and k are as defined above.

For dishwashers that do not have a direct water line, Vmw is equal to the manufacturer reported water capacity used in the main wash stage of the test cycle.

2.5.2.1.2 Dosage based on number of place settings. Determine detergent dosage as specified in sections 2.10 and 2.10.1 of AHAM DW-1-2020.

2.5.2.2 Dosage for water re-use system dishwashers. Determine detergent dosage as specified in section 2.10.2 of AHAM DW-1-2020.

2.5.3 Detergent Placement.

Prewash and main wash detergent must be placed as specified in sections 2.10 and 2.10.1 of AHAM DW-1-2020. For any dishwasher that does not have a main wash detergent compartment and the manufacturer does not recommend a location to place the main wash detergent, place the main wash detergent directly into the dishwasher chamber.

2.6 Connected functionality.

For dishwashers that can communicate through a network (e.g., Bluetooth® or internet connection), disable all network functions that can be disabled by means provided in the manufacturer's user manual, for the duration of testing. If network functions cannot be disabled by means provided in the manufacturer's user manual, conduct the standby power test with network function in the “as-shipped” condition.

3. Instrumentation

For this test procedure, the test instruments are to be calibrated annually according to the specifications in sections 3.1 through 3.7 of AHAM DW-1-2020, including the applicable provisions of IEC 62301 as referenced in section 3.6 of AHAM DW-1-2020. Additionally, the following requirements are also applicable.

3.1 Water meter.

The water meter requirements described in section 3.3 of AHAM DW-1-2020 are applicable to all dishwashers except dishwashers that do not have a direct water line. For such dishwashers these water meter conditions do not apply and water is added manually pursuant to section 2.1.1 of this appendix.

3.2 Water pressure gauge.

The water pressure gauge requirements described in section 3.4 of AHAM DW-1-2020 are applicable to all dishwashers except dishwashers that do not have a direct water line. For such dishwashers these water pressure gauge conditions do not apply and water is added manually pursuant to section 2.1.1 of this appendix.

4. Test Cycle and Measurements

The test cycle and measurement specifications in sections 4.1 through 4.2 of AHAM DW-1-2020 apply to this test procedure, including section 5.1, note 1, and section 5.3.2 of IEC 62301 as referenced in section 4.2 of AHAM DW-1-2020. Additionally, the following requirements are also applicable.

4.1 Water consumption.

The water consumption requirements described in section 4.1.4 of AHAM DW-1-2020 are applicable to all dishwashers except dishwashers that do not have a direct water line. For such dishwashers these water consumption measurement requirements do not apply and water consumption, V, is the value reported by the manufacturer.

5. Calculation of Derived Results From Test Measurements

The calculations in section 5.1 through 5.7 of AHAM DW-1-2020 apply to this test procedure. The following additional requirements are also applicable:

(a) In sections 5.1.3, 5.1.4, 5.1.5, 5.4.3, 5.4.4, 5.4.5, and 5.7 of AHAM DW-1-2020, use N = 215 cycles/year in place of N = 184 cycles/year.

(b) In section 5.7 of AHAM DW-1-2020, use SLP = 8,465 for dishwashers that are not capable of operating in fan-only mode.

(c) For dishwashers that do not have a direct water line, water consumption is equal to the volume of water use in the test cycle, as specified by the manufacturer.

(d) In sections 5.6.1.3, 5.6.1.4, 5.6.2.3, and 5.6.2.4 of AHAM DW-1-2020, use (C/e) in place of K.

[88 FR 3277, Jan. 18, 2023, as amended at 88 FR 48357, July 27, 2023; 89 FR 83617, Oct. 17, 2024]

Appendix C2 - Appendix C2 to Subpart B of Part 430—Uniform Test Method for Measuring the Energy Consumption of Dishwashers

Note:

Manufacturers must use the results of testing under this appendix to determine compliance with the relevant standards provided at § 430.32(f)(2). Manufacturers may use this appendix to certify compliance with the standards provided at § 430.32(f)(2) prior to the applicable compliance date for those standards.

Any representations related to energy or water consumption of dishwashers must be made in accordance with the appropriate appendix that applies (i.e., appendix C1 or appendix C2) when determining compliance with the relevant standards.

0. Incorporation by Reference

In § 430.3, DOE incorporated by reference the entire standard for AHAM DW-1-2020 and AHAM DW-2-2020; however, only enumerated provision of AHAM DW-1-2020, AHAM DW-2-2020, and IEC 62301 are applicable as follows:

0.1 AHAM DW-1-2020

(a) Sections 1.1 through 1.30 as referenced in section 1 of this appendix;

(b) Section 2.1 as referenced in sections 2 and 2.1 of this appendix;

(c) Sections 2.2 through 2.3.3, sections 2.5 and 2.7, sections 2.7.2 through 2.8, and section 2.11, as referenced in section 2 of this appendix;

(d) Section 2.4 as referenced in sections 2 and 2.2 of this appendix;

(e) Section 2.6.3 as referenced in sections 2 and 2.3 of this appendix;

(f) Section 2.7.1 as referenced in sections 2 and 2.4 of this appendix;

(g) Section 2.9 as referenced in sections 2 and 2.5 of this appendix;

(h) Section 2.10 as referenced in sections 2 and 2.6 of this appendix;

(i) Sections 3.1 through 3.2 and sections 3.5 through 3.7 as referenced in section 3 of this appendix;

(j) Section 3.3 as referenced in sections 3 and 3.1 of this appendix;

(k) Section 3.4 as referenced in sections 3 and 3.2 of this appendix;

(l) Section 4.1 as referenced in sections 4 and 4.1 of this appendix;

(m) Section 4.1.4 as referenced in sections 4 and 4.1.2 of this appendix; and

(n) Section 5 as referenced in section 5 of this appendix.

0.2 AHAM DW-2-2020

(a) Section 3.4 as referenced in sections 2 and 2.4 of this appendix, and through reference to sections 1.5 and 1.22 of AHAM DW-1-2020 in section 1 of this appendix.

(b) Section 3.5 through reference to sections 1.5 and 1.22 of AHAM DW-1-2020 in section 1 of this appendix.

(c) Section 4.1 as referenced in section 2 of this appendix.

(d) Sections 5.3 through 5.8 as referenced in section 2 of this appendix, and through reference to sections 1.18, 1.19 and 1.20 of AHAM DW-1-2020 in section 1 of this appendix.

(e) Section 5.10 as referenced in sections 2 and 2.8 of this appendix;

(f) Sections 5.10.1.1 as referenced in sections 4 and 4.2 of this appendix; and

(g) Section 5.12.3.1 as referenced in sections 5 and 5.1 of this appendix.

0.3 IEC 62301

(a) Sections 4.2, 4.3.2, and 5.2 as referenced in section 2 of this appendix; and

(b) Sections 5.1, note 1, and 5.3.2 as referenced in section 4 of this appendix.

1. Definitions

The definitions in sections 1.1 through 1.30 of AHAM DW-1-2020 apply to this test procedure, including the applicable provisions of AHAM DW-2-2020 as referenced in sections 1.5, 1.18, 1.19, 1.20, and 1.22 of AHAM DW-1-2020.

2. Testing Conditions

The testing conditions in Section 2.1 through 2.11 of AHAM DW-1-2020, except sections 2.6.1 and 2.6.2, and the testing conditions in section 5.10 of AHAM DW-2-2020 apply to this test procedure, including the following provisions of:

(a) Sections 5.2, 4.3.2, and 4.2 of IEC 62301 as referenced in sections 2.1, 2.2.4, and 2.5.2 of AHAM DW-1-2020, respectively, and

(b) Sections 5.3 through 5.8 of AHAM DW-2-2020 as referenced in sections 2.6.3.1, 2.6.3.2, and 2.6.3.3 of AHAM DW-1-2020; section 3.4 of AHAM DW-2-2020, excluding the accompanying Note, as referenced in section 2.7.1 of AHAM DW-1-2020; section 5.4 of AHAM DW-2-2020 as referenced in section 2.7.4 of AHAM DW-1-2020; section 5.5 of AHAM DW-2-2020 as referenced in section 2.7.5 of AHAM DW-1-2020, and section 4.1 of AHAM DW-2-2020 as referenced in section 2.10.1 of AHAM DW-1-2020. Additionally, the following requirements are also applicable.

2.1 Installation Requirements.

The installation requirements described in section 2.1 of AHAM DW-1-2020 are applicable to all dishwashers, with the following additions:

2.1.1 In-Sink Dishwashers.

For in-sink dishwashers, the requirements pertaining to the rectangular enclosure for under-counter or under-sink dishwashers are not applicable. For such dishwashers, the rectangular enclosure must consist of a front, a back, two sides, and a bottom. The front, back, and sides of the enclosure must be brought into the closest contact with the appliance that the configuration of the dishwasher will allow. The height of the enclosure shall be as specified in the manufacturer's instructions for installation height. If no instructions are provided, the enclosure height shall be 36 inches. The dishwasher must be installed from the top and mounted to the edges of the enclosure.

2.1.2 Dishwashers without a Direct Water Line.

Manually fill the built-in water reservoir to the full capacity reported by the manufacturer, using water at a temperature in accordance with section 2.3 of AHAM DW-1-2020.

2.2 Water pressure.

The water pressure requirements described in section 2.4 of AHAM DW-1-2020 are applicable to all dishwashers except dishwashers that do not have a direct water line.

2.3 Non-soil-sensing and soil-sensing dishwashers to be tested at a nominal inlet temperature of 50 °F, 120 °F, or 140 °F.

The test load and soiling requirements for all non-soil-sensing and soil-sensing dishwashers shall be the same as those requirements specified in section 2.6.3 of AHAM DW-1-2020 for soil-sensing dishwashers. Additionally, both non-soil-sensing and soil-sensing compact dishwashers that have a capacity of less than four place settings shall be tested at the rated capacity of the dishwasher and the test load shall be soiled as follows at each soil load:

(a) Heavy soil load: soil two-thirds of the place settings, excluding flatware and serving pieces (rounded up to the nearest integer) or one place setting, whichever is greater;

(b) Medium soil load: soil one-quarter of the place settings, excluding flatware and serving pieces (rounded up to the nearest integer) or one place setting, whichever is smaller;

(c) Light soil load: soil one-quarter of the place settings, excluding flatware and serving pieces (rounded up to the nearest integer) or one place setting, whichever is smaller, using half the quantity of soils specified for one place setting.

2.4 Test load items.

The test load items described in section 2.7.1 of AHAM DW-1-2020 apply to this test procedure, including the applicable provisions of section 3.4 of AHAM DW-2-2020, as referenced in section 2.7.1 of AHAM DW-1-2020. The following test load items may be used in the alternative.

Dishware/glassware/flatware item Primary source Description Primary No. Alternate source Alternate source No. Dinner PlateCorning Comcor®/Corelle®10 inch Dinner Plate6003893 Bread and Butter PlateCorning Comcor®/Corelle®6.75 inch Bread & Butter6003887Arzberg8500217100 or 2000-00001-0217-1. Fruit BowlCorning Comcor®/Corelle®10 oz. Dessert Bowl6003899Arzberg3820513100. CupCorning Comcor®/Corelle®8 oz. Ceramic Cup6014162Arzberg1382-00001-4732. SaucerCorning Comcor®/Corelle®6 inch Saucer6010972Arzberg1382-00001-4731. Serving BowlCorning Comcor®/Corelle®1 qt. Serving Bowl6003911 PlatterCorning Comcor®/Corelle®9.5 inch Oval Platter6011655 Glass—Iced TeaLibbey551 HT Flatware—KnifeOneida®—Accent2619KPVFWMF—Gastro 080012.0803.6047. Flatware—Dinner ForkOneida®—Accent2619FRSFWMF—Signum 190012.1905.6040. Flatware—Salad ForkOneida®—Accent2619FSLFWMF—Signum 190012.1964.6040. Flatware—TeaspoonOneida®—Accent2619STSFWMF—Signum 190012.1910.6040. Flatware—Serving ForkOneida®—Flight2865FCMWMF—Signum 190012.1902.6040. Flatware—Serving SpoonOneida®—Accent2619STBFWMF—Signum 190012.1904.6040.

2.5 Preconditioning requirements.

The preconditioning requirements described in section 2.9 of AHAM DW-1-2020 are applicable to all dishwashers except the measurement of the prewash fill water volume, Vpw, if any, and measurement of the main wash fill water volume, Vmw, are not required.

2.6 Detergent.

The detergent requirements described in section 2.10 of AHAM DW-1-2020 are applicable to all dishwashers. For any dishwasher that does not have a main wash detergent compartment and the manufacturer does not recommend a location to place the main wash detergent, place the detergent directly into the dishwasher chamber.

2.7 Connected functionality.

For dishwashers that can communicate through a network (e.g., Bluetooth® or internet connection), disable all network functions that can be disabled by means provided in the manufacturer's user manual, for the duration of testing. If network functions cannot be disabled by means provided in the manufacturer's user manual, conduct the standby power test with network function in the “as-shipped” condition.

2.8 Evaluation Room Lighting Conditions.

The lighting setup in the evaluation room where the test load is scored shall be according to the requirements specified in section 5.10 of AHAM DW-2-2020.

3. Instrumentation

For this test procedure, the test instruments are to be calibrated annually according to the specifications in section 3.1 through 3.7 of AHAM DW-1-2020, including the applicable provisions of IEC 62301 as referenced in section 3.6 of AHAM DW-1-2020. Additionally, the following requirements are also applicable.

3.1 Water meter.

The water meter requirements described in section 3.3 of AHAM DW-1-2020 are applicable to all dishwashers except dishwashers that do not have a direct water line. For such dishwashers these water meter conditions do not apply and water is added manually pursuant to section 2.1.1 of this appendix.

3.2 Water pressure gauge.

The water pressure gauge requirements described in section 3.4 of AHAM DW-1-2020 are applicable to all dishwashers except dishwashers that do not have a direct water line. For such dishwashers these water pressure gauge conditions do not apply and water is added manually pursuant to section 2.1.1 of this appendix.

4. Test Cycle and Measurements

The test cycle and measurement specifications in sections 4.1 through 4.2 of AHAM DW-1-2020 and the scoring specifications in section 5.10.1.1 of AHAM DW-2-2020 apply to this test procedure, including section 5.1, note 1, and section 5.3.2 of IEC 62301 as referenced in section 4.2 of AHAM DW-1-2020. Additionally, the following requirements are also applicable.

4.1 Active mode cycle.

The active mode energy consumption measurement requirements described in section 4.1 of AHAM DW-1-2020 are applicable to all dishwashers. Additionally, the following requirements are also applicable:

(a) After the completion of each test cycle (sensor heavy response, sensor medium response, and sensor light response), the test load shall be scored according to section 4.2 of this appendix and its cleaning index calculated according to section 5.1 of this appendix.

(b) A test cycle is considered valid if its cleaning index is 70 or higher; otherwise, the test cycle is invalid and the data from that test run is discarded.

(c) For soil-sensing dishwashers, if the test cycle at any soil load is invalid, clean the dishwasher filter according to manufacturer's instructions and repeat the test at that soil load on the most energy-intensive cycle (determined as provided in section 4.1.1 of this appendix) that achieves a cleaning index of 70 or higher.

(d) For non-soil-sensing dishwashers, perform testing as described in section 4.1.a through 4.1.c of this appendix, except that, if a test cycle at a given soil load meets the cleaning index threshold criteria of 70 when tested on the normal cycle, no further testing is required for test cycles at lesser soil loads.

4.1.1 Determination of most energy-intensive cycle.

If the most energy-intensive cycle is not known and needs to be determined via testing, ensure the filter is cleaned as specified in the manufacturer's instructions and test each available cycle type, selecting the default cycle options for that cycle type. In the absence of manufacturer recommendations on washing and drying temperature options, the highest energy consumption options must be selected. Following the completion of each test cycle, the machine electrical energy consumption and water consumption shall be measured according to sections 4.1.1 and 4.1.4 of AHAM DW-1-2020, respectively. The total cycle energy consumption, EMEI, of each tested cycle type shall be calculated according to section 5.2 of this appendix. The most energy-intensive cycle is the cycle type with the highest value of EMEI.

For standard dishwashers, test each cycle with a clean load of eight place settings plus six serving pieces, as specified in section 2.7 of AHAM DW-1-2020. For compact dishwashers, test each cycle with a clean load of four place settings plus six serving pieces, as specified in section 2.7 of AHAM DW-1-2020. If the capacity of the dishwasher, as stated by the manufacturer, is less than four place settings, then the test load must be the stated capacity.

4.1.2 Water consumption.

The water consumption requirements described in section 4.1.4 of AHAM DW-1-2020 are applicable to all dishwashers except dishwashers that do not have a direct water line. For such dishwashers these water consumption measurement requirements do not apply and water consumption, V, is the value reported by the manufacturer.

4.2 Scoring.

Following the termination of an active mode test, each item in the test load shall be scored on a scale from 0 to 9 according to the instructions in section 5.10.1.1 of AHAM DW-2-2020.

5. Calculation of Derived Results From Test Measurements

The calculations in sections 5.1 through 5.7 of AHAM DW-1-2020 and section 5.12.3.1 of AHAM DW-2-2020 apply to this test procedure. The following additional requirements are also applicable:

(a) For both soil-sensing and non-soil-sensing dishwashers, use the equations specified for soil-sensing dishwashers.

(b) If a non-soil-sensing dishwasher is not tested at a certain soil load as specified in section 4.1.d of this appendix, use the energy and water consumption values of the preceding soil load when calculating the weighted average energy and water consumption values (i.e., if the sensor medium response and sensor light response tests on the normal cycle are not conducted, use the values of the sensor heavy response test for all three soil loads; if only the sensor light response test is not conducted, use the values of the sensor medium response test for the sensor light response test).

(c) For dishwashers that do not have a direct water line, water consumption is equal to the volume of water use in the test cycle, as specified by the manufacturer.

(d) In sections 5.6.1.3, 5.6.1.4, 5.6.2.3, and 5.6.2.4 of AHAM DW-1-2020, use (C/e) in place of K.

5.1 Cleaning Index.

Determine the per-cycle cleaning index for each test cycle using the equation in section 5.12.3.1 of AHAM DW-2-2020.

5.2 Calculation for determination of the most energy-intensive cycle type.

The total cycle energy consumption for the determination of the most energy-intensive cycle specified in section 4.1.1 of this appendix is calculated for each tested cycle type as:

EMEI = M + EF−(ED/2) + W where, M = per-cycle machine electrical energy consumption, expressed in kilowatt hours per cycle, EF = fan-only mode electrical energy consumption, if available on the tested cycle type, expressed in kilowatt hours per cycle, ED = drying energy consumed using the power-dry feature after the termination of the last rinse option of the tested cycle type, if available on the tested cycle type, expressed in kilowatt hours per cycle, and W = water energy consumption and is defined as: V × T × K, for dishwashers using electrically heated water, and V × T × C/e, for dishwashers using gas-heated or oil-heated water.

Additionally,

V = water consumption in gallons per cycle, T = nominal water heater temperature rise and is equal to 90 °F for dishwashers that operate with a nominal 140 °F inlet water temperature, and 70 °F for dishwashers that operate with a nominal 120 °F inlet water temperature, K = specific heat of water in kilowatt-hours per gallon per degree Fahrenheit = 0.0024, C = specific heat of water in Btu's per gallon per degree Fahrenheit = 8.2, and e = nominal gas or oil water heater recovery efficiency = 0.75. [88 FR 3279, Jan. 18, 2023, as amended at 89 FR 83617, Oct. 17, 2204]

Appendix D1 - Appendix D1 to Subpart B of Part 430—Uniform Test Method for Measuring the Energy Consumption of Clothes Dryers

Note:

The procedures in either this appendix or appendix D2 to this subpart must be used to determine compliance with the energy conservation standards for clothes dryers provided at § 430.32(h)(3). Manufacturers must use a single appendix for all representations, including certifications of compliance, and may not use this appendix for certain representations and appendix D2 to this subpart for other representations. The procedures in appendix D2 to this subpart must be used to determine compliance with the energy conservation standards for clothes dryers provided at § 430.32(h)(4).

0. Incorporation by Reference

DOE incorporated by reference in § 430.3 the standards for AHAM HLD-1 and IEC 62301, in their entirety, however, only enumerated provisions of those documents are applicable to this appendix. In cases where there is a conflict between any industry standard(s) and this appendix, the language of the test procedure in this appendix takes precedence over the industry standard(s).

(1) AHAM HLD-1:

(i) Section 3.3.5.1 “Standard Simulator” as referenced in sections 2.1.2 through 2.1.3 of this appendix.

(ii) [Reserved]

(2) IEC 62301:

(i) Section 5, Paragraph 5.1, Note 1 as referenced in section 3.6.2 of this appendix.

(ii) Section 5, Paragraph 5.3.2 “Sampling Method” as referenced in section 3.6.3 of this appendix.

1. Definitions

1.1 “Active mode” means a mode in which the clothes dryer is connected to a main power source, has been activated and is performing the main function of tumbling the clothing with or without heated or unheated forced air circulation to remove moisture from the clothing, remove wrinkles or prevent wrinkling of the clothing, or both.

1.2 “AHAM” means the Association of Home Appliance Manufacturers.

1.3 “AHAM HLD-1” means the test standard published by the Association of Home Appliance Manufacturers, titled “Household Tumble Type Clothes Dryers,” ANSI-approved June 11, 2010, ANSI/AHAM HLD-1-2010.

1.4 “Automatic termination control” means a dryer control system with a sensor which monitors either the dryer load temperature or its moisture content and with a controller which automatically terminates the drying process. A mark, detent, or other visual indicator or detent which indicates a preferred automatic termination control setting must be present if the dryer is to be classified as having an “automatic termination control.” A mark is a visible single control setting on one or more dryer controls.

1.5 “Bone dry” means a condition of a load of test cloths which has been dried in a dryer at maximum temperature for a minimum of 10 minutes, removed, and weighed before cool down, and then dried again for 10-minute periods until the final weight change of the load is 1 percent or less.

1.6 “Compact” or “compact size” means a clothes dryer with a drum capacity of less than 4.4 cubic feet.

1.7 “Cool down” means that portion of the clothes drying cycle when the added gas or electric heat is terminated and the clothes continue to tumble and dry within the drum.

1.8 “Cycle” means a sequence of operation of a clothes dryer which performs a clothes drying operation, and may include variations or combinations of the functions of heating, tumbling, and drying.

1.9 “Drum capacity” means the volume of the drying drum in cubic feet.

1.10 “IEC 62301” (Second Edition) means the test standard published by the International Electrotechnical Commission (“IEC”) titled “Household electrical appliances—Measurement of standby power,” Publication 62301 (Edition 2.0 2011-01) (incorporated by reference; see § 430.3).

1.11 “Final moisture content” (“FMC”) means the ratio of the weight of water contained by the dry test load (i.e., after completion of the drying cycle) to the bone-dry weight of the test load, expressed as a percent.

1.12 “Inactive mode” means a standby mode that facilitates the activation of active mode by remote switch (including remote control), internal sensor, or timer, or that provides continuous status display.

1.13 “Initial moisture content” (“IMC”) means the ratio of the weight of water contained by the damp test load (i.e., prior to completion of the drying cycle) to the bone-dry weight of the test load, expressed as a percent.

1.14 “Moisture content” means the ratio of the weight of water contained by the test load to the bone-dry weight of the test load, expressed as a percent.

1.15 “Off mode” means a mode in which the clothes dryer is connected to a main power source and is not providing any active or standby mode function, and where the mode may persist for an indefinite time. An indicator that only shows the user that the product is in the off position is included within the classification of an off mode.

1.16 “Standard size” means a clothes dryer with a drum capacity of 4.4 cubic feet or greater.

1.17 “Standby mode” means any product modes where the energy using product is connected to a main power source and offers one or more of the following user-oriented or protective functions which may persist for an indefinite time:

(a) To facilitate the activation of other modes (including activation or deactivation of active mode) by remote switch (including remote control), internal sensor, or timer.

(b) Continuous functions, including information or status displays (including clocks) or sensor-based functions. A timer is a continuous clock function (which may or may not be associated with a display) that provides regular scheduled tasks (e.g., switching) and that operates on a continuous basis.

1.18 “Vented clothes dryer” means a clothes dryer that exhausts the evaporated moisture from the cabinet.

1.19 “Ventless clothes dryer” means a clothes dryer that uses a closed-loop system with an internal condenser to remove the evaporated moisture from the heated air. The moist air is not discharged from the cabinet.

2. Testing Conditions

2.1 Installation.

2.1.1 All clothes dryers. For both vented clothes dryers and ventless clothes dryers, install the clothes dryer in accordance with manufacturer's instructions as shipped with the unit. If the manufacturer's instructions do not specify the installation requirements for a certain component, it shall be tested in the as-shipped condition. Where the manufacturer gives the option to use the dryer both with and without a duct, the dryer shall be tested without the exhaust simulator described in section 3.3.5.1 of AHAM HLD-1 (incorporated by reference; see § 430.3). All external joints should be taped to avoid air leakage. For drying testing, disconnect all lights, such as task lights, that do not provide any information related to the drying process on the clothes dryer and that do not consume more than 10 watts during the clothes dryer test cycle. Control setting indicator lights showing the cycle progression, temperature or dryness settings, or other cycle functions that cannot be turned off during the test cycle shall not be disconnected during the active mode test cycle. For standby and off mode testing, the clothes dryer shall also be installed in accordance with section 5, paragraph 5.2 of IEC 62301 (Second Edition) (incorporated by reference; see § 430.3), disregarding the provisions regarding batteries and the determination, classification, and testing of relevant modes. For standby and off mode testing, all lighting systems shall remain connected.

2.1.2 Vented clothes dryers. For vented clothes dryers, the dryer exhaust shall be restricted by adding the AHAM exhaust simulator described in section 3.3.5.1 of AHAM HLD-1.

2.1.3 Ventless clothes dryers. For ventless clothes dryers, the dryer shall be tested without the AHAM exhaust simulator. If the manufacturer gives the option to use a ventless clothes dryer, with or without a condensation box, the dryer shall be tested with the condensation box installed. For ventless clothes dryers, the condenser unit of the dryer must remain in place and not be taken out of the dryer for any reason between tests.

2.2 Ambient temperature and humidity.

2.2.1 For drying testing, maintain the room ambient air temperature at 75 ±3 °F and the room relative humidity at 50 percent ±10 percent relative humidity.

2.2.2 For standby and off mode testing, maintain room ambient air temperature conditions as specified in section 4, paragraph 4.2 of IEC 62301 (Second Edition) (incorporated by reference; see § 430.3)

2.3 Energy supply.

2.3.1 Electrical supply. Maintain the electrical supply at the clothes dryer terminal block within 1 percent of 120/240 or 120/208Y or 120 volts as applicable to the particular terminal block wiring system and within 1 percent of the nameplate frequency as specified by the manufacturer. If the dryer has a dual voltage conversion capability, conduct the test at the highest voltage specified by the manufacturer.

2.3.1.1 Supply voltage waveform. For the clothes dryer standby mode and off mode testing, maintain the electrical supply voltage waveform indicated in section 4, paragraph 4.3.2 of IEC 62301 (Second Edition) (incorporated by reference; see § 430.3). If the power measuring instrument used for testing is unable to measure and record the total harmonic content during the test measurement period, it is acceptable to measure and record the total harmonic content immediately before and after the test measurement period.

2.3.2 Gas supply.

2.3.2.1 Natural gas supply. Maintain the gas supply to the clothes dryer immediately ahead of all controls at a pressure of 7 to 10 inches of water column. The natural gas supplied should have a heating value of approximately 1,025 Btus per standard cubic foot. The actual heating value, Hn2, in Btus per standard cubic foot, for the natural gas to be used in the test shall be obtained either from measurements using a standard continuous flow calorimeter as described in section 2.4.6 of this appendix or by the purchase of bottled natural gas whose Btu rating is certified to be at least as accurate a rating as could be obtained from measurements with a standard continuous flow calorimeter as described in section 2.4.6 of this appendix.

2.3.2.2 Propane gas supply. Maintain the gas supply to the clothes dryer immediately ahead of all controls at a pressure of 11 to 13 inches of water column. The propane gas supplied should have a heating value of approximately 2,500 Btus per standard cubic foot. The actual heating value, Hp, in Btus per standard cubic foot, for the propane gas to be used in the test shall be obtained either from measurements using a standard continuous flow calorimeter as described in section 2.4.6 of this appendix or by the purchase of bottled gas whose Btu rating is certified to be at least as accurate a rating as could be obtained from measurement with a standard continuous calorimeter as described in section 2.4.6 of this appendix.

2.3.2.3 Hourly Btu Rating. Maintain the hourly Btu rating of the burner within ±5 percent of the rating specified by the manufacturer. If the hourly Btu rating of the burner cannot be maintained within ±5 percent of the rating specified by the manufacturer, make adjustments in the following order until an hourly Btu rating of the burner within ±5 percent of the rating specified by the manufacturer is achieved:

(1) Modify the gas inlet supply pressure within the allowable range specified in section 2.3.2.1 or 2.3.2.2 of this appendix, as applicable;

(2) If the clothes dryer is equipped with a gas pressure regulator, modify the outlet pressure of the gas pressure regulator within ±10 percent of the value recommended by the manufacturer in the installation manual, on the nameplate sticker, or wherever the manufacturer makes such a recommendation for the basic model; and

(3) Modify the orifice as necessary to achieve the required hourly Btu rating.

2.4 Instrumentation. Perform all test measurements using the following instruments as appropriate.

2.4.1 Weighing scales.

2.4.1.1 Weighing scale for test cloth. The scale shall have a range of 0 to a maximum of 60 pounds with a resolution of at least 0.001 pounds and a maximum error no greater than 0.1 percent of any measured value within the range of 3 to 15 pounds.

2.4.1.2 Weighing scale for drum capacity measurements. The scale should have a range of 0 to a maximum of 600 pounds with resolution of 0.50 pounds and a maximum error no greater than 0.5 percent of the measured value.

2.4.2 Kilowatt-hour meter. The kilowatt-hour meter shall have a resolution of 0.001 kilowatt-hours and a maximum error no greater than 0.5 percent of the measured value.

2.4.3 Gas meter. The gas meter shall have a resolution of 0.001 cubic feet and a maximum error no greater than 0.5 percent of the measured value.

2.4.4 Dry and wet bulb psychrometer. The dry and wet bulb psychrometer shall have an error no greater than ±1 °F. A relative humidity meter with a maximum error tolerance expressed in °F equivalent to the requirements for the dry and wet bulb psychrometer or with a maximum error tolerance of ±2 percent relative humidity would be acceptable for measuring the ambient humidity.

2.4.5 Temperature. The temperature sensor shall have an error no greater than ±1 °F.

2.4.6 Standard Continuous Flow Calorimeter. The calorimeter shall have an operating range of 750 to 3,500 Btu per cubic feet. The maximum error of the basic calorimeter shall be no greater than 0.2 percent of the actual heating value of the gas used in the test. The indicator readout shall have a maximum error no greater than 0.5 percent of the measured value within the operating range and a resolution of 0.2 percent of the full-scale reading of the indicator instrument.

2.4.7 Standby mode and off mode watt meter. The watt meter used to measure standby mode and off mode power consumption shall meet the requirements specified in section 4, paragraph 4.4 of IEC 62301 (Second Edition) (incorporated by reference; see § 430.3). If the power measuring instrument used for testing is unable to measure and record the crest factor, power factor, or maximum current ratio during the test measurement period, it is acceptable to measure the crest factor, power factor, and maximum current ratio immediately before and after the test measurement period.

2.5 Lint trap. Clean the lint trap thoroughly before each test run.

2.6 Test Cloths.

2.6.1 Energy test cloth. The energy test cloth shall be clean and consist of the following:

(a) Pure finished bleached cloth, made with a momie or granite weave, which is a blended fabric of 50-percent cotton and 50-percent polyester and weighs within + 10 percent of 5.75 ounces per square yard after test cloth preconditioning, and has 65 ends on the warp and 57 picks on the fill. The individual warp and fill yarns are a blend of 50-percent cotton and 50-percent polyester fibers.

(b) Cloth material that is 24 inches by 36 inches and has been hemmed to 22 inches by 34 inches before washing. The maximum shrinkage after five washes shall not be more than 4 percent on the length and width.

(c) The number of test runs on the same energy test cloth shall not exceed 25 runs.

2.6.2 Energy stuffer cloths. The energy stuffer cloths shall be made from energy test cloth material, and shall consist of pieces of material that are 12 inches by 12 inches and have been hemmed to 10 inches by 10 inches before washing. The maximum shrinkage after five washes shall not be more than 4 percent on the length and width. The number of test runs on the same energy stuffer cloth shall not exceed 25 runs after test cloth preconditioning.

2.6.3 Test Cloth Preconditioning.

A new test cloth load and energy stuffer cloths shall be treated as follows:

(1) Bone dry the load to a weight change of ±1 percent, or less, as prescribed in section 1.5.

(2) Place the test cloth load in a standard clothes washer set at the maximum water fill level. Wash the load for 10 minutes in soft water (17 parts per million hardness or less), using 60.8 grams of AHAM standard test detergent Formula 3. Wash water temperature is to be controlled at 140 ° ±5 °F (60 ° ±2.7 °C). Rinse water temperature is to be controlled at 100 ° ±5 °F (37.7 ±2.7 °C).

(3) Rinse the load again at the same water temperature.

(4) Bone dry the load as prescribed in section 1.5 and weigh the load.

(5) This procedure is repeated until there is a weight change of 1 percent or less.

(6) A final cycle is to be a hot water wash with no detergent, followed by two warm water rinses.

2.7 Test loads.

2.7.1 Load size. Determine the load size for the unit under test, according to Table 1 of this section.

Table 1—Test Loads

Unit under test Test load
(bone dry weight)
Standard size clothes dryer8.45 pounds ± .085 pounds. Compact size clothes dryer3.00 pounds ± .03 pounds.

Each test load must consist of energy test cloths and no more than five energy stuffer cloths.

2.7.2 Test load preparation. Dampen the load by agitating it in water whose temperature is 60 °F ± 5 °F and consists of 0 to 17 parts per million hardness for approximately 2 minutes in order to saturate the fabric. Then, extract water from the wet test load by spinning the load to a target moisture content between 54.0-61.0 percent of the bone-dry weight of the test load. If after extraction the moisture content is less than 54.0 percent, make a final mass adjustment, such that the moisture content is between 54.0-61.0 percent of the bone-dry weight of the test load, by adding water uniformly distributed among all of the test cloths in a very fine spray using a spray bottle.

2.7.3 Method of loading. Load the energy test cloths by grasping them in the center, shaking them to hang loosely, and then dropping them in the dryer at random.

2.8 Clothes dryer preconditioning.

2.8.1 Vented clothes dryers. For vented clothes dryers, before any test cycle, operate the dryer without a test load in the non-heat mode for 15 minutes or until the discharge air temperature is varying less than 1 °F for 10 minutes—whichever is longer—in the test installation location with the ambient conditions within the specified test condition tolerances of section 2.2 of this appendix.

2.8.2 Ventless clothes dryers. For ventless clothes dryers, before any test cycle, the steady-state machine temperature must be equal to ambient room temperature described in 2.2.1. This may be done by leaving the machine at ambient room conditions for at least 12 hours between tests.

3. Test Procedures and Measurements

3.1 Drum Capacity. Measure the drum capacity by sealing all openings in the drum except the loading port with a plastic bag, and ensuring that all corners and depressions are filled and that there are no extrusions of the plastic bag through any openings in the interior of the drum. Support the dryer's rear drum surface on a platform scale to prevent deflection of the drum surface, and record the weight of the empty dryer. Fill the drum with water to a level determined by the intersection of the door plane and the loading port (i.e., the uppermost edge of the drum that is in contact with the door seal). Record the temperature of the water and then the weight of the dryer with the added water and then determine the mass of the water in pounds. Add the appropriate volume to account for any space in the drum interior not measured by water fill (e.g., the space above the uppermost edge of the drum within a curved door) and subtract the appropriate volume to account for space that is measured by water fill but cannot be used when the door is closed (e.g., space occupied by the door when closed). The drum capacity is calculated to the nearest 0.1 cubic foot as follows:

C = w/d ±volume adjustment C = capacity in cubic feet. w = mass of water in pounds. d = density of water at the measured temperature in pounds per cubic foot.

3.2 Dryer Loading. Load the dryer as specified in 2.7.

3.3 Test cycle. Operate the clothes dryer at the maximum temperature setting and, if equipped with a timer, at the maximum time setting. Any other optional cycle settings that do not affect the temperature or time settings shall be tested in the as-shipped position, except that if the clothes dryer has network capabilities, the network settings must be disabled throughout testing if such settings can be disabled by the end-user and the product's user manual provides instructions on how to do so. If the network settings cannot be disabled by the end-user, or the product's user manual does not provide instruction for disabling network settings, then the unit must be tested with the network settings in the factory default configuration for the test cycle. If the clothes dryer does not have a separate temperature setting selection on the control panel, the maximum time setting should be used for the drying test cycle. Dry the load until the moisture content of the test load is between 2.5 and 5.0 percent of the bone-dry weight of the test load, at which point the test cycle is stopped, but do not permit the dryer to advance into cool down. If required, reset the timer to increase the length of the drying cycle. After stopping the test cycle, remove and weigh the test load within 5 minutes following termination of the test cycle. The clothes dryer shall not be stopped intermittently in the middle of the test cycle for any reason. Record the data specified by section 3.4 of this appendix. If the dryer automatically stops during a cycle because the condensation box is full of water, the test is stopped, and the test run is invalid, in which case the condensation box shall be emptied and the test re-run from the beginning. For ventless clothes dryers, during the time between two cycles, the door of the dryer shall be closed except for loading and unloading.

3.4 Data recording. Record for each test cycle:

3.4.1 Bone-dry weight of the test load, Wbonedry, as described in section 2.7.1 of this appendix.

3.4.2 Moisture content of the wet test load before the test, IMC, as described in section 2.7.2 of this appendix.

3.4.3 Moisture content of the dry test load obtained after the test, FMC, as described in section 3.3 of this appendix.

3.4.4 Test room conditions, temperature, and percent relative humidity described in 2.2.1.

3.4.5 For electric dryers—the total kilowatt-hours of electric energy, Et, consumed during the test described in 3.3.

3.4.6 For gas dryers:

3.4.6.1 Total kilowatt-hours of electrical energy, Ete, consumed during the test described in 3.3.

3.4.6.2 Cubic feet of gas per cycle, Etg, consumed during the test described in 3.3.

3.4.6.3 Correct the gas heating value, GEF, as measured in 2.3.2.1 and 2.3.2.2, to standard pressure and temperature conditions in accordance with U.S. Bureau of Standards, circular C417, 1938.

3.5 Test for automatic termination field use factor. The field use factor for automatic termination can be claimed for those dryers which meet the requirements for automatic termination control, defined in 1.4.

3.6 Standby mode and off mode power. Connect the clothes dryer to a watt meter as specified in section 2.4.7 of this appendix. Establish the testing conditions set forth in section 2 of this appendix.

3.6.1 Perform standby mode and off mode testing after completion of an active mode drying cycle included as part of the test cycle; after removing the test load; without changing the control panel settings used for the active mode drying cycle; with the door closed; and without disconnecting the electrical energy supply to the clothes dryer between completion of the active mode drying cycle and the start of standby mode and off mode testing.

3.6.2 For clothes dryers that take some time to automatically enter a stable inactive mode or off mode state from a higher power state as discussed in Section 5, Paragraph 5.1, Note 1 of IEC 62301, allow sufficient time for the clothes dryer to automatically reach the default inactive/off mode state before proceeding with the test measurement.

3.6.3 Once the stable inactive/off mode state has been reached, measure and record the default inactive/off mode power, Pdefault, in watts, following the test procedure for the sampling method specified in Section 5, Paragraph 5.3.2 of IEC 62301.

3.6.4 For a clothes dryer with a switch (or other means) that can be optionally selected by the end user to achieve a lower-power inactive/off mode state than the default inactive/off mode state measured in section 3.6.3 of this appendix, after performing the measurement in section 3.6.3 of this appendix, activate the switch (or other means) to the position resulting in the lowest power consumption and repeat the measurement procedure described in section 3.6.3 of this appendix. Measure and record the lowest inactive/off mode power, Plowest, in watts.

4. Calculation of Derived Results From Test Measurements

4.1 Total per-cycle electric dryer energy consumption. Calculate the total electric dryer energy consumption per cycle, Ece, expressed in kilowatt-hours per cycle and defined as:

Ece = [53.5/(IMC − FMC)] × Et × field use, Where: Et = the energy recorded in section 3.4.5 of this appendix. 53.5 = an experimentally established value for the percent reduction in the moisture content of the test load during a laboratory test cycle expressed as a percent. field use = field use factor, = 1.18 for clothes dryers with time termination control systems only without any automatic termination control functions. = 1.04 for clothes dryers with automatic control systems that meet the requirements of the definition for automatic termination control in section 1.4 of this appendix, including those that also have a supplementary timer control, or that may also be manually controlled. IMC = the moisture content of the wet test load as recorded in section 3.4.2 of this appendix. FMC = the moisture content of the dry test load as recorded in section 3.4.3 of this appendix.

4.2 Per-cycle gas dryer electrical energy consumption. Calculate the gas dryer electrical energy consumption per cycle, Ege, expressed in kilowatt-hours per cycle and defined as:

Ege = [53.5/(IMC − FMC)] × Ete × field use, Where: Ete = the energy recorded in section 3.4.6.1 of this appendix. field use, 53.5, MCw, and MCd as defined in section 4.1 of this appendix.

4.3 Per-cycle gas dryer gas energy consumption. Calculate the gas dryer gas energy consumption per cycle, Egg, expressed in Btus per cycle and defined as:

Egg = [53.5/(MCw − MCd)] × Etg × field use × GEF Where: Etg = the energy recorded in section 3.4.6.2 of this appendix. GEF = corrected gas heat value (Btu per cubic feet) as defined in section 3.4.6.3 of this appendix. field use, 53.5, IMC, and FMC as defined in section 4.1 of this appendix.

4.4 Total per-cycle gas dryer energy consumption expressed in kilowatt-hours. Calculate the total gas dryer energy consumption per cycle, Ecg, expressed in kilowatt-hours per cycle and defined as:

Ecg = Ege + (Egg/3412 Btu/kWh) Where: Ege as defined in 4.2 Egg as defined in 4.3

4.5 Per-cycle standby mode and off mode energy consumption. Calculate the clothes dryer per-cycle standby mode and off mode energy consumption, ETSO, expressed in kilowatt-hours per cycle and defined as:

ETSO = [(Pdefault × Sdefault) + (Plowest × Slowest)] × K/283 Where: Pdefault = Default inactive/off mode power, in watts, as measured in section 3.6.3 of this appendix. Plowest = Lowest inactive/off mode power, in watts, as measured in section 3.6.4 of this appendix for clothes dryer with a switch (or other means) that can be optionally selected by the end user to achieve a lower-power inactive/off mode than the default inactive/off mode; otherwise, Plowest=0. Sdefault = Annual hours in default inactive/off mode, defined as 8,620 if no optional lowest-power inactive/off mode is available; otherwise 4,310. Slowest = Annual hours in lowest-power inactive/off mode, defined as 0 if no optional lowest-power inactive/off mode is available; otherwise 4,310. K = Conversion factor of watt-hours to kilowatt-hours = 0.001. 283 = Representative average number of clothes dryer cycles in a year. 8,620 = Combined annual hours for inactive and off mode. 4,310 = One-half of the combined annual hours for inactive and off mode.

4.6 Per-cycle combined total energy consumption expressed in kilowatt-hours. Calculate the per-cycle combined total energy consumption, ECC, expressed in kilowatt-hours per cycle and defined for an electric clothes dryer as:

ECC = Ece + ETSO Where: Ece = the energy recorded in section 4.1 of this appendix, and ETSO = the energy recorded in section 4.5 of this appendix, and defined for a gas clothes dryer as: ECC = Ecg + ETSO Where: Ecg = the energy recorded in section 4.4 of this appendix, and ETSO = the energy recorded in section 4.5 of this appendix.

4.7 Combined Energy Factor in pounds per kilowatt-hour. Calculate the combined energy factor, CEF, expressed in pounds per kilowatt-hour and defined as:

CEF = Wbonedry/ECC Where: Wbonedry = the bone dry test load weight 3.4.1, and ECC = the energy recorded in 4.6 [76 FR 1032, Jan. 6, 2011, as amended at 78 FR 49645, Aug. 14, 2013; 86 FR 56639, Oct. 8, 2021; 89 FR 81305, Oct. 8, 2024]

Appendix D2 - Appendix D2 to Subpart B of Part 430—Uniform Test Method for Measuring the Energy Consumption of Clothes Dryers

Note:

The procedures in either appendix D1 to this subpart or this appendix must be used to determine compliance with the energy conservation standards for clothes dryers provided at § 430.32(h)(3). Manufacturers must use a single appendix for all representations, including certifications of compliance, and may not use appendix D1 to this subpart for certain representations and this appendix for other representations. The procedures in this appendix must be used to determine compliance with the energy conservation standards for clothes dryers provided at § 430.32(h)(4). Manufacturers may use this appendix to certify compliance with the clothes dryer standards provided at § 430.32(h)(4) prior to the applicable compliance date for those standards.

Per-cycle standby mode and off mode energy consumption in section 4.5 of this appendix is calculated using the value for the annual representative average number of clothes dryer cycles in a year specified in section 4.5.1(a) of this appendix until March 1, 2028. Beginning on March 1, 2028, per-cycle standby mode and off mode energy consumption in section 4.5 of this appendix is calculated using the value for the annual representative average number of clothes dryer cycles in a year specified in section 4.5.1(b) of this appendix.

0. Incorporation by Reference

DOE incorporated by reference in § 430.3 the entire standard for AHAM HLD-1 and IEC 62301, however, only enumerated provisions of those documents are applicable to this appendix. In cases where there is a conflict between any industry standard(s) and this appendix, the language of the test procedure in this appendix takes precedence over the industry standard(s).

(1) AHAM HLD-1:

(i) Section 3.3.5.1 “Standard Simulator” as referenced in sections 2.1.2 through 2.1.3 of this appendix.

(ii) [Reserved]

(2) IEC 62301:

(i) Section 5, Paragraph 5.1, Note 1 as referenced in section 3.5.2 of this appendix.

(ii) Section 5, Paragraph 5.3.2 “Sampling Method” as referenced in section 3.5.3 of this appendix.

1. Definitions

1.1 “Active mode” means a mode in which the clothes dryer is connected to a main power source, has been activated and is performing the main function of tumbling the clothing with or without heated or unheated forced air circulation to remove moisture from the clothing, remove wrinkles or prevent wrinkling of the clothing, or both.

1.2 “AHAM” means the Association of Home Appliance Manufacturers.

1.3 “AHAM HLD-1” means the test standard published by the Association of Home Appliance Manufacturers, titled “Household Tumble Type Clothes Dryers,” ANSI-approved June 11, 2010, ANSI/AHAM HLD-1-2010.

1.4 “Automatic termination control” means a dryer control system with a sensor which monitors either the dryer load temperature or its moisture content and with a controller which automatically terminates the drying process. A mark, detent, or other visual indicator or detent which indicates a preferred automatic termination control setting must be present if the dryer is to be classified as having an “automatic termination control.” A mark is a visible single control setting on one or more dryer controls.

1.5 “Automatic termination control dryer” means a clothes dryer which can be preset to carry out at least one sequence of operations to be terminated by means of a system assessing, directly or indirectly, the moisture content of the load. An automatic termination control dryer with supplementary timer or that may also be manually controlled shall be tested as an automatic termination control dryer.

1.6 “Bone dry” means a condition of a load of test cloths which has been dried in a dryer at maximum temperature for a minimum of 10 minutes, removed, and weighed before cool down, and then dried again for 10-minute periods until the final weight change of the load is 1 percent or less.

1.7 “Compact” or “compact size” means a clothes dryer with a drum capacity of less than 4.4 cubic feet.

1.8 “Cool down” means that portion of the clothes drying cycle when the added gas or electric heat is terminated and the clothes continue to tumble and dry within the drum.

1.9 “Cycle” means a sequence of operation of a clothes dryer which performs a clothes drying operation, and may include variations or combinations of the functions of heating, tumbling, and drying.

1.10 “Drum capacity” means the volume of the drying drum in cubic feet.

1.11 “Final moisture content” (“FMC”) means the ratio of the weight of water contained by the dry test load (i.e., after completion of the drying cycle) to the bone-dry weight of the test load, expressed as a percent.

1.12 “IEC 62301” (Second Edition) means the test standard published by the International Electrotechnical Commission (“IEC”) titled “Household electrical appliances—Measurement of standby power,” Publication 62301 (Edition 2.0 2011-01) (incorporated by reference; see § 430.3).

1.13 “Initial moisture content” (“IMC”) means the ratio of the weight of water contained by the damp test load (i.e., prior to completion of the drying cycle) to the bone-dry weight of the test load, expressed as a percent.

1.14 “Inactive mode” means a standby mode that facilitates the activation of active mode by remote switch (including remote control), internal sensor, or timer, or that provides continuous status display.

1.15 “Moisture content” means the ratio of the weight of water contained by the test load to the bone-dry weight of the test load, expressed as a percent.

1.16 “Off mode” means a mode in which the clothes dryer is connected to a main power source and is not providing any active or standby mode function, and where the mode may persist for an indefinite time. An indicator that only shows the user that the product is in the off position is included within the classification of an off mode.

1.17 “Standard size” means a clothes dryer with a drum capacity of 4.4 cubic feet or greater.

1.18 “Standby mode” means any product modes where the energy using product is connected to a mains power source and offers one or more of the following user-oriented or protective functions which may persist for an indefinite time:

(a) To facilitate the activation of other modes (including activation or deactivation of active mode) by remote switch (including remote control), internal sensor, or timer.

(b) Continuous functions, including information or status displays (including clocks) or sensor-based functions. A timer is a continuous clock function (which may or may not be associated with a display) that provides regular scheduled tasks (e.g., switching) and that operates on a continuous basis.

1.19 “Timer dryer” means a clothes dryer that can be preset to carry out at least one operation to be terminated by a timer, but may also be manually controlled, and does not include any automatic termination function.

1.20 “Vented clothes dryer” means a clothes dryer that exhausts the evaporated moisture from the cabinet.

1.21 “Ventless clothes dryer” means a clothes dryer that uses a closed-loop system with an internal condenser to remove the evaporated moisture from the heated air. The moist air is not discharged from the cabinet.

2. Testing Conditions

2.1 Installation.

2.1.1 All clothes dryers. For both vented clothes dryers and ventless clothes dryers, install the clothes dryer in accordance with manufacturer's instructions as shipped with the unit. If the manufacturer's instructions do not specify the installation requirements for a certain component, it shall be tested in the as-shipped condition. Where the manufacturer gives the option to use the dryer both with and without a duct, the dryer shall be tested without the exhaust simulator described in section 3.3.5.1 of AHAM HLD-1 (incorporated by reference; see § 430.3). All external joints should be taped to avoid air leakage. For drying testing, disconnect all lights, such as task lights, that do not provide any information related to the drying process on the clothes dryer and that do not consume more than 10 watts during the clothes dryer test cycle. Control setting indicator lights showing the cycle progression, temperature or dryness settings, or other cycle functions that cannot be turned off during the test cycle shall not be disconnected during the active mode test cycle. For standby and off mode testing, the clothes dryer shall also be installed in accordance with section 5, paragraph 5.2 of IEC 62301 (Second Edition) (incorporated by reference; see § 430.3), disregarding the provisions regarding batteries and the determination, classification, and testing of relevant modes. For standby and off mode testing, all lighting systems shall remain connected.

2.1.2 Vented clothes dryers. For vented clothes dryers, the dryer exhaust shall be restricted by adding the AHAM exhaust simulator described in section 3.3.5.1 of AHAM HLD-1.

2.1.3 Ventless clothes dryers. For ventless clothes dryers, the dryer shall be tested without the AHAM exhaust simulator. If the manufacturer gives the option to use a ventless clothes dryer, with or without a condensation box, the dryer shall be tested with the condensation box installed. For ventless clothes dryers, the condenser unit of the dryer must remain in place and not be taken out of the dryer for any reason between tests.

2.2 Ambient temperature and humidity.

2.2.1 For drying testing, maintain the room ambient air temperature at 75 ±3 F and the room relative humidity at 50 percent ±10 percent relative humidity.

2.2.2 For standby and off mode testing, maintain room ambient air temperature conditions as specified in section 4, paragraph 4.2 of IEC 62301 (Second Edition) (incorporated by reference; see § 430.3).

2.3 Energy supply.

2.3.1 Electrical supply. Maintain the electrical supply at the clothes dryer terminal block within 1 percent of 120/240 or 120/208Y or 120 volts as applicable to the particular terminal block wiring system and within 1 percent of the nameplate frequency as specified by the manufacturer. If the dryer has a dual voltage conversion capability, conduct the test at the highest voltage specified by the manufacturer.

2.3.1.1 Supply voltage waveform. For the clothes dryer standby mode and off mode testing, maintain the electrical supply voltage waveform indicated in section 4, paragraph 4.3.2 of IEC 62301 (Second Edition) (incorporated by reference; see § 430.3). If the power measuring instrument used for testing is unable to measure and record the total harmonic content during the test measurement period, it is acceptable to measure and record the total harmonic content immediately before and after the test measurement period.

2.3.2 Gas supply.

2.3.2.1 Natural gas supply. Maintain the gas supply to the clothes dryer immediately ahead of all controls at a pressure of 7 to 10 inches of water column. The natural gas supplied should have a heating value of approximately 1,025 Btus per standard cubic foot. The actual heating value, Hn2, in Btus per standard cubic foot, for the natural gas to be used in the test shall be obtained either from measurements using a standard continuous flow calorimeter as described in section 2.4.6 of this appendix or by the purchase of bottled natural gas whose Btu rating is certified to be at least as accurate a rating as could be obtained from measurements with a standard continuous flow calorimeter as described in section 2.4.6 of this appendix.

2.3.2.2 Propane gas supply. Maintain the gas supply to the clothes dryer immediately ahead of all controls at a pressure of 11 to 13 inches of water column. The propane gas supplied should have a heating value of approximately 2,500 Btus per standard cubic foot. The actual heating value, Hp, in Btus per standard cubic foot, for the propane gas to be used in the test shall be obtained either from measurements using a standard continuous flow calorimeter as described in section 2.4.6 of this appendix or by the purchase of bottled gas whose Btu rating is certified to be at least as accurate a rating as could be obtained from measurement with a standard continuous calorimeter as described in section 2.4.6 of this appendix.

2.3.2.3 Hourly Btu Rating. Maintain the hourly Btu rating of the burner within ±5 percent of the rating specified by the manufacturer. If the hourly Btu rating of the burner cannot be maintained within ±5 percent of the rating specified by the manufacturer, make adjustments in the following order until an hourly Btu rating of the burner within ±5 percent of the rating specified by the manufacturer is achieved:

(1) Modify the gas inlet supply pressure within the allowable range specified in section 2.3.2.1 or 2.3.2.2 of this appendix, as applicable;

(2) If the clothes dryer is equipped with a gas pressure regulator, modify the outlet pressure of the gas pressure regulator within ±10 percent of the value recommended by the manufacturer in the installation manual, on the nameplate sticker, or wherever the manufacturer makes such a recommendation for the basic model; and

(3) Modify the orifice as necessary to achieve the required hourly Btu rating.

2.4 Instrumentation. Perform all test measurements using the following instruments as appropriate.

2.4.1 Weighing scales.

2.4.1.1 Weighing scale for test cloth. The scale shall have a range of 0 to a maximum of 60 pounds with a resolution of at least 0.001 pounds and a maximum error no greater than 0.1 percent of any measured value within the range of 3 to 15 pounds.

2.4.1.2 Weighing scale for drum capacity measurements. The scale should have a range of 0 to a maximum of 600 pounds with resolution of 0.50 pounds and a maximum error no greater than 0.5 percent of the measured value.

2.4.2 Kilowatt-hour meter. The kilowatt-hour meter shall have a resolution of 0.001 kilowatt-hours and a maximum error no greater than 0.5 percent of the measured value.

2.4.3 Gas meter. The gas meter shall have a resolution of 0.001 cubic feet and a maximum error no greater than 0.5 percent of the measured value.

2.4.4 Dry and wet bulb psychrometer. The dry and wet bulb psychrometer shall have an error no greater than ±1 °F. A relative humidity meter with a maximum error tolerance expressed in °F equivalent to the requirements for the dry and wet bulb psychrometer or with a maximum error tolerance of ±2 percent relative humidity would be acceptable for measuring the ambient humidity.

2.4.5 Temperature. The temperature sensor shall have an error no greater than ±1 °F.

2.4.6 Standard Continuous Flow Calorimeter. The calorimeter shall have an operating range of 750 to 3,500 Btu per cubic foot. The maximum error of the basic calorimeter shall be no greater than 0.2 percent of the actual heating value of the gas used in the test. The indicator readout shall have a maximum error no greater than 0.5 percent of the measured value within the operating range and a resolution of 0.2 percent of the full-scale reading of the indicator instrument.

2.4.7 Standby mode and off mode watt meter. The watt meter used to measure standby mode and off mode power consumption shall meet the requirements specified in section 4, paragraph 4.4 of IEC 62301 (Second Edition) (incorporated by reference; see § 430.3). If the power measuring instrument used for testing is unable to measure and record the crest factor, power factor, or maximum current ratio during the test measurement period, it is acceptable to measure the crest factor, power factor, and maximum current ratio immediately before and after the test measurement period.

2.5 Lint trap. Clean the lint trap thoroughly before each test run.

2.6 Test Cloths.

2.6.1 Energy test cloth. The energy test cloth shall be clean and consist of the following:

(a) Pure finished bleached cloth, made with a momie or granite weave, which is a blended fabric of 50-percent cotton and 50-percent polyester and weighs within + 10 percent of 5.75 ounces per square yard after test cloth preconditioning, and has 65 ends on the warp and 57 picks on the fill. The individual warp and fill yarns are a blend of 50-percent cotton and 50-percent polyester fibers.

(b) Cloth material that is 24 inches by 36 inches and has been hemmed to 22 inches by 34 inches before washing. The maximum shrinkage after five washes shall not be more than 4 percent on the length and width.

(c) The number of test runs on the same energy test cloth shall not exceed 25 runs.

2.6.2 Energy stuffer cloths. The energy stuffer cloths shall be made from energy test cloth material, and shall consist of pieces of material that are 12 inches by 12 inches and have been hemmed to 10 inches by 10 inches before washing. The maximum shrinkage after five washes shall not be more than 4 percent on the length and width. The number of test runs on the same energy stuffer cloth shall not exceed 25 runs after test cloth preconditioning.

2.6.3 Test Cloth Preconditioning.

A new test cloth load and energy stuffer cloths shall be treated as follows:

(1) Bone dry the load to a weight change of ±1 percent, or less, as prescribed in section 1.6 of this appendix.

(2) Place the test cloth load in a standard clothes washer set at the maximum water fill level. Wash the load for 10 minutes in soft water (17 parts per million hardness or less), using 60.8 grams of AHAM standard test detergent Formula 3. Wash water temperature should be maintained at 140 °F ±5 °F (60 °C ±2.7 °C). Rinse water temperature is to be controlled at 100 °F ±5 °F (37.7 °C ±2.7 °C).

(3) Rinse the load again at the same water temperature.

(4) Bone dry the load as prescribed in section 1.6 of this appendix and weigh the load.

(5) This procedure is repeated until there is a weight change of 1 percent or less.

(6) A final cycle is to be a hot water wash with no detergent, followed by two warm water rinses.

2.7 Test loads.

2.7.1 Load size. Determine the load size for the unit under test, according to Table 1 of this section.

Table 1—Test Loads

Unit under test Test load
(bone dry weight)
Standard size clothes dryer8.45 pounds ± .085 pounds. Compact size clothes dryer3.00 pounds ± .03 pounds.

Each test load must consist of energy test cloths and no more than five energy stuffer cloths.

2.7.2 Test load preparation. Dampen the load by agitating it in water whose temperature is 60 °F ±5 °F and consists of 0 to 17 parts per million hardness for approximately 2 minutes to saturate the fabric. Then, extract water from the wet test load by spinning the load until the moisture content of the load is between 52.5 and 57.5 percent of the bone-dry weight of the test load. Make a final mass adjustment, such that the moisture content is 57.5 percent ±0.33 percent by adding water uniformly distributed among all of the test cloths in a very fine spray using a spray bottle.

2.7.3 Method of loading. Load the energy test cloths by grasping them in the center, shaking them to hang loosely, and then dropping them in the dryer at random.

2.8 Clothes dryer preconditioning.

2.8.1 Vented clothes dryers. For vented clothes dryers, before any test cycle, operate the dryer without a test load in the non-heat mode for 15 minutes or until the discharge air temperature is varying less than 1 °F for 10 minutes—whichever is longer—in the test installation location with the ambient conditions within the specified test condition tolerances of section 2.2 of this appendix.

2.8.2 Ventless clothes dryers. For ventless clothes dryers, before any test cycle, the steady-state machine temperature must be equal to ambient room temperature described in 2.2.1. This may be done by leaving the machine at ambient room conditions for at least 12 hours between tests.

3. Test Procedures and Measurements

3.1 Drum Capacity. Measure the drum capacity by sealing all openings in the drum except the loading port with a plastic bag, and ensuring that all corners and depressions are filled and that there are no extrusions of the plastic bag through any openings in the interior of the drum. Support the dryer's rear drum surface on a platform scale to prevent deflection of the drum surface, and record the weight of the empty dryer. Fill the drum with water to a level determined by the intersection of the door plane and the loading port (i.e., the uppermost edge of the drum that is in contact with the door seal). Record the temperature of the water and then the weight of the dryer with the added water and then determine the mass of the water in pounds. Add the appropriate volume to account for any space in the drum interior not measured by water fill (e.g., the space above the uppermost edge of the drum within a curved door) and subtract the appropriate volume to account for the space that is measured by water fill but cannot be used when the door is closed (e.g., space occupied by the door when closed). The drum capacity is calculated to the nearest 0.1 cubic foot as follows:

C= w/d ±volume adjustment C = capacity in cubic feet. w = mass of water in pounds. d = density of water at the measured temperature in pounds per cubic foot.

3.2 Dryer Loading. Load the dryer as specified in 2.7.

3.3 Test cycle.

3.3.1 Timer dryers. For timer dryers, operate the clothes dryer at the maximum temperature setting and, if equipped with a timer, at the maximum time setting. Any other optional cycle settings that do not affect the temperature or time settings shall be tested in the as-shipped position, except that if the clothes dryer has network capabilities, the network settings must be disabled throughout testing if such settings can be disabled by the end-user and the product's user manual provides instructions on how to do so. If the network settings cannot be disabled by the end-user, or the product's user manual does not provide instruction for disabling network settings, then the unit must be tested with the network settings in the factory default configuration for the test cycle. If the clothes dryer does not have a separate temperature setting selection on the control panel, the maximum time setting should be used for the drying test cycle. Dry the load until the moisture content of the test load is between 1 and 2.5 percent of the bone-dry weight of the test load, at which point the test cycle is stopped, but do not permit the dryer to advance into cool down. If required, reset the timer to increase the length of the drying cycle. After stopping the test cycle, remove and weigh the test load within 5 minutes following termination of the test cycle. The clothes dryer shall not be stopped intermittently in the middle of the test cycle for any reason. Record the data specified by section 3.4 of this appendix. If the dryer automatically stops during a cycle because the condensation box is full of water, the test is stopped, and the test run is invalid, in which case the condensation box shall be emptied and the test re-run from the beginning. For ventless clothes dryers, during the time between two cycles, the door of the dryer shall be closed except for loading and unloading.

3.3.2 Automatic termination control dryers. For automatic termination control dryers, a “normal” program shall be selected for the test cycle. For dryers that do not have a “normal” program, the cycle recommended by the manufacturer for drying cotton or linen clothes shall be selected. Where the drying temperature setting can be chosen independently of the program, it shall be set to the maximum. Where the dryness level setting can be chosen independently of the program, it shall be set to the “normal” or “medium” dryness level setting. If such designation is not provided, then the dryness level shall be set at the mid-point between the minimum and maximum settings. If an even number of discrete settings are provided, use the next-highest setting above the midpoint, in the direction of the maximum dryness setting or next-lowest setting below the midpoint, in the direction of the minimum dryness setting. Any other optional cycle settings that do not affect the program, temperature or dryness settings shall be tested in the as-shipped position, except that if the clothes dryer has network capabilities, the network settings must be disabled throughout testing if such settings can be disabled by the end-user and the product's user manual provides instructions on how to do so. If the network settings cannot be disabled by the end-user, or the product's user manual does not provide instruction for disabling network settings, then the unit must be tested with the network settings in the factory default configuration for the test cycle.

Operate the clothes dryer until the completion of the programmed cycle, including the cool down period. The cycle shall be considered complete when the dryer indicates to the user that the cycle has finished (by means of a display, indicator light, audible signal, or other signal) and the heater and drum/fan motor shuts off for the final time. If the clothes dryer is equipped with a wrinkle prevention mode (i.e., that continuously or intermittently tumbles the clothes dryer drum after the clothes dryer indicates to the user that the cycle has finished) that is activated by default in the as-shipped position or if manufacturers' instructions specify that the feature is recommended to be activated for normal use, the cycle shall be considered complete after the end of the wrinkle prevention mode. After the completion of the test cycle, remove and weigh the test load within 5 minutes following termination of the test cycle. Record the data specified in section 3.4 of this appendix. If the final moisture content is greater than 2 percent, the results from the test are invalid and a second run must be conducted. Conduct the second run of the test on the unit using the highest dryness level setting. If, on this second run, the dryer does not achieve a final moisture content of 2 percent or lower, the dryer has not sufficiently dried the clothes and the test results may not be used for certification of compliance with energy conservation standards. If the dryer automatically stops during a cycle because the condensation box is full of water, the test is stopped, and the test run is invalid, in which case the condensation box shall be emptied and the test re-run from the beginning. For ventless clothes dryers, during the time between two cycles, the door of the dryer shall be closed except for loading and unloading.

3.4 Data recording. Record for each test cycle:

3.4.1 Bone-dry weight of the test load, Wbonedry, as described in section 2.7.1 of this appendix.

3.4.2 Moisture content of the wet test load before the test, IMC, as described in section 2.7.2 of this appendix.

3.4.3 Moisture content of the dry test load obtained after the test, FMC, as described in section 3.3 of this appendix.

3.4.4 Test room conditions, temperature, and percent relative humidity described in 2.2.1.

3.4.5 For electric dryers—the total kilowatt-hours of electric energy, Et, consumed during the test described in 3.3.

3.4.6 For gas dryers:

3.4.6.1 Total kilowatt-hours of electrical energy, Ete, consumed during the test described in 3.3.

3.4.6.2 Cubic feet of gas per cycle, Etg, consumed during the test described in 3.3.

3.4.6.3 Correct the gas heating value, GEF, as measured in 2.3.2.1 and 2.3.2.2, to standard pressure and temperature conditions in accordance with U.S. Bureau of Standards, circular C417, 1938.

3.4.7 The cycle settings selected, in accordance with section 3.3.2 of this appendix, for the automatic termination control dryer test.

3.5 Standby mode and off mode power. Connect the clothes dryer to a watt meter as specified in section 2.4.7 of this appendix. Establish the testing conditions set forth in section 2 of this appendix.

3.5.1 Perform standby mode and off mode testing after completion of an active mode drying cycle included as part of the test cycle; after removing the test load; without changing the control panel settings used for the active mode drying cycle; with the door closed; and without disconnecting the electrical energy supply to the clothes dryer between completion of the active mode drying cycle and the start of standby mode and off mode testing.

3.5.2 For clothes dryers that take some time to automatically enter a stable inactive mode or off mode state from a higher power state as discussed in Section 5, Paragraph 5.1, Note 1 of IEC 62301, allow sufficient time for the clothes dryer to automatically reach the default inactive/off mode state before proceeding with the test measurement.

3.5.3 Once the stable inactive/off mode state has been reached, measure and record the default inactive/off mode power, Pdefault, in watts, following the test procedure for the sampling method specified in Section 5, Paragraph 5.3.2 of IEC 62301.

3.5.4 For a clothes dryer with a switch (or other means) that can be optionally selected by the end user to achieve a lower-power inactive/off mode state than the default inactive/off mode state measured in section 3.5.3 of this appendix, after performing the measurement in section 3.5.3 of this appendix, activate the switch (or other means) to the position resulting in the lowest power consumption and repeat the measurement procedure described in section 3.5.3 of this appendix. Measure and record the lowest inactive/off mode power, Plowest, in watts.

4. Calculation of Derived Results From Test Measurements

4.1 Total per-cycle electric dryer energy consumption. Calculate the total per-cycle electric dryer energy consumption required to achieve a final moisture content of 2 percent or less, Ece, expressed in kilowatt-hours per cycle and defined as:

Ece = Et, for automatic termination control dryers, and, Ece = [55.5/(IMC−FMC)] × Et × field use, for timer dryers Where: 55.5 = an experimentally established value for the percent reduction in the moisture content of the test load during a laboratory test cycle expressed as a percent. Et = the energy recorded in section 3.4.5 of this appendix. field use = 1.18, the field use factor for clothes dryers with time termination control systems only without any automatic termination control functions. IMC = the moisture content of the wet test load as recorded in section 3.4.2 of this appendix. FMC = the moisture content of the dry test load as recorded in section 3.4.3 of this appendix.

4.2 Per-cycle gas dryer electrical energy consumption. Calculate the per-cycle gas dryer electrical energy consumption required to achieve a final moisture content of 2 percent or less, Ege, expressed in kilowatt-hours per cycle and defined as:

Ege = Ete, for automatic termination control dryers, and, Ege = [55.5/(IMC−FMC)] × Ete × field use, for timer dryers Where: Ete = the energy recorded in section 3.4.6.1 of this appendix. field use, 55.5, IMC, and FMC as defined in section 4.1 of this appendix.

4.3 Per-cycle gas dryer gas energy consumption. Calculate the per-cycle gas dryer gas energy consumption required to achieve a final moisture content of 2 percent or less, Egg, expressed in Btus per cycle and defined as:

Egg = Etg × GEF for automatic termination control dryers, and, Egg = [55.5/(IMC−FMC)] × Etg × field use × GEF for timer dryers Where: Etg = the energy recorded in section 3.4.6.2 of this appendix. GEF = corrected gas heat value (Btu per cubic foot) as defined in section 3.4.6.3 of this appendix, field use, 55.5, IMC, and FMC as defined in section 4.1 of this appendix.

4.4 Total per-cycle gas dryer energy consumption expressed in kilowatt-hours. Calculate the total per-cycle gas dryer energy consumption required to achieve a final moisture content of 2 percent or less, Ecg, expressed in kilowatt-hours per cycle and defined as:

Ecg = Ege + (Egg/3412 Btu/kWh) Where: Ege = the energy calculated in section 4.2 of this appendix Egg = the energy calculated in section 4.3 of this appendix

4.5 Per-cycle standby mode and off mode energy consumption. Calculate the clothes dryer per-cycle standby mode and off mode energy consumption, ETSO, expressed in kilowatt-hours per cycle and defined as:

ETSO = [(Pdefault × Sdefault) + (Plowest × Slowest)] × K/Cannual Where: Pdefault = Default inactive/off mode power, in watts, as measured in section 3.5.3 of this appendix. Plowest = Lowest inactive/off mode power, in watts, as measured in section 3.5.4 of this appendix for clothes dryer with a switch (or other means) that can be optionally selected by the end user to achieve a lower-power inactive/off mode than the default inactive/off mode; otherwise, Plowest =0. Sdefault = Annual hours in default inactive/off mode, defined as 8,620 if no optional lowest-power inactive/off mode is available; otherwise 4,310. Slowest = Annual hours in lowest-power inactive/off mode, defined as 0 if no optional lowest-power inactive/off mode is available; otherwise 4,310. K = Conversion factor of watt-hours to kilowatt-hours = 0.001. Cannual = Representative average number of clothes dryer cycles in a year as specified in section 4.5.1. 8,620 = Combined annual hours for inactive and off mode. 4,310 = One-half of the combined annual hours for inactive and off mode.

4.5.1 Representative average number of clothes dryer cycles in a year. Per the Introductory Note:

(1) Cannual = 283 (2) Cannual = 236

4.6 Per-cycle combined total energy consumption expressed in kilowatt-hours. Calculate the per-cycle combined total energy consumption, ECC, expressed in kilowatt-hours per cycle and defined for an electric clothes dryer as:

ECC = Ece + ETSO Where: Ece = the energy calculated in section 4.1 of this appendix, and ETSO = the energy calculated in section 4.5 of this appendix, and defined for a gas clothes dryer as: ECC = Ecg + ETSO Where: Ecg = the energy calculated in section 4.4 of this appendix, and ETSO = the energy calculated in section 4.5 of this appendix.

4.7 Combined Energy Factor in pounds per kilowatt-hour. Calculate the combined energy factor, CEF, expressed in pounds per kilowatt-hour and defined as:

CEF = Wbonedry/ECC Where: Wbonedry = the bone dry test load weight recorded in section 3.4.1 of this appendix, and ECC = the energy calculated in section 4.6 of this appendix. [78 FR 49647, Aug. 14, 2013, as amended at 86 FR 56641, Oct. 8, 2021; 89 FR 81305, Oct. 8, 2024]

Appendix E - Appendix E to Subpart B of Part 430—Uniform Test Method for Measuring the Energy Consumption of Water Heaters

Note: Prior to December 18, 2023, representations with respect to the energy use or efficiency of consumer water heaters covered by this test method, including compliance certifications, must be based on testing conducted in accordance with either this appendix as it now appears or appendix E as it appeared at 10 Cspan part 430, subpart B revised as of January 1, 2021. Prior to June 15, 2024, representations with respect to the energy use or efficiency of residential-duty commercial water heaters covered by this test method, including compliance certifications, must be based on testing conducted in accordance with either this appendix as it now appears or appendix E as it appeared at 10 Cspan part 430, subpart B revised as of January 1, 2021.

On and after December 18, 2023, representations with respect to energy use or efficiency of consumer water heaters covered by this test method, including compliance certifications, must be based on testing conducted in accordance with this appendix, except as described in the paragraphs that follow. On and after June 15, 2024, representations with respect to energy use or efficiency of residential-duty commercial water heaters covered by this test method, including compliance certifications, must be based on testing conducted in accordance with this appendix, except as follows.

Prior to May 6, 2029, consumer water heaters subject to section 4.10 of this appendix may optionally apply the requirements of section 4.10 of this appendix. For residential-duty commercial water heaters subject to section 4.10 of this appendix the requirements of section 4.10 of this appendix may optionally be applied prior to the compliance date of any final rule reviewing potential amended energy conservation standards for this equipment published after June 21, 2023.

Prior to May 6, 2029, consumer water heaters subject to section 5.1.2 of this appendix (as specified at § 429.17(a)(1)(ii)(E) of this chapter) may optionally apply the requirements of section 5.1.2 of this appendix in lieu of the requirements in section 5.1.1 of this appendix.

On or after May 6, 2029, representations with respect to energy use or efficiency of consumer water heaters subject to sections 4.10 and 5.1.2 of this appendix must be based on testing conducted in accordance with those provisions.

0. Incorporation by Reference.

DOE incorporated by reference in § 430.3 the entire standard for: ASHRAE 41.1-2020; ASHRAE 41.6-2014; ASHRAE 118.2-2022; ASTM D2156-09 (R2018); and ASTM E97-1987. However, only enumerated provisions of ASHRAE 118.2-2022 are applicable to this appendix, as follows:

0.1 ASHRAE 118.2-2022

(a) Annex B—Gas Heating Value Correction Factor;

(b) [Reserved]

0.2 [Reserved]

1. Definitions.

1.1. Cut-in means the time when or water temperature at which a water heater control or thermostat acts to increase the energy or fuel input to the heating elements, compressor, or burner.

1.2. Cut-out means the time when or water temperature at which a water heater control or thermostat acts to reduce to a minimum the energy or fuel input to the heating elements, compressor, or burner.

1.3. Design Power Rating means the power rating or input rate that a water heater manufacturer assigns to a particular design of water heater and that is included on the nameplate of the water heater, expressed in kilowatts or Btu (kJ) per hour as appropriate. For modulating water heaters, the design power rating is the maximum power rating or input rate that is specified by the manufacturer on the nameplate of the water heater.

1.4. Draw Cluster means a collection of water draws initiated during the 24-hour simulated-use test during which no successive draws are separated by more than 2 hours.

1.5. First-Hour Rating means an estimate of the maximum volume of “hot” water that a non-flow activated water heater can supply within an hour that begins with the water heater fully heated (i.e., with all thermostats satisfied).

1.6. Flow-Activated describes an operational scheme in which a water heater initiates and terminates heating based on sensing flow.

1.7. Heat Trap means a device that can be integrally connected or independently attached to the hot and/or cold water pipe connections of a water heater such that the device will develop a thermal or mechanical seal to minimize the recirculation of water due to thermal convection between the water heater tank and its connecting pipes.

1.8. Maximum GPM (L/min) Rating means the maximum gallons per minute (liters per minute) of hot water that can be supplied by a flow-activated water heater when tested in accordance with section 5.3.2 of this appendix.

1.19 Water Heater Requiring a Storage Tank means a water heater without a storage tank supplied by the manufacturer that cannot meet the requirements of sections 2 and 5 of this appendix without the use of a storage water heater or unfired hot water storage tank.

1.10. Rated Storage Volume means the water storage capacity of a water heater, in gallons (liters), as certified by the manufacturer pursuant to 10 Cspan part 429.

1.11. Recovery Efficiency means the ratio of energy delivered to the water to the energy content of the fuel consumed by the water heater.

1.12. Recovery Period means the time when the main burner of a water heater with a rated storage volume greater than or equal to 2 gallons is raising the temperature of the stored water.

1.13. Split-system heat pump water heater means a heat pump-type water heater in which at least the compressor, which may be installed outdoors, is separate from the storage tank.

1.14. Standby means the time, in hours, during which water is not being withdrawn from the water heater.

1.15. Symbol Usage. The following identity relationships are provided to help clarify the symbology used throughout this procedure:

Cp—specific heat of water Eannual—annual energy consumption of a water heater Eannual,e—annual electrical energy consumption of a water heater Eannual,f—annual fossil-fuel energy consumption of a water heater EX—energy efficiency of a heat pump-type water heater when the 24-hour simulated use test is optionally conducted at any of the additional air temperature conditions as specified in section 2.8 of this appendix, where the subscript “X” corresponds to the dry-bulb temperature at which the test is conducted. Fhr—first-hour rating of a non-flow activated water heater Fmax—maximum GPM (L/min) rating of a flow-activated water heater i—a subscript to indicate the draw number during a test kV—storage tank volume scaling ratio for water heaters with a rated storage volume greater than or equal to 2 gallons Mdel,i—mass of water removed during the ith draw of the 24-hour simulated-use test Min,i—mass of water entering the water heater during the ith draw of the 24-hour simulated-use test M*del,i—for non-flow activated water heaters, mass of water removed during the ith draw during the first-hour rating test M*in,i—for non-flow activated water heaters, mass of water entering the water heater during the ith draw during the first-hour rating test Mdel,10m—for flow-activated water heaters, mass of water removed continuously during the maximum GPM (L/min) rating test Min,10m—for flow-activated water heaters, mass of water entering the water heater continuously during the maximum GPM (L/min) rating test n—for non-flow activated water heaters, total number of draws during the first-hour rating test N—total number of draws during the 24-hour simulated-use test Nr—number of draws from the start of the 24-hour simulated-use test to the end to the first recovery period as described in section 5.4.2 of this appendix Q—total fossil fuel and/or electric energy consumed during the entire 24-hour simulated-use test Qd—daily water heating energy consumption adjusted for net change in internal energy Qda—Qd with adjustment for variation of tank to ambient air temperature difference from nominal value Qdm—overall adjusted daily water heating energy consumption including Qda and QHWD Qe—total electrical energy used during the 24-hour simulated-use test Qf—total fossil fuel energy used by the water heater during the 24-hour simulated-use test Qhr—hourly standby losses of a water heater with a rated storage volume greater than or equal to 2 gallons QHW—daily energy consumption to heat water at the measured average temperature rise across the water heater QHW,67 °F—daily energy consumption to heat quantity of water removed during test over a temperature rise of 67 °F (37.3 °C) QHWD—adjustment to daily energy consumption, QHW, due to variation of the temperature rise across the water heater not equal to the nominal value of 67 °F (37.3 °C) Qr—energy consumption of water heater from the beginning of the test to the end of the first recovery period Qstby—total energy consumed during the standby time interval τstby,1, as determined in section 5.4.2 of this appendix Qsu,0—cumulative energy consumption, including all fossil fuel and electrical energy use, of the water heater from the start of the 24-hour simulated-use test to the start of the standby period as determined in section 5.4.2 of this appendix Qsu,f—cumulative energy consumption, including all fossil fuel and electrical energy use, of the water heater from the start of the 24-hour simulated-use test to the end of the standby period as determined in section 5.4.2 of this appendix T0—mean tank temperature at the beginning of the 24-hour simulated-use test as determined in section 5.4.2 of this appendix T24—mean tank temperature at the end of the 24-hour simulated-use test as determined in section 5.4.2 of this appendix Ta,stby—average ambient air temperature during all standby periods of the 24-hour simulated-use test as determined in section 5.4.2 of this appendix Ta,stby,1—overall average ambient temperature between the start and end of the standby period as determined in section 5.4.2 of this appendix Tt,stby,1— overall average mean tank temperature between the start and end of the standby period as determined in section 5.4.2 of this appendix Tdel—for flow-activated water heaters, average outlet water temperature during the maximum GPM (L/min) rating test Tdel,i—average outlet water temperature during the ith draw of the 24-hour simulated-use test Tin—for flow-activated water heaters, average inlet water temperature during the maximum GPM (L/min) rating test Tst—for water heaters which cannot have internal tank temperature directly measured, estimated average internal storage tank temperature Tp—for water heaters which cannot have internal tank temperature directly measured, average of the inlet and the outlet water temperatures at the end of the period defined by τp Tin,p—for water heaters which cannot have internal tank temperature directly measured, average of the inlet water temperatures Tout,p—for water heaters which cannot have internal tank temperature directly measured, average of the outlet water temperatures Tin,i—average inlet water temperature during the ith draw of the 24-hour simulated-use test Tmax,1—maximum measured mean tank temperature after the first recovery period of the 24-hour simulated-use test as determined in section 5.4.2 of this appendix Tsu,0—maximum measured mean tank temperature at the beginning of the standby period as determined in section 5.4.2 of this appendix Tsu,f—measured mean tank temperature at the end of the standby period as determined in section 5.4.2 of this appendix T*del,i—for non-flow activated water heaters, average outlet water temperature during the ith draw (i = 1 to n) of the first-hour rating test T*max,i—for non-flow activated water heaters, maximum outlet water temperature observed during the ith draw (i = 1 to n) of the first-hour rating test T*min,i—for non-flow activated water heaters, minimum outlet water temperature to terminate the ith draw (i = 1 to n) of the first-hour rating test UA—standby loss coefficient of a water heater with a rated storage volume greater than or equal to 2 gallons UEF—uniform energy factor of a water heater V—the volume of hot water drawn during the applicable draw pattern Vdel,i—volume of water removed during the ith draw (i = 1 to N) of the 24-hour simulated-use test Vin,i—volume of water entering the water heater during the ith draw (i = 1 to N) of the 24-hour simulated-use test V*del,i—for non-flow activated water heaters, volume of water removed during the ith draw (i = 1 to n) of the first-hour rating test V*in,i—for non-flow activated water heaters, volume of water entering the water heater during the ith draw (i = 1 to n) of the first-hour rating test Vdel,10m—for flow-activated water heaters, volume of water removed during the maximum GPM (L/min) rating test Vin,10m—for flow-activated water heaters, volume of water entering the water heater during the maximum GPM (L/min) rating test Vst—measured storage volume of the storage tank for water heaters with a rated storage volume greater than or equal to 2 gallons Veff—effective storage volume vout,p—for water heaters which cannot have internal tank temperature directly measured, average flow rate Wf—weight of storage tank when completely filled with water for water heaters with a rated storage volume greater than or equal to 2 gallons Wt—tare weight of storage tank when completely empty of water for water heaters with a rated storage volume greater than or equal to 2 gallons ηr—recovery efficiency ρ—density of water τp—for water heaters which cannot have internal tank temperature directly measured, duration of the temperature measurement period, determined by the length of time taken for the outlet water temperature to be within 2 °F of the inlet water temperature for 15 consecutive seconds (including the 15-second stabilization period) τstby,1—elapsed time between the start and end of the standby period as determined in section 5.4.2 of this appendix τstby,2—overall time of standby periods when no water is withdrawn during the 24-hour simulated-use test as determined in section 5.4.2 of this appendix

1.16. Temperature Controller means a device that is available to the user to adjust the temperature of the water inside a water heater that stores heated water or the outlet water temperature.

1.17. Thermal break means a thermally non-conductive material that can withstand a pressure of 150 psi (1.034 MPa) at a temperature greater than the maximum temperature the water heater is designed to produce and is utilized to insulate a bypass loop, if one is used in the test set-up, from the inlet piping.

1.18. Uniform Energy Factor means the measure of water heater overall efficiency.

1.19. Water Heater Requiring a Storage Tank means a water heater without a storage tank specified or supplied by the manufacturer that cannot meet the requirements of sections 2 and 5 of this appendix without the use of a storage water heater or unfired hot water storage tank.

2. Test Conditions.

2.1 Installation Requirements. Tests shall be performed with the water heater and instrumentation installed in accordance with section 4 of this appendix.

2.2 Ambient Air Temperature and Relative Humidity.

2.2.1 Non-Heat Pump Water Heaters. The ambient air temperature shall be maintained between 65.0 °F and 70.0 °F (18.3 °C and 21.1 °C) on a continuous basis.

2.2.2 Heat Pump Water Heaters. The dry-bulb temperature shall be maintained at an average of 67.5 °F ± 1 °F (19.7 °C ± 0.6 °C) after a cut-in and before the next cut-out, an average of 67.5 °F ± 2.5 °F (19.7 °C ± 1.4 °C) after a cut-out and before the next cut-in, and at 67.5 °F ± 5 °F (19.7 °C ± 2.8 °C) on a continuous basis throughout the test. The relative humidity shall be maintained within a range of 50% ± 5% throughout the test, and at an average of 50% ± 2% after a cut-in and before the next cut-out.

When testing a split-system heat pump water heater or heat pump water heater requiring a separate storage tank, the heat pump portion of the system shall be tested at the conditions within this section and the separate water heater or unfired hot water storage tank shall be tested at either the conditions within this section or the conditions specified in section 2.2.1 of this appendix.

2.3 Supply Water Temperature. The temperature of the water being supplied to the water heater shall be maintained at 58 °F ± 2 °F (14.4 °C ± 1.1 °C) throughout the test.

2.4 Outlet Water Temperature. The temperature controllers of a non-flow activated water heater shall be set so that water is delivered at a temperature of 125 °F ± 5 °F (51.7 °C ± 2.8 °C).

2.5 Set Point Temperature. The temperature controller of a flow-activated water heater shall be set to deliver water at a temperature of 125 °F ± 5 °F (51.7 °C ± 2.8 °C). If the flow-activated water heater is not capable of delivering water at a temperature of 125 °F ± 5 °F (51.7 °C ± 2.8 °C) when supplied with water at the supply water temperature specified in section 2.3 of this appendix, then the flow-activated water heater shall be set to deliver water at its maximum water temperature.

2.6 Supply Water Pressure. During the test when water is not being withdrawn, the supply pressure shall be maintained between 40 psig (275 kPa) and the maximum allowable pressure specified by the water heater manufacturer.

2.7 Electrical and/or Fossil Fuel Supply.

2.7.1 Electrical. Maintain the electrical supply voltage to within ±2% of the center of the voltage range specified on the nameplate of the water heater by the water heater and/or heat pump manufacturer, from 5 seconds after a cut-in to 5 seconds before next cut-out.

2.7.2 Natural Gas. Maintain the supply pressure in accordance with the supply pressure specified on the nameplate of the water heater by the manufacturer. If the supply pressure is not specified, maintain a supply pressure of 7-10 inches of water column (1.7-2.5 kPa). If the water heater is equipped with a gas appliance pressure regulator and the gas appliance pressure regulator can be adjusted, the regulator outlet pressure shall be within the greater of ±10% of the manufacturer's specified manifold pressure, found on the nameplate of the water heater, or ±0.2 inches water column (0.05 kPa). Maintain the gas supply pressure and manifold pressure only when operating at the design power rating. For all tests, use natural gas having a heating value of approximately 1,025 Btu per standard cubic foot (38,190 kJ per standard cubic meter).

2.7.3 Propane Gas. Maintain the supply pressure in accordance with the supply pressure specified on the nameplate of the water heater by the manufacturer. If the supply pressure is not specified, maintain a supply pressure of 11-13 inches of water column (2.7-3.2 kPa). If the water heater is equipped with a gas appliance pressure regulator and the gas appliance pressure regulator can be adjusted, the regulator outlet pressure shall be within the greater of ±10% of the manufacturer's specified manifold pressure, found on the nameplate of the water heater, or ±0.2 inches water column (0.05 kPa). Maintain the gas supply pressure and manifold pressure only when operating at the design power rating. For all tests, use propane gas with a heating value of approximately 2,500 Btu per standard cubic foot (93,147 kJ per standard cubic meter).

2.7.4 Fuel Oil Supply. Maintain an uninterrupted supply of fuel oil. The fuel pump pressure shall be within ±10% of the pump pressure specified on the nameplate of the water heater or the installation and operations (I&O) manual by the manufacturer. Use fuel oil having a heating value of approximately 138,700 Btu per gallon (38,660 kJ per liter).

2.8 Optional Test Conditions (Heat Pump-Type Water Heaters). The following test conditions may be used for optional representations of EX for heat pump-type water heaters. When conducting a 24-hour simulated use test to determine EX, the test conditions in section 2.1 and sections 2.4 through 2.7 apply. The ambient air temperature and humidity conditions in section 2.2 and the supply water temperature in section 2.3 are replaced with the air temperature, humidity, and supply water temperature conditions as shown in the following table. Testing may optionally be performed at any or all of the conditions in the table, and the sampling plan found at 10 Cspan 429.17(a) may be applied for voluntary representations.

Heat pump type Metric Outdoor air conditions Indoor air conditions Supply water
temperature
( °F)
Dry-bulb
temperature
( °F)
Relative
humidity
(%)
Dry-bulb
temperature
( °F)
Relative
humidity
(%)
Split-System or CirculatingE55.03067.55042.0 E3434.07247.0 E9595.02567.0 Integrated, Split-System, or CirculatingE50N/AN/A50.05850.0 E95N/AN/A95.04067.0
3. Instrumentation.

3.1 Pressure Measurements. Pressure-measuring instruments shall have an error no greater than the following values:

Item measured Instrument accuracy Instrument precision Gas pressure±0.1 inch of water column (±0.025 kPa)±0.05 inch of water column (±0.012 kPa). Atmospheric pressure±0.1 inch of mercury column (±0.34 kPa)±0.05 inch of mercury column (±0.17 kPa). Water pressure±1.0 pounds per square inch (±6.9 kPa)±0.50 pounds per square inch (±3.45 kPa).

3.2 Temperature Measurement

3.2.1 Measurement. Temperature measurements shall be made in accordance with the Standard Method for Temperature Measurement, ASHRAE 41.1-2020, including the conditions as specified in ASHRAE 41.6-2014 as referenced in ASHRAE 41.1-2020, and excluding the steady-state temperature criteria in section 5.5 of ASHRAE 41.1-2020.

3.2.2 Accuracy and Precision. The accuracy and precision of the instruments, including their associated readout devices, shall be within the following limits:

Item measured Instrument accuracy Instrument precision Air dry-bulb temperature±0.2 °F (±0.1 °C)±0.1 °F (±0.06 °C). Air wet-bulb temperature±0.2 °F (±0.1 °C)±0.1 °F (±0.06 °C). Inlet and outlet water temperatures±0.2 °F (±0.1 °C)±0.1 °F (±0.06 °C). Storage tank temperatures±0.5 °F (±0.3 °C)±0.25 °F (±0.14 °C).

3.2.3 Scale Division. In no case shall the smallest scale division of the instrument or instrument system exceed 2 times the specified precision.

3.2.4 Temperature Difference. Temperature difference between the entering and leaving water may be measured with any of the following:

(a) A thermopile (b) Calibrated resistance thermometers (c) Precision thermometers (d) Calibrated thermistors (e) Calibrated thermocouples (f) Quartz thermometers

3.2.5 Thermopile Construction. If a thermopile is used, it shall be made from calibrated thermocouple wire taken from a single spool. Extension wires to the recording device shall also be made from that same spool.

3.2.6 Time Constant. The time constant of the instruments used to measure the inlet and outlet water temperatures shall be no greater than 2 seconds.

3.3 Liquid Flow Rate Measurement. The accuracy of the liquid flow rate measurement, using the calibration if furnished, shall be equal to or less than ±1% of the measured value in mass units per unit time.

3.4 Electrical Energy. The electrical energy used shall be measured with an instrument and associated readout device that is accurate within ±0.5% of the reading.

3.5 Fossil Fuels. The quantity of fuel used by the water heater shall be measured with an instrument and associated readout device that is accurate within ±1% of the reading.

3.6 Mass Measurements. For mass measurements greater than or equal to 10 pounds (4.5 kg), a scale that is accurate within ±0.5% of the reading shall be used to make the measurement. For mass measurements less than 10 pounds (4.5 kg), the scale shall provide a measurement that is accurate within ±0.1 pound (0.045 kg).

3.7 Heating Value. The higher heating value of the natural gas, propane, or fuel oil shall be measured with an instrument and associated readout device that is accurate within ±1% of the reading. The heating values of natural gas and propane must be corrected from those measured to the standard temperature of 60.0 °F (15.6 °C) and standard pressure of 30 inches of mercury column (101.6 kPa) using the method described in Annex B of ASHRAE 118.2-2022.

3.8 Time. The elapsed time measurements shall be measured with an instrument that is accurate within ±0.5 seconds per hour.

3.9 Volume. Volume measurements shall be measured with an accuracy of ±2% of the total volume.

3.10 Relative Humidity. If a relative humidity (RH) transducer is used to measure the relative humidity of the surrounding air while testing heat pump water heaters, the relative humidity shall be measured with an accuracy of ±1.5% RH.

4. Installation.

4.1 Water Heater Mounting. A water heater designed to be freestanding shall be placed on a 3/4 inch (2 cm) thick plywood platform supported by three 2x4 inch (5 cm x 10 cm) runners. If the water heater is not approved for installation on combustible flooring, suitable non-combustible material shall be placed between the water heater and the platform. Water heaters designed to be installed into a kitchen countertop space shall be placed against a simulated wall section. Wall-mounted water heaters shall be supported on a simulated wall in accordance with the manufacturer-published installation instructions. When a simulated wall is used, the construction shall be 2x4 inch (5 cm x 10 cm) studs, faced with 3/4 inch (2 cm) plywood. For heat pump water heaters not delivered as a single package, the units shall be connected in accordance with the manufacturer-published installation instructions, and the overall system shall be placed on the above-described plywood platform. If installation instructions are not provided by the heat pump manufacturer, uninsulated 8 foot (2.4 m) long connecting hoses having an inside diameter of 5/8 inch (1.6 cm) shall be used to connect the storage tank and the heat pump water heater. With the exception of using the storage tank described in section 4.10 of this appendix, the same requirements shall apply for water heaters requiring a storage tank. The testing of the water heater shall occur in an area that is protected from drafts of more than 50 ft/min (0.25 m/s) from room ventilation registers, windows, or other external sources of air movement.

4.2 Water Supply. Connect the water heater to a water supply capable of delivering water at conditions as specified in sections 2.3 and 2.6 of this appendix.

4.3 Water Inlet and Outlet Configuration. For freestanding water heaters that are taller than 36 inches (91.4 cm), inlet and outlet piping connections shall be configured in a manner consistent with Figures 1 and 2 of section 7 of this appendix. Inlet and outlet piping connections for wall-mounted water heaters shall be consistent with Figure 3 of section 7 of this appendix. For freestanding water heaters that are 36 inches or less in height and not supplied as part of a counter-top enclosure (commonly referred to as an under-the-counter model), inlet and outlet piping shall be installed in a manner consistent with Figures 4, 5, or 6 of section 7 of this appendix. For water heaters that are supplied with a counter-top enclosure, inlet and outlet piping shall be made in a manner consistent with Figures 7a and 7b of section 7 of this appendix, respectively. The vertical piping noted in Figures 7a and 7b shall be located (whether inside the enclosure or along the outside in a recessed channel) in accordance with the manufacturer-published installation instructions.

All dimensions noted in Figures 1 through 7 of section 7 of this appendix must be achieved. All piping between the water heater and inlet and outlet temperature sensors, noted as TIN and TOUT in the figures, shall be Type “L” hard copper having the same diameter as the connections on the water heater. Unions may be used to facilitate installation and removal of the piping arrangements. Install a pressure gauge and diaphragm expansion tank in the supply water piping at a location upstream of the inlet temperature sensor. Install an appropriately rated pressure and temperature relief valve on all water heaters at the port specified by the manufacturer. Discharge piping for the relief valve must be non-metallic. If heat traps, piping insulation, or pressure relief valve insulation are supplied with the water heater, they must be installed for testing. Except when using a simulated wall, provide sufficient clearance such that none of the piping contacts other surfaces in the test room.

At the discretion of the test laboratory, the mass or water delivered may be measured on either the inlet or outlet of the water heater.

For water heaters designed to be used with a mixing valve and that do not have a self-contained mixing valve, a mixing valve shall be installed according to the water heater and/or mixing valve manufacturer's installation instructions. If permitted by the water heater and mixing valve manufacturer's instructions, the mixing valve and cold water junction may be installed where the elbows are located in the outlet and inlet line, respectively. If there are no installation instructions for the mixing valve in the water heater or mixing valve manufacturer's instructions, then the mixing valve shall be installed on the outlet line and the cold water shall be supplied from the inlet line from a junction installed downstream from the location where the inlet water temperature is measured. The outlet water temperature, water flow rate, and/or mass measuring instrumentation, if installed on the outlet side of the water heater, shall be installed downstream from the mixing valve.

4.4 Fuel and/or Electrical Power and Energy Consumption. Install one or more instruments that measure, as appropriate, the quantity and rate of electrical energy and/or fossil fuel consumption in accordance with section 3 of this appendix.

4.5 Internal Storage Tank Temperature Measurements. For water heaters with rated storage volumes greater than or equal to 20 gallons, install six temperature measurement sensors inside the water heater tank with a vertical distance of at least 4 inches (100 mm) between successive sensors. For water heaters with rated storage volumes between 2 and 20 gallons, install three temperature measurement sensors inside the water heater tank. Position a temperature sensor at the vertical midpoint of each of the six equal volume nodes within a tank larger than 20 gallons or the three equal volume nodes within a tank between 2 and 20 gallons. Nodes designate the equal volumes used to evenly partition the total volume of the tank. As much as is possible, the temperature sensor should be positioned away from any heating elements, anodic protective devices, tank walls, and flue pipe walls. If the tank cannot accommodate six temperature sensors and meet the installation requirements specified in this section, install the maximum number of sensors that comply with the installation requirements. Install the temperature sensors through:

(a) The anodic device opening;

(b) The relief valve opening; or

(c) The hot water outlet.

If installed through the relief valve opening or the hot water outlet, a tee fitting or outlet piping, as applicable, must be installed as close as possible to its original location. If the relief valve temperature sensor is relocated, and it no longer extends into the top of the tank, install a substitute relief valve that has a sensing element that can reach into the tank. If the hot water outlet includes a heat trap, install the heat trap on top of the tee fitting. Cover any added fittings with thermal insulation having an R value between 4 and 8 h·ft 2· °F/Btu (0.7 and 1.4 m 2· °C/W). If temperature measurement sensors cannot be installed within the water heater, follow the alternate procedures in section 5.4.2.2 of this appendix.

4.6 Ambient Air Temperature Measurement. Install an ambient air temperature sensor at the vertical midpoint of the water heater and approximately 2 feet (610 mm) from the surface of the water heater. Shield the sensor against radiation.

4.7 Inlet and Outlet Water Temperature Measurements. Install temperature sensors in the cold-water inlet pipe and hot-water outlet pipe as shown in Figures 1, 2, 3, 4, 5, 6, 7a, and 7b of section 7 of this appendix, as applicable.

4.8 Flow Control. Install a valve or valves to provide flow as specified in sections 5.3 and 5.4 of this appendix.

4.9 Flue Requirements.

4.9.1 Gas-Fired Water Heaters. Establish a natural draft in the following manner. For gas-fired water heaters with a vertically discharging draft hood outlet, connect to the draft hood outlet a 5-foot (1.5-meter) vertical vent pipe extension with a diameter equal to the largest flue collar size of the draft hood. For gas-fired water heaters with a horizontally discharging draft hood outlet, connect to the draft hood outlet a 90-degree elbow with a diameter equal to the largest flue collar size of the draft hood, connect a 5-foot (1.5-meter) length of vent pipe to that elbow, and orient the vent pipe to discharge vertically upward. Install direct-vent gas-fired water heaters with venting equipment specified by the manufacturer in the I&O manual using the minimum vertical and horizontal lengths of vent pipe recommended by the manufacturer.

4.9.2 Oil-Fired Water Heaters. Establish a draft at the flue collar at the value specified by the manufacturer in the I&O manual. Establish the draft by using a sufficient length of vent pipe connected to the water heater flue outlet, and directed vertically upward. For an oil-fired water heater with a horizontally discharging draft hood outlet, connect to the draft hood outlet a 90-degree elbow with a diameter equal to the largest flue collar size of the draft hood, connect to the elbow fitting a length of vent pipe sufficient to establish the draft, and orient the vent pipe to discharge vertically upward. Direct-vent oil-fired water heaters should be installed with venting equipment as specified by the manufacturer in the I&O manual, using the minimum vertical and horizontal lengths of vent pipe recommended by the manufacturer.

4.10 Storage Tank Requirement for Water Heaters Requiring a Storage Tank (i.e., Circulating Water Heaters). On or after May 6, 2029, when testing a gas-fired, oil-fired, or electric resistance circulating water heater (i.e., any circulating water heater that does not use a heat pump), the tank to be used for testing shall be an unfired hot water storage tank having volume between 80 and 120 gallons (364-546 liters) determined using the method specified in section 5.2.1 of this appendix that meets but does not exceed the minimum energy conservation standards required according to § 431.110 of this chapter. When testing a heat pump circulating water heater, the tank to be used for testing shall be an electric storage water heater that has a measured volume of 30 gallons (±5 gallons), has a First-Hour Rating less than 51 gallons resulting in classification under the low draw pattern, and has a rated UEF equal to the minimum UEF standard specified at § 430.32(d), rounded to the nearest 0.01. The operational mode of the heat pump circulating water heater and storage water heater paired system shall be set in accordance with section 5.1.1 of this appendix. If the circulating water heater is supplied with a separate non-integrated circulating pump, install this pump as per the manufacturer's installation instructions and include its power consumption in energy use measurements.

4.11 External Communication. If the water heater can connect to an external network or controller, any external communication or connection shall be disabled for the duration of testing; however, the communication module shall remain in an “on” state.

5. Test Procedures.

5.1 Operational Mode Selection. For water heaters that allow for multiple user-selected operational modes, all procedures specified in this appendix shall be carried out with the water heater in the same operational mode (i.e., only one mode).

5.1.1 Testing at Normal Setpoint. The operational mode shall be the default mode (or similarly named, suggested mode for normal operation) as defined by the manufacturer in the I&O manual for giving selection guidance to the consumer. For heat pump water heaters, if a default mode is not defined in the product literature, each test shall be conducted under an operational mode in which both the heat pump and any electric resistance back-up heating element(s) are activated by the unit's control scheme, and which can achieve the internal storage tank temperature specified in this test procedure; if multiple operational modes meet these criteria, the water heater shall be tested under the most energy-intensive mode. If no default mode is specified and the unit does not offer an operational mode that utilizes both the heat pump and the electric resistance back-up heating element(s), the first-hour rating test and the 24-hour simulated-use test shall be tested in heat-pump-only mode. For other types of water heaters where a default mode is not specified, test the unit in all modes and rate the unit using the results of the most energy-intensive mode.

5.1.2 High Temperature Testing. This paragraph applies to electric storage water heaters capable of achieving a Tmax,1 above 135 °F. The following exceptions apply:

(1) Electric storage water heaters that do not have a permanent mode or setting in which the water heater is capable of heating and storing water above 135 °F (as measured by Tmax,1), where permanent mode or setting means a mode of operation that is continuous and does not require any external consumer intervention to maintain for longer than 120 hours;

(2) Electric storage water heaters that meet the definition of “heat pump-type” water heater at § 430.2;

(3) Electric storage water heaters that are only capable of heating the stored water above 135 °F in response to instructions received from a utility or third-party demand-response program.

(4) Electric storage water heaters with measured storage volumes (Vst) less than 20 gallons or greater than 55 gallons.

This paragraph may optionally apply to electric heat pump water heaters for voluntary representations of high-temperature operation only.

For those equipped with factory-installed or built-in mixing valves, set the unit to maintain the highest mean tank temperature possible while delivering water at 125 °F ±5 °F. For those not so equipped, install an ASSE 1017-certified mixing valve in accordance with the provisions in section 4.3 of this appendix and adjust the valve to deliver water at 125 °F ±5 °F when the water heater is operating at its highest storage tank temperature setpoint. Maintain this setting throughout the entirety of the test.

5.2 Water Heater Preparation.

5.2 1 Determination of Storage Tank Volume. For water heaters and separate storage tanks used for testing circulating water heaters, determine the storage capacity, Vst, of the water heater or separate storage tank under test, in gallons (liters), by subtracting the tare weight, Wt, (measured while the tank is empty) from the gross weight of the storage tank when completely filled with water at the supply water temperature specified in section 2.3 of this appendix, Wf, (with all air eliminated and line pressure applied as described in section 2.6 of this appendix) and dividing the resulting net weight by the density of water at the measured temperature.

5.2.2 Setting the Outlet Discharge Temperature.

5.2.2.1 Flow-Activated Water Heaters, including certain instantaneous water heaters and certain storage-type water heaters. Initiate normal operation of the water heater at the design power rating. Monitor the discharge water temperature and set to the value specified in section 2.5 of this appendix in accordance with the manufacturer's I&O manual. If the water heater is not capable of providing this discharge temperature when the flow rate is 1.7 gallons ± 0.25 gallons per minute (6.4 liters ± 0.95 liters per minute), then adjust the flow rate as necessary to achieve the specified discharge water temperature. Once the proper temperature control setting is achieved, the setting must remain fixed for the duration of the maximum GPM test and the 24-hour simulated-use test.

5.2.2.2 All Other Water Heaters.

5.2.2.2.1 Water Heaters with a Single Temperature Controller.

5.2.2.2.1.1 Water Heaters with Rated Volumes Less than 20 Gallons. Starting with a tank at the supply water temperature as specified in section 2.3 of this appendix, initiate normal operation of the water heater. After cut-out, initiate a draw from the water heater at a flow rate of 1.0 gallon ± 0.25 gallons per minute (3.8 liters ± 0.95 liters per minute) for 2 minutes. Starting 15 seconds after commencement of the draw, record the outlet temperature at 15-second intervals until the end of the 2-minute period. Determine whether the maximum outlet temperature is within the range specified in section 2.4 of this appendix. If not, turn off the water heater, adjust the temperature controller, and then drain and refill the tank with supply water at the temperature specified in section 2.3 of this appendix. Then, once again, initiate normal operation of the water heater, and repeat the 2-minute outlet temperature test following cut-out. Repeat this sequence until the maximum outlet temperature during the 2-minute test is within the range specified in section 2.4 of this appendix. Once the proper temperature control setting is achieved, the setting must remain fixed for the duration of the first-hour rating test and the 24-hour simulated-use test.

5.2.2.2.1.2 Water Heaters with Rated Volumes Greater than or Equal to 20 Gallons. Starting with a tank at the supply water temperature specified in section 2.3 of this appendix, initiate normal operation of the water heater. After cut-out, initiate a draw from the water heater at a flow rate of 1.7 gallons ± 0.25 gallons per minute (6.4 liters ± 0.95 liters per minute) for 5 minutes. Starting 15 seconds after commencement of the draw, record the outlet temperature at 15-second intervals until the end of the 5-minute period. Determine whether the maximum outlet temperature is within the range specified in section 2.4 of this appendix. If not, turn off the water heater, adjust the temperature controller, and then drain and refill the tank with supply water at the temperature specified in section 2.3 of this appendix. Then, once again, initiate normal operation of the water heater, and repeat the 5-minute outlet temperature test following cut-out. Repeat this sequence until the maximum outlet temperature during the 5-minute test is within the range specified in section 2.4 of this appendix. Once the proper temperature control setting is achieved, the setting must remain fixed for the duration of the first-hour rating test and the 24-hour simulated-use test.

5.2.2.2.2 Water Heaters with Two or More Temperature Controllers. Verify the temperature controller set-point while removing water in accordance with the procedure set forth for the first-hour rating test in section 5.3.3 of this appendix. The following criteria must be met to ensure that all temperature controllers are set to deliver water in the range specified in section 2.4 of this appendix:

(a) At least 50 percent of the water drawn during the first draw of the first-hour rating test procedure shall be delivered at a temperature within the range specified in section 2.4 of this appendix.

(b) No water is delivered above the range specified in section 2.4 of this appendix during first-hour rating test.

(c) The delivery temperature measured 15 seconds after commencement of each draw begun prior to an elapsed time of 60 minutes from the start of the test shall be within the range specified in section 2.4 of this appendix.

If these conditions are not met, turn off the water heater, adjust the temperature controllers, and then drain and refill the tank with supply water at the temperature specified in section 2.3 of this appendix. Repeat the procedure described at the start of section 5.2.2.2.2 of this appendix until the criteria for setting the temperature controllers is met.

If the conditions stated above are met, the data obtained during the process of verifying the temperature control set-points may be used in determining the first-hour rating provided that all other conditions and methods required in sections 2 and 5.2.4 of this appendix in preparing the water heater were followed.

5.2.3 Power Input Determination. For all water heaters except electric types, initiate normal operation (as described in section 5.1 of this appendix) and determine the power input, P, to the main burners (including pilot light power, if any) after 15 minutes of operation. Adjust all burners to achieve an hourly Btu (kJ) rating that is within ±2% of the maximum input rate value specified by the manufacturer. For an oil-fired water heater, adjust the burner to give a CO2 reading recommended by the manufacturer and an hourly Btu (kJ) rating that is within ±2% of the maximum input rate specified by the manufacturer. Smoke in the flue may not exceed No. 1 smoke as measured by the procedure in ASTM D2156 (R2018), including the conditions as specified in ASTM E97-1987 as referenced in ASTM D2156 (R2018). If the input rating is not within ±2%, first increase or decrease the fuel pressure within the tolerances specified in section 2.7.2, 2.7.3 or 2.7.4 (as applicable) of this appendix until it is ±2% of the maximum input rate value specified by the manufacturer. If, after adjusting the fuel pressure, the fuel input rate cannot be achieved within ±2 percent of the maximum input rate value specified by the manufacturer, for gas-fired models increase or decrease the gas supply pressure within the range specified by the manufacturer. Finally, if the measured fuel input rate is still not within ±2 percent of the maximum input rate value specified by the manufacturer, modify the gas inlet orifice, if so equipped, as necessary to achieve a fuel input rate that is within ±2 percent of the maximum input rate value specified by the manufacturer.

5.2.4 Soak-In Period for Water Heaters with Rated Storage Volumes Greater than or Equal to 2 Gallons. For water heaters with a rated storage volume greater than or equal to 2 gallons (7.6 liters), the water heater must sit filled with water, connected to a power source, and without any draws taking place for at least 12 hours after initially being energized so as to achieve the nominal temperature set-point within the tank and with the unit connected to a power source.

5.3 Delivery Capacity Tests.

5.3.1 General. For flow-activated water heaters, conduct the maximum GPM test, as described in section 5.3.2, Maximum GPM Rating Test for Flow-Activated Water Heaters, of this appendix. For all other water heaters, conduct the first-hour rating test as described in section 5.3.3 of this appendix.

5.3.2 Maximum GPM Rating Test for Flow-Activated Water Heaters. Establish normal water heater operation at the design power rating with the discharge water temperature set in accordance with section 5.2.2.1 of this appendix.

For this 10-minute test, either collect the withdrawn water for later measurement of the total mass removed or use a water meter to directly measure the water mass of volume removed. Initiate water flow through the water heater and record the inlet and outlet water temperatures beginning 15 seconds after the start of the test and at subsequent 5-second intervals throughout the duration of the test. At the end of 10 minutes, turn off the water. Determine and record the mass of water collected, M10m, in pounds (kilograms), or the volume of water, V10m, in gallons (liters).

5.3.3 First-Hour Rating Test.

5.3.3.1 General. During hot water draws for water heaters with rated storage volumes greater than or equal to 20 gallons, remove water at a rate of 3.0 ± 0.25 gallons per minute (11.4 ± 0.95 liters per minute). During hot water draws for water heaters with rated storage volumes below 20 gallons, remove water at a rate of 1.5 ± 0.25 gallon per minute (5.7 ± 0.95 liters per minute). Collect the water in a container that is large enough to hold the volume removed during an individual draw and is suitable for weighing at the termination of each draw to determine the total volume of water withdrawn. As an alternative to collecting the water, a water meter may be used to directly measure the water mass or volume withdrawn during each draw.

5.3.3.2 Draw Initiation Criteria. Begin the first-hour rating test by starting a draw on the water heater. After completion of this first draw, initiate successive draws based on the following criteria. For gas-fired and oil-fired water heaters, initiate successive draws when the temperature controller acts to reduce the supply of fuel to the main burner. For electric water heaters having a single element or multiple elements that all operate simultaneously, initiate successive draws when the temperature controller acts to reduce the electrical input supplied to the element(s). For electric water heaters having two or more elements that do not operate simultaneously, initiate successive draws when the applicable temperature controller acts to reduce the electrical input to the energized element located vertically highest in the storage tank. For heat pump water heaters that do not use supplemental, resistive heating, initiate successive draws immediately after the electrical input to the compressor is reduced by the action of the water heater's temperature controller. For heat pump water heaters that use supplemental resistive heating, initiate successive draws immediately after the electrical input to the first of either the compressor or the vertically highest resistive element is reduced by the action of the applicable water heater temperature controller. This draw initiation criterion for heat pump water heaters that use supplemental resistive heating, however, shall only apply when the water located above the thermostat at cut-out is heated to within the range specified in section 2.4 of this appendix. If this criterion is not met, then the next draw should be initiated once the heat pump compressor cuts out.

5.3.3.3 Test Sequence. Establish normal water heater operation. If the water heater is not presently operating, initiate a draw. The draw may be terminated any time after cut-in occurs. After cut-out occurs (i.e., all temperature controllers are satisfied), if the water heater can have its internal tank temperatures measured, record the internal storage tank temperature at each sensor described in section 4.5 of this appendix every one minute, and determine the mean tank temperature by averaging the values from these sensors.

Initiate a draw after a maximum mean tank temperature (the maximum of the mean temperatures of the individual sensors) has been observed following a cut-out. If the water heater cannot have its internal tank temperatures measured, wait 5 minutes after cut-out. Record the time when the draw is initiated and designate it as an elapsed time of zero (τ* = 0). (The superscript * is used to denote variables pertaining to the first-hour rating test). Record the outlet water temperature beginning 15 seconds after the draw is initiated and at 5-second intervals thereafter until the draw is terminated. Determine the maximum outlet temperature that occurs during this first draw and record it as T*max,1. For the duration of this first draw and all successive draws, in addition, monitor the inlet temperature to the water heater to ensure that the required supply water temperature test condition specified in section 2.3 of this appendix is met. Terminate the hot water draw when the outlet temperature decreases to T*max,1−15 °F (T*max,1−8.3 °C). (Note, if the outlet temperature does not decrease to T*max,1−15 °F (T*max,1−8.3 °C) during the draw, then hot water would be drawn continuously for the duration of the test. In this instance, the test would end when the temperature decreases to T*max,1−15 °F (T*max,1−8.3 °C) after the electrical power and/or fuel supplied to the water heater is shut off, as described in the following paragraphs.) Record this temperature as T*min,1. Following draw termination, determine the average outlet water temperature and the mass or volume removed during this first draw and record them as T*del,i and M*1 or V*1, respectively.

Initiate a second and, if applicable, successive draw(s) each time the applicable draw initiation criteria described in section 5.3.3.2 of this appendix are satisfied. As required for the first draw, record the outlet water temperature 15 seconds after initiating each draw and at 5-second intervals thereafter until the draw is terminated. Determine the maximum outlet temperature that occurs during each draw and record it as T*max,i, where the subscript i refers to the draw number. Terminate each hot water draw when the outlet temperature decreases to T*max,i−15 °F (T*max,i−8.3 °C). Record this temperature as T*min,i. Calculate and record the average outlet temperature and the mass or volume removed during each draw (T*del,i and M*i or V*i, respectively). Continue this sequence of draw and recovery until one hour after the start of the test, then shut off the electrical power and/or fuel supplied to the water heater.

If a draw is occurring at one hour from the start of the test, continue this draw until the outlet temperature decreases to T*max,n−15 °F (T*max,n−8.3 °C), at which time the draw shall be immediately terminated. (The subscript n shall be used to denote measurements associated with the final draw.) If a draw is not occurring one hour after the start of the test, initiate a final draw at one hour, regardless of whether the criteria described in section 5.3.3.2 of this appendix are satisfied. This draw shall proceed for a minimum of 30 seconds and shall terminate when the outlet temperature first indicates a value less than or equal to the cut-off temperature used for the previous draw (T*min,n−1). If an outlet temperature greater than T*min,n−1 is not measured within 30 seconds of initiation of the draw, zero additional credit shall be given towards first-hour rating (i.e., M*n = 0 or V*n = 0) based on the final draw. After the final draw is terminated, calculate and record the average outlet temperature and the mass or volume removed during the final draw (T*del,n and M*n or V*n, respectively).

5.4 24-Hour Simulated-Use Test.

5.4.1 Selection of Draw Pattern. The water heater will be tested under a draw profile that depends upon the first-hour rating obtained following the test prescribed in section 5.3.3 of this appendix, or the maximum GPM rating obtained following the test prescribed in section 5.3.2 of this appendix, whichever is applicable. For water heaters that have been tested according to the first-hour rating procedure, one of four different patterns shall be applied based on the measured first-hour rating, as shown in Table I of this section. For water heater that have been tested according to the maximum GPM rating procedure, one of four different patterns shall be applied based on the maximum GPM, as shown in Table II of this section.

Table I—Draw Pattern To Be Used Based on First-Hour Rating

First-hour rating greater than or equal to: . . . and first-hour rating less than: Draw pattern to be used in the 24-hour simulated-use test 0 gallons18 gallonsVery-Small-Usage (Table III.1). 18 gallons51 gallonsLow-Usage (Table III.2). 51 gallons75 gallonsMedium-Usage (Table III.3). 75 gallonsNo upper limitHigh-Usage (Table III.4).

Table II—Draw Pattern To Be Used Based on Maximum GPM Rating

Maximum GPM rating greater than or equal to: and maximum GPM rating less than: Draw pattern to be used in the 24-hour simulated-use test 0 gallons/minute1.7 gallons/minuteVery-Small-Usage (Table III.1). 1.7 gallons/minute2.8 gallons/minuteLow-Usage (Table III.2). 2.8 gallons/minute4 gallons/minuteMedium-Usage (Table III.3). 4 gallons/minuteNo upper limitHigh-Usage (Table III.4).

The draw patterns are provided in Tables III.1 through III.4 in section 5.5 of this appendix. Use the appropriate draw pattern when conducting the test sequence provided in section 5.4.2 of this appendix for water heaters with rated storage volumes greater than or equal to 2 gallons or section 5.4.3 of this appendix for water heaters with rated storage volumes less than 2 gallons.

5.4.2 Test Sequence for Water Heater With Rated Storage Volume Greater Than or Equal to 2 Gallons.

If the water heater is turned off, fill the water heater with supply water at the temperature specified in section 2.3 of this appendix and maintain supply water pressure as described in section 2.6 of this appendix. Turn on the water heater and associated heat pump unit, if present. If turned on in this fashion, the soak-in period described in section 5.2.4 of this appendix shall be implemented. If the water heater has undergone a first-hour rating test prior to conduct of the 24-hour simulated-use test, allow the water heater to fully recover after completion of that test such that the main burner, heating elements, or heat pump compressor of the water heater are no longer raising the temperature of the stored water. In all cases, the water heater shall sit idle for 1 hour prior to the start of the 24-hour test; during which time no water is drawn from the unit, and there is no energy input to the main heating elements, heat pump compressor, and/or burners.

For water heaters that can have their internal storage tank temperature measured directly, perform testing in accordance with the instructions in section 5.4.2.1 of this appendix. For water heaters that cannot have their internal tank temperatures measured, perform testing in accordance with the instructions in section 5.4.2.2. of this appendix.

5.4.2.1 Water Heaters Which Can Have Internal Storage Tank Temperature Measured Directly.

After the 1-hour period specified in section 5.4.2 of this appendix, the 24-hour simulated-use test will begin. One minute prior to the start of the 24-hour simulated-use test, record the mean tank temperature (T0).

At the start of the 24-hour simulated-use test, record the electrical and/or fuel measurement readings, as appropriate. Begin the 24-hour simulated-use test by withdrawing the volume specified in the appropriate table in section 5.5 of this appendix (i.e., Table III.1, Table III.2, Table III.3, or Table III.4, depending on the first-hour rating or maximum GPM rating) for the first draw at the flow rate specified in the applicable table. Record the time when this first draw is initiated and assign it as the test elapsed time (τ) of zero (0). Record the average storage tank and ambient temperature every minute throughout the 24-hour simulated-use test. At the elapsed times specified in the applicable draw pattern table in section 5.5 of this appendix for a particular draw pattern, initiate additional draws pursuant to the draw pattern, removing the volume of hot water at the prescribed flow rate specified by the table. The maximum allowable deviation from the specified volume of water removed for any single draw taken at a nominal flow rate of 1.0 GPM or 1.7 GPM is ±0.1 gallons (±0.4 liters). The maximum allowable deviation from the specified volume of water removed for any single draw taken at a nominal flow rate of 3.0 GPM is ±0.25 gallons (0.9 liters). The quantity of water withdrawn during the last draw shall be increased or decreased as necessary such that the total volume of water withdrawn equals the prescribed daily amount for that draw pattern ±1.0 gallon (±3.8 liters). If this adjustment to the volume drawn during the last draw results in no draw taking place, the test is considered invalid.

All draws during the 24-hour simulated-use test shall be made at the flow rates specified in the applicable draw pattern table in section 5.5 of this appendix, within a tolerance of ±0.25 gallons per minute (±0.9 liters per minute). Measurements of the inlet and outlet temperatures shall be made 15 seconds after the draw is initiated and at every subsequent 3-second interval throughout the duration of each draw. Calculate and record the mean of the hot water discharge temperature and the cold water inlet temperature for each draw Tdel,i and Tin,i). Determine and record the net mass or volume removed (Mi or Vi), as appropriate, after each draw.

The first recovery period is the time from the start of the 24-hour simulated-use test and continues during the temperature rise of the stored water until the first cut-out; if the cut-out occurs during a subsequent draw, the first recovery period includes the time until the draw of water from the tank stops. If, after the first cut-out occurs but during a subsequent draw, a subsequent cut-in occurs prior to the draw completion, the first recovery period includes the time until the subsequent cut-out occurs, prior to another draw. The first recovery period may continue until a cut-out occurs when water is not being removed from the water heater or a cut-out occurs during a draw and the water heater does not cut-in prior to the end of the draw.

At the end of the first recovery period, record the maximum mean tank temperature observed after cut-out (Tmax,1). At the end of the first recovery period, record the total energy consumed by the water heater from the beginning of the test (Qr), including all fossil fuel and/or electrical energy use, from the main heat source and auxiliary equipment including, but not limited to, burner(s), resistive elements(s), compressor, fan, controls, pump, etc., as applicable.

The start of the portion of the test during which the standby loss coefficient is determined depends upon whether the unit has fully recovered from the first draw cluster. If a recovery is occurring at or within five minutes after the end of the final draw in the first draw cluster, as identified in the applicable draw pattern table in section 5.5 of this appendix, then the standby period starts when a maximum mean tank temperature is observed starting five minutes after the end of the recovery period that follows that draw. If a recovery does not occur at or within five minutes after the end of the final draw in the first draw cluster, as identified in the applicable draw pattern table in section 5.5 of this appendix, then the standby period starts five minutes after the end of that draw. Determine and record the total electrical energy and/or fossil fuel consumed from the beginning of the test to the start of the standby period (Qsu,0).

In preparation for determining the energy consumed during standby, record the reading given on the electrical energy (watt-hour) meter, the gas meter, and/or the scale used to determine oil consumption, as appropriate. Record the mean tank temperature at the start of the standby period (Tsu,0). At 1-minute intervals, record ambient temperature, the electric and/or fuel instrument readings, and the mean tank temperature until the next draw is initiated. The end of the standby period is when the final mean tank temperature is recorded, as described. Just prior to initiation of the next draw, record the mean tank temperature (Tsu,f). If the water heater is undergoing recovery when the next draw is initiated, record the mean tank temperature (Tsu,f) at the minute prior to the start of the recovery. Determine the total electrical energy and/or fossil fuel energy consumption from the beginning of the test to the end of the standby period (Qsu,f). Record the time interval between the start of the standby period and the end of the standby period (τstby,1).

Following the final draw of the prescribed draw pattern and subsequent recovery, allow the water heater to remain in the standby mode until exactly 24 hours have elapsed since the start of the 24-hour simulated-use test (i.e., since τ = 0). During the last hour of the 24-hour simulated-use test (i.e., hour 23 of the 24-hour simulated-use test), power to the main burner, heating element, or compressor shall be disabled. At 24 hours, record the reading given by the gas meter, oil meter, and/or the electrical energy meter as appropriate. Determine the fossil fuel and/or electrical energy consumed during the entire 24-hour simulated-use test and designate the quantity as Q.

In the event that the recovery period continues from the end of the last draw of the first draw cluster until the subsequent draw, the standby period will start after the end of the first recovery period after the last draw of the 24-hour simulated-use test, when the temperature reaches the maximum mean tank temperature, though no sooner than five minutes after the end of this recovery period. The standby period shall last eight hours, so testing may extend beyond the 24-hour duration of the 24-hour simulated-use test. Determine and record the total electrical energy and/or fossil fuel consumed from the beginning of the 24-hour simulated-use test to the start of the 8-hour standby period (Qsu,0). In preparation for determining the energy consumed during standby, record the reading(s) given on the electrical energy (watt-hour) meter, the gas meter, and/or the scale used to determine oil consumption, as appropriate. Record the mean tank temperature at the start of the standby period (Tsu,0). Record the mean tank temperature, the ambient temperature, and the electric and/or fuel instrument readings at 1-minute intervals until the end of the 8-hour period. Record the mean tank temperature at the end of the 8-hour standby period (Tsu,f). If the water heater is undergoing recovery at the end of the standby period, record the mean tank temperature (Tsu,f) at the minute prior to the start of the recovery, which will mark the end of the standby period. Determine the total electrical energy and/or fossil fuel energy consumption from the beginning of the test to the end of the standby period (Qsu,f). Record the time interval between the start of the standby period and the end of the standby period as τstby,1. Record the average ambient temperature from the start of the standby period to the end of the standby period (Ta,stby,1). Record the average mean tank temperature from the start of the standby period to the end of the standby period (Tt,stby,1).

If the standby period occurred at the end of the first recovery period after the last draw of the 24-hour simulated-use test, allow the water heater to remain in the standby mode until exactly 24 hours have elapsed since the start of the 24-hour simulated-use test (i.e., since τ = 0) or the end of the standby period, whichever is longer. At 24 hours, record the mean tank temperature (T24) and the reading given by the gas meter, oil meter, and/or the electrical energy meter as appropriate. If the water heater is undergoing a recovery at 24 hours, record the reading given by the gas meter, oil meter, and/or electrical energy meter, as appropriate, and the mean tank temperature (T24) at the minute prior to the start of the recovery. Determine the fossil fuel and/or electrical energy consumed during the 24 hours and designate the quantity as Q.

Record the time during which water is not being withdrawn from the water heater during the entire 24-hour period (τstby,2). When the standby period occurs after the last draw of the 24-hour simulated-use test, the test may extend past hour 24. When this occurs, the measurements taken after hour 24 apply only to the calculations of the standby loss coefficient. All other measurements during the time between hour 23 and hour 24 remain the same.

5.4.2.2 Water Heaters Which Cannot Have Internal Storage Tank Temperature Measured Directly.

After the water heater has undergone a 1-hour idle period (as described in section 5.4.2 of this appendix), deactivate the burner, compressor, or heating element(s).

Remove water from the storage tank by performing a continuous draw at the flow rate specified for the first draw of applicable draw pattern for the 24-hour simulated use test in section 5.5 of this appendix within a tolerance of ±0.25 gallons per minute (±0.9 liters per minute). While removing the hot water, measure the inlet and outlet temperature after initiating the draw at 3-second intervals. Remove water until the outlet water temperature is within ±2 °F (±1.1 °C) of the inlet water temperature for 15 consecutive seconds. Determine the mean tank temperature using section 6.3.77 of this appendix and assign this value of Tst for T0, Tmax,1, and Tsu,0.

After completing the draw, reactivate the burner, compressor, or heating elements(s) and allow the unit to fully recover such that the main burner, heating elements, or heat pump compressor is no longer raising the temperature of the stored water. Let the water heater sit idle again for 1 hour prior to beginning the 24-hour test, during which time no water shall be drawn from the unit, and there shall be no energy input to the main heating elements. After the 1-hour period, the 24-hour simulated-use test will begin.

At the start of the 24-hour simulated-use test, record the electrical and/or fuel measurement readings, as appropriate. Begin the 24-hour simulated-use test by withdrawing the volume specified in the appropriate table in section 5.5 of this appendix (i.e., Table III.1, Table III.2, Table III.3, or Table III.4, depending on the first-hour rating or maximum GPM rating) for the first draw at the flow rate specified in the applicable table. Record the time when this first draw is initiated and assign it as the test elapsed time (τ) of zero (0). Record the average ambient temperature every minute throughout the 24-hour simulated-use test. At the elapsed times specified in the applicable draw pattern table in section 5.5 of this appendix for a particular draw pattern, initiate additional draws pursuant to the draw pattern, removing the volume of hot water at the prescribed flow rate specified by the table. The maximum allowable deviation from the specified volume of water removed for any single draw taken at a nominal flow rate of 1.0 GPM or 1.7 GPM is ± 0.1 gallons (± 0.4 liters). The maximum allowable deviation from the specified volume of water removed for any single draw taken at a nominal flow rate of 3.0 GPM is ± 0.25 gallons (0.9 liters). The quantity of water withdrawn during the last draw shall be increased or decreased as necessary such that the total volume of water withdrawn equals the prescribed daily amount for that draw pattern ± 1.0 gallon (± 3.8 liters). If this adjustment to the volume drawn during the last draw results in no draw taking place, the test is considered invalid.

All draws during the 24-hour simulated-use test shall be made at the flow rates specified in the applicable draw pattern table in section 5.5 of this appendix, within a tolerance of ±0.25 gallons per minute (±0.9 liters per minute). Measurements of the inlet and outlet temperatures shall be made 15 seconds after the draw is initiated and at every subsequent 3-second interval throughout the duration of each draw. Calculate and record the mean of the hot water discharge temperature and the cold water inlet temperature for each draw Tdel,i and Tin,i). Determine and record the net mass or volume removed (Mi or Vi), as appropriate, after each draw.

The first recovery period is the time from the start of the 24-hour simulated-use test and continues until the first cut-out; if the cut-out occurs during a subsequent draw, the first recovery period includes the time until the draw of water from the tank stops. If, after the first cut-out occurs but during a subsequent draw, a subsequent cut-in occurs prior to the draw completion, the first recovery period includes the time until the subsequent cut-out occurs, prior to another draw. The first recovery period may continue until a cut-out occurs when water is not being removed from the water heater or a cut-out occurs during a draw and the water heater does not cut-in prior to the end of the draw.

At the end of the first recovery period, record the total energy consumed by the water heater from the beginning of the test (Qr), including all fossil fuel and/or electrical energy use, from the main heat source and auxiliary equipment including, but not limited to, burner(s), resistive elements(s), compressor, fan, controls, pump, etc., as applicable.

The standby period begins at five minutes after the first time a recovery ends following last draw of the simulated-use test and shall continue for 8 hours. At the end of the 8-hour standby period, record the total amount of time elapsed since the start of the 24-hour simulated-use test (i.e., since τ = 0).

Determine and record the total electrical energy and/or fossil fuel consumed from the beginning of the 24-hour simulated-use test to the start of the 8-hour standby period (Qsu,0). In preparation for determining the energy consumed during standby, record the reading(s) given on the electrical energy (watt-hour) meter, the gas meter, and/or the scale used to determine oil consumption, as appropriate. Record the ambient temperature and the electric and/or fuel instrument readings at 1-minute intervals until the end of the 8-hour period. At the 8-hour mark, deactivate the water heater before drawing water from the tank. Remove water from the storage tank by performing a continuous draw atthe flow rate specified for the first draw of applicable draw pattern for the 24-hour simulated use test in section 5.5 of this appendix within a tolerance of ±0.25 gallons per minute (±0.9 liters per minute). While removing the hot water, measure the inlet and outlet temperature after initiating the draw at 3-second intervals. Remove water until the outlet water temperature is within ±2 °F (±1.1 °C) of the inlet water temperature for 15 consecutive seconds. Determine the mean tank temperature using section 6.3.77 of this appendix and assign this value of Tst for Tsu,f and T24.

Determine the total electrical energy and/or fossil fuel energy consumption from the beginning of the test to the end of the standby period (Qsu,f). Record the time interval between the start of the standby period and the end of the standby period as τstby,1. Record the average ambient temperature from the start of the standby period to the end of the standby period (Ta,stby,1). The average mean tank temperature from the start of the standby period to the end of the standby period (Tt,stby,1) shall be the average of Tsu,0 and Tsu,f.

5.4.3 Test Sequence for Water Heaters With Rated Storage Volume Less Than 2 Gallons.

Establish normal operation with the discharge water temperature at 125 °F ± 5 °F (51.7 °C ± 2.8 °C) and set the flow rate as determined in section 5.2 of this appendix. Prior to commencement of the 24-hour simulated-use test, the unit shall remain in an idle state in which controls are active but no water is drawn through the unit for a period of one hour. With no draw occurring, record the reading given by the gas meter and/or the electrical energy meter as appropriate. Begin the 24-hour simulated-use test by withdrawing the volume specified in Tables III.1 through III.4 of section 5.5 of this appendix for the first draw at the flow rate specified. Record the time when this first draw is initiated and designate it as an elapsed time, τ, of 0. At the elapsed times specified in Tables III.1 through III.4 for a particular draw pattern, initiate additional draws, removing the volume of hot water at the prescribed flow rate specified in Tables III.1 through III.4. The maximum allowable deviation from the specified volume of water removed for any single draw taken at a nominal flow rate less than or equal to 1.7 GPM (6.4 L/min) is ±0.1 gallons (±0.4 liters). The maximum allowable deviation from the specified volume of water removed for any single draw taken at a nominal flow rate of 3.0 GPM (11.4 L/min) is ±0.25 gallons (0.9 liters). The quantity of water drawn during the final draw shall be increased or decreased as necessary such that the total volume of water withdrawn equals the prescribed daily amount for that draw pattern ±1.0 gallon (±3.8 liters). If this adjustment to the volume drawn in the last draw results in no draw taking place, the test is considered invalid.

All draws during the 24-hour simulated-use test shall be made at the flow rates specified in the applicable draw pattern table in section 5.5 of this appendix within a tolerance of ±0.25 gallons per minute (±0.9 liters per minute) unless the unit being tested is flow-activated and has a rated Max GPM of less than 1 gallon per minute, in which case the tolerance shall be ±25% of the rated Max GPM. Measurements of the inlet and outlet water temperatures shall be made 15 seconds after the draw is initiated and at every 3-second interval thereafter throughout the duration of the draw. Calculate the mean of the hot water discharge temperature and the cold-water inlet temperature for each draw. Record the mass of the withdrawn water or the water meter reading, as appropriate, after each draw. At the end of the first recovery period following the first draw, determine and record the fossil fuel and/or electrical energy consumed, Qr. Following the final draw and subsequent recovery, allow the water heater to remain in the standby mode until exactly 24 hours have elapsed since the start of the test (i.e., since τ = 0). At 24 hours, record the reading given by the gas meter, oil meter, and/or the electrical energy meter, as appropriate. Determine the fossil fuel and/or electrical energy consumed during the entire 24-hour simulated-use test and designate the quantity as Q.

5.5 Draw Patterns.

The draw patterns to be imposed during 24-hour simulated-use tests are provided in Tables III.1 through III.4. Subject each water heater under test to one of these draw patterns based on its first-hour rating or maximum GPM rating, as discussed in section 5.4.1 of this appendix. Each draw pattern specifies the elapsed time in hours and minutes during the 24-hour test when a draw is to commence, the total volume of water in gallons (liters) that is to be removed during each draw, and the flow rate at which each draw is to be taken, in gallons (liters) per minute.

Table III.1—Very-Small-Usage Draw Pattern

Draw No. Time during test **
[hh:mm]
Volume
[gallons (L)]
Flow rate ***
[GPM (L/min)]
1 *0:002.0 (7.6)1 (3.8) 2 *1:001.0 (3.8)1 (3.8) 3 *1:050.5 (1.9)1 (3.8) 4 *1:100.5 (1.9)1 (3.8) 5 *1:150.5 (1.9)1 (3.8) 68:001.0 (3.8)1 (3.8) 78:152.0 (7.6)1 (3.8) 89:001.5 (5.7)1 (3.8) 99:151.0 (3.8)1 (3.8) Total Volume Drawn Per Day: 10 gallons (38 L)

* Denotes draws in first draw cluster.

** If a draw extends to the start of the subsequent draw, then the subsequent draw shall start when the required volume of the previous draw has been delivered.

*** Should the water heater have a maximum GPM rating less than 1 GPM (3.8 L/min), then all draws shall be implemented at a flow rate equal to the rated maximum GPM.

Table III.2—Low-Usage Draw Pattern

Draw No. Time during test
[hh:mm]
Volume
[gallons (L)]
Flow rate
[GPM (L/min)]
1 *0:0015.0 (56.8)1.7 (6.4) 2 *0:302.0 (7.6)1 (3.8) 3 *1:001.0 (3.8)1 (3.8) 410:306.0 (22.7)1.7 (6.4) 511:304.0 (15.1)1.7 (6.4) 612:001.0 (3.8)1 (3.8) 712:451.0 (3.8)1 (3.8) 812:501.0 (3.8)1 (3.8) 916:152.0 (7.6)1 (3.8) 1016:452.0 (7.6)1.7 (6.4) 1117:003.0 (11.4)1.7 (6.4) Total Volume Drawn Per Day: 38 gallons (144 L)

*Denotes draws in first draw cluster.

Table III.3—Medium-Usage Draw Pattern

Draw No. Time during test
[hh:mm]
Volume
[gallons (L)]
Flow Rate
[GPM (L/min)]
1 *0:0015.0 (56.8)1.7 (6.4) 2 *0:302.0 (7.6)1 (3.8) 3 *1:409.0 (34.1)1.7 (6.4) 410:309.0 (34.1)1.7 (6.4) 511:305.0 (18.9)1.7 (6.4) 612:001.0 (3.8)1 (3.8) 712:451.0 (3.8)1 (3.8) 812:501.0 (3.8)1 (3.8) 916:001.0 (3.8)1 (3.8) 1016:152.0 (7.6)1 (3.8) 1116:452.0 (7.6)1.7 (6.4) 1217:007.0 (26.5)1.7 (6.4) Total Volume Drawn Per Day: 55 gallons (208 L)

* Denotes draws in first draw cluster.

Table III.4—High-Usage Draw Pattern

Draw No. Time during test
[hh:mm]
Volume
[gallons (L)]
Flow rate
[GPM (L/min)]
1 *0:0027.0 (102)3 (11.4) 2 *0:302.0 (7.6)1 (3.8) 3 *0:401.0 (3.8)1 (3.8) 4 *1:409.0 (34.1)1.7 (6.4) 510:3015.0 (56.8)3 (11.4) 611:305.0 (18.9)1.7 (6.4) 712:001.0 (3.8)1 (3.8) 812:451.0 (3.8)1 (3.8) 912:501.0 (3.8)1 (3.8) 1016:002.0 (7.6)1 (3.8) 1116:152.0 (7.6)1 (3.8) 1216:302.0 (7.6)1.7 (6.4) 1316:452.0 (7.6)1.7 (6.4) 1417:0014.0 (53.0)3 (11.4) Total Volume Drawn Per Day: 84 gallons (318 L)

* Denotes draws in first draw cluster.

5.6 Optional Tests (Heat Pump-Type Water Heaters). Optional testing may be conducted on heat pump-type water heaters to determine EX. If optional testing is performed, conduct the additional 24-hour simulated use test(s) at one or multiple of the test conditions specified in section 2.8 of this appendix. Prior to conducting a 24-hour simulated use test at an optional condition, confirm the air and water conditions specified in section 2.8 are met and re-set the outlet discharge temperature in accordance with section 5.2.2 of this appendix. Perform the optional 24-hour simulated use test(s) in accordance with section 5.4 of this appendix using the same draw pattern used for the determination of UEF.

6. Computations.

6.1 First-Hour Rating Computation. For the case in which the final draw is initiated at or prior to one hour from the start of the test, the first-hour rating, Fhr, shall be computed using,

Where: n = the number of draws that are completed during the first-hour rating test. V*del,i = the volume of water removed during the ith draw of the first-hour rating test, gal (L) or, if the mass of water removed is being measured, Where: M*del,i = the mass of water removed during the ith draw of the first-hour rating test, lb (kg). ρdel,i = the density of water removed, evaluated at the average outlet water temperature measured during the ith draw of the first-hour rating test, (T*del,i), lb/gal (kg/L). or, if the volume of the water entering the water heater is being measured, Where: V*in,i = the volume of water entering the water heater during the ith draw of the first-hour rating test, gal (L). ρin,i = the density of water entering the water heater, evaluated at the average inlet water temperature measured during the ith draw of the first-hour rating test, (T*in,i), lb/gal (kg/L). or, if the mass of water entering the water heater is being measured, Where: M*in,i = the mass of water entering the water heater during the ith draw of the first-hour rating test, lb (kg).

For the case in which a draw is not in progress at one hour from the start of the test and a final draw is imposed at the elapsed time of one hour, the first-hour rating shall be calculated using,

where n and V*del,i are the same quantities as defined above, and V*del,n = the volume of water removed during the nth (final) draw of the first-hour rating test, gal (L). T*del,n−1 = the average water outlet temperature measured during the (n−1)th draw of the first-hour rating test, °F ( °C). T*del,n = the average water outlet temperature measured during the nth (final) draw of the first-hour rating test, °F ( °C). T*min,n−1 = the minimum water outlet temperature measured during the (n−1)th draw of the first-hour rating test, °F ( °C).

6.2 Maximum GPM (L/min) Rating Computation. Compute the maximum GPM (L/min) rating, Fmax, as:

Where: Vdel,10m = the volume of water removed during the maximum GPM (L/min) rating test, gal (L). Tdel = the average delivery temperature, °F ( °C). Tin = the average inlet temperature, °F ( °C). 10 = the number of minutes in the maximum GPM (L/min) rating test, min. or, if the mass of water removed is measured, Where: Mdel,10m = the mass of water removed during the maximum GPM (L/min) rating test, lb (kg). ρdel = the density of water removed, evaluated at the average delivery water temperature of the maximum GPM (L/min) rating test (Tdel), lb/gal (kg/L). or, if the volume of water entering the water heater is measured, Where: Vin,10m = the volume of water entering the water heater during the maximum GPM (L/min) rating test, gal (L). ρin = the density of water entering the water heater, evaluated at the average inlet water temperature of the maximum GPM (L/min) rating test (Tdel), lb/gal (kg/L). or, if the mass of water entering the water heater is measured, Where: Min,10m = the mass of water entering the water heater during the maximum GPM (L/min) rating test, lb (kg).

6.3 Computations for Water Heaters with a Rated Storage Volume Greater Than or Equal to 2 Gallons and Circulating Water Heaters.

6.3.1 Storage Tank Capacity. The storage tank capacity, Vst, is computed as follows:

Where: Vst = the storage capacity of the water heater, or, for circulating water heaters, the storage capacity of the separate storage tank used in accordance with section 4.10, gal (L). Wf = the weight of the storage tank when completely filled with water, lb (kg). Wt = the (tare) weight of the storage tank when completely empty, lb (kg). ρ = the density of water used to fill the tank measured at the temperature of the water, lb/gal (kg/L).

6.3.1.1 Effective Storage Volume. The effective storage tank capacity, Veff, is computed as follows:

For water heaters requiring a separate storage tank, Veff is the storage tank capacity of the separate storage tank as determined per section 6.3.1.

For all other water heaters:

Veff = kVVst

Where: Vst = as defined in section 6.3.1 and kV = a dimensionless volume scaling factor determined as follows:

If the first recovery period extends into the second draw of the 24-hour simulated use test, and

If T0 > (Tdel,1 + 5 °F) and T0 ≥ 130 °F,

(if T0 > (Tdel,1 + 2.8 °C) and T0 ≥ 54.4 °C),

If the first recovery period does not extend into the second draw of the 24-hour simulated use test, and

If Tmax,1 > (Tdel,2 + 5 °F) and Tmax,1 ≥ 130 °F,

(if Tmax,1 > (Tdel,2 + 2.8 °C) and Tmax,1 ≥ 54.4 °C),

Otherwise, kV = 1.

Where: T0= the mean tank temperature at the beginning of the 24-hour simulated-use test, °F( °C). Tdel,1= the average outlet water temperature during the first draw of the 24-hour simulated-use test, °F( °C). ρ(T0) = the density of the stored hot water evaluated at the mean tank temperature at the beginning of the 24-hour simulated-use test (T0), lb/gal (kg/L). Cp(T0) = the specific heat of the stored hot water, evaluated at T0, Btu/(lb· °F) (kJ/(kg· °C)). Tmax,1 = the maximum measured mean tank temperature after cut-out following the first draw of the 24-hour simulated-use test, °F( °C). Tdel,2= the average outlet water temperature during the second draw of the 24-hour simulated-use test, °F( °C). ρ(Tmax,1) = the density of the stored hot water evaluated at the maximum measured mean tank temperature after cut-out following the first draw of the 24-hour simulated-use test (Tmax,1), lb/gal (kg/L). Cp(Tmax,1) = the specific heat of the stored hot water, evaluated at Tmax,1, Btu/(lb· °F) (kJ/(kg· °C)). ρ(125 °F) = the density of the stored hot water at 125 °F, lb/gal (kg/L). Cp(125 °F) = the specific heat of the stored hot water at 125 °F, Btu/(lb· °F) (kJ/(kg· °C)). 125 °F (51.7 °C) = the nominal maximum mean tank temperature for a storage tank that does not utilize a mixing valve to achieve a 125 °F delivery temperature.

67.5 °F (19.7 °C) = the nominal average ambient air temperature.

6.3.2 Mass of Water Removed. Determine the mass of water removed during each draw of the 24-hour simulated-use test (Mdel,i) as:

If the mass of water removed is measured, use the measured value, or, if the volume of water removed is being measured,

Mdel,i = Vdel,i * Pdel,i

Where: Vdel,i = volume of water removed during the ith draw of the 24-hour simulated-use test, gal (L). ρdel,i = density of the water removed, evaluated at the average outlet water temperature measured during the ith draw of the 24-hour simulated-use test, (Tdel,i), lb/gal (kg/L). or, if the volume of water entering the water heater is measured,

Mdel,i = Vin,i * ρin,i

Where: Vin,i = volume of water entering the water heater during draw ith draw of the 24-hour simulated-use test, gal (L). ρin,i = density of the water entering the water heater, evaluated at the average inlet water temperature measured during the ith draw of the 24-hour simulated-use test, (Tin,i), lb/gal (kg/L). or, if the mass of water entering the water heater is measured,

Mdel,i = Min,i

Where: Min,i = mass of water entering the water heater during draw ith draw of the 24-hour simulated-use test, lb (kg).

6.3.3 Recovery Efficiency. The recovery efficiency for gas, oil, and heat pump water heaters with a rated storage volume greater than or equal to 2 gallons, ηr, is computed as:

Where: Vst = as defined in section 6.3.1 of this appendix. ρ1 = density of stored hot water evaluated at (Tmax,1 + T0)/2, lb/gal (kg/L). Cp1 = specific heat of the stored hot water, evaluated at (Tmax,1 + T0)/2, Btu/(lb· °F) (kJ/(kg· °C). Tmax,1 = maximum mean tank temperature recorded after the first recovery period as defined in section 5.4.2 of this appendix, °F ( °C). T0 = mean tank temperature recorded at the beginning of the 24-hour simulated-use test as determined in section 5.4.2 of this appendix, °F ( °C). Qr = the total energy used by the water heater during the first recovery period as defined in section 5.4.2 of this appendix, including auxiliary energy such as pilot lights, pumps, fans, etc., Btu (kJ). (Electrical auxiliary energy shall be converted to thermal energy using the following conversion: 1 kWh = 3412 Btu). Nr = number of draws from the start of the 24-hour simulated-use test to the end to the first recovery period as described in section 5.4.2. Mdel,i = mass of water removed as calculated in section 6.3.2 of this appendix during the ith draw of the first recovery period as described in section 5.4.2, lb (kg). Cpi = specific heat of the withdrawn water during the ith draw of the first recovery period as described in section 5.4.2, evaluated at (Tdel,i + Tin,i)/2, Btu/(lb· °F) (kJ/(kg· °C)). Tdel,i = average water outlet temperature measured during the ith draw of the first recovery period as described in section 5.4.2, °F ( °C). Tin,i = average water inlet temperature measured during the ith draw of the first recovery period as described in section 5.4.2, °F ( °C).

The recovery efficiency for electric water heaters with immersed heating elements, not including heat pump water heaters with immersed heating elements, is assumed to be 98 percent.

6.3.4 Hourly Standby Losses. The energy consumed as part of the standby loss test of the 24-hour simulated-use test, Qstby, is computed as:

Qstby = Qsu,f − Qsu,o Where: Qsu,0 = cumulative energy consumption, including all fossil fuel and electrical energy use, of the water heater from the start of the 24-hour simulated-use test to the start of the standby period as determined in section 5.4.2 of this appendix, Btu (kJ). Qsu,f = cumulative energy consumption, including all fossil fuel and electrical energy use, of the water heater from the start of the 24-hour simulated-use test to the end of the standby period as determined in section 5.4.2 of this appendix, Btu (kJ).

The hourly standby energy losses are computed as:

Where: Qhr = the hourly standby energy losses of the water heater, Btu/h (kJ/h). Vst = as defined in section 6.3.1 of this appendix. ρ = density of the stored hot water, evaluated at (Tsu,f + Tsu,0)/2, lb/gal (kg/L). Cp = specific heat of the stored water, evaluated at (Tsu,f + Tsu,0)/2, Btu/(lb· °F), (kJ/(kg·K)). Tsu,f = the mean tank temperature measured at the end of the standby period as determined in section 5.4.2 of this appendix, °F ( °C). Tsu,0 = the maximum mean tank temperature measured at the beginning of the standby period as determined in section 5.4.2 of this appendix, °F ( °C). ηr = as defined in section 6.3.3 of this appendix. τstby,1 = elapsed time between the start and end of the standby period as determined in section 5.4.2 of this appendix, h.

The standby heat loss coefficient for the tank is computed as:

Where: UA = standby heat loss coefficient of the storage tank, Btu/(h· °F), (kJ/(h· °C). Tt,stby,1 = overall average mean tank temperature between the start and end of the standby period as determined in section 5.4.2 of this appendix, °F ( °C). Ta,stby,1 = overall average ambient temperature between the start and end of the standby period as determined in section 5.4.2 of this appendix, °F ( °C). 6.3.5 Daily Water Heating Energy Consumption. The total energy used by the water heater during the 24-hour simulated-use test (Q) is as measured in section 5.4.2 of this appendix, or, Q = Qf + Qe = total energy used by the water heater during the 24-hour simulated-use test, including auxiliary energy such as pilot lights, pumps, fans, etc., Btu (kJ). Qf = total fossil fuel energy used by the water heater during the 24-hour simulated-use test, Btu (kJ). Qe = total electrical energy used during the 24-hour simulated-use test, Btu (kJ). (Electrical energy shall be converted to thermal energy using the following conversion: 1kWh = 3412 Btu.)

The daily water heating energy consumption, Qd, is computed as:

Where: Vst = as defined in section 6.3.1 of this appendix. ρ = density of the stored hot water, evaluated at (T24 + T0)/2, lb/gal (kg/L). Cp = specific heat of the stored water, evaluated at (T24 + T0)/2, Btu/(lb· °F), (kJ/(kg·K)). T24 = mean tank temperature at the end of the 24-hour simulated-use test as determined in section 5.4.2 of this appendix, °F ( °C). T0 = mean tank temperature recorded at the beginning of the 24-hour simulated-use test as determined in section 5.4.2 of this appendix, °F ( °C). ηr = as defined in section 6.3.3 of this appendix. 6.3.6 Adjusted Daily Water Heating Energy Consumption. The adjusted daily water heating energy consumption, Qda, takes into account that the ambient temperature may differ from the nominal value of 67.5 °F (19.7 °C) due to the allowable variation in surrounding ambient temperature of 65 °F (18.3 °C) to 70 °C (21.1 °C). The adjusted daily water heating energy consumption is computed as: Qda = Qd − (67.5 °C − Ta,stby,2) UA τstby,2 or, Qda = Qd − (19.7 °C − Ta,stby,2) UA τstby,2 Where: Qda = the adjusted daily water heating energy consumption, Btu (kJ). Qd = as defined in section 6.3.4 of this appendix. Ta,stby,2 = the average ambient temperature during the total standby portion, τstby,2, of the 24-hour simulated-use test, °F ( °C). UA = as defined in section 6.3.4 of this appendix. τstby,2 = the number of hours during the 24-hour simulated-use test when water is not being withdrawn from the water heater.

A modification is also needed to take into account that the temperature difference between the outlet water temperature and supply water temperature may not be equivalent to the nominal value of 67 °F (125 °F-58 °F) or 37.3 °C (51.7 °C-14.4 °C). The following equations adjust the experimental data to a nominal 67 °F (37.3 °C) temperature rise.

The energy used to heat water, Btu/day (kJ/day), may be computed as:

Where: N = total number of draws in the 24-hour simulated-use test. Mdel,i = the mass of water removed during the ith draw (i = 1 to N) as calculated in section 6.3.2 of this appendix, lb (kg). Cpi = the specific heat of the water withdrawn during the ith draw of the 24-hour simulated-use test, evaluated at (Tdel,i + Tin,i)/2, Btu/(lb· °F) (kJ/(kg· °C)). Tdel,i = the average water outlet temperature measured during the ith draw (i = 1 to N), °F ( °C). Tin,i = the average water inlet temperature measured during the ith draw (i = 1 to N), °F ( °C). ηr = as defined in section 6.3.3 of this appendix.

The energy required to heat the same quantity of water over a 67 °F (37.3 °C) temperature rise, Btu/day (kJ/day), is:

or, The difference between these two values is: QHWD = QHW,67. °F − QHW or, QHWD = QHW,37.3 °C − QHW

This difference (QHWD) must be added to the adjusted daily water heating energy consumption value. Thus, the daily energy consumption value, which takes into account that the ambient temperature may not be 67.5 °F (19.7 °C) and that the temperature rise across the storage tank may not be 67 °F (37.3 °C) is:

Qdm = Qda − QHWD

6.3.7 Estimated Mean Tank Temperature for Water Heaters with Rated Storage Volumes Greater Than or Equal to 2 Gallons. If testing is conducted in accordance with section 5.4.2.2 of this appendix, calculate the mean tank temperature immediately prior to the internal tank temperature determination draw using the following equation:

Where: Tst = the estimated average internal storage tank temperature, °F ( °C). Tp = the average of the inlet and the outlet water temperatures at the end of the period defined by τp, °F ( °C). vout,p = the average flow rate during the period, gal/min (L/min). Vst = the rated storage volume of the water heater, gal (L). τp = the number of minutes in the duration of the period, determined by the length of time taken for the outlet water temperature to be within 2 °F of the inlet water temperature for 15 consecutive seconds and including the 15-second stabilization period. Tin,p = the average of the inlet water temperatures during the period, °F ( °C). Tout,p = the average of the outlet water temperatures during the period, °F ( °C).

6.3.8 Uniform Energy Factor. The uniform energy factor, UEF, is computed as:

Where: N = total number of draws in the 24-hour simulated-use test. Qdm = the modified daily water heating energy consumption as computed in accordance with section 6.3.6 of this appendix, Btu (kJ). Mdel,i = the mass of water removed during the ith draw (i = 1 to N) as calculated in section 6.3.2 of this appendix, lb (kg). Cpi = the specific heat of the water withdrawn during the ith draw of the 24-hour simulated-use test, evaluated at (125 °F + 58 °F)/2 = 91.5 °F ((51.7 °C + 14.4 °C)/2 = 33 °C), Btu/(lb· °F) (kJ/(kg· °C)).

6.3.9 Annual Energy Consumption. The annual energy consumption for water heaters with rated storage volumes greater than or equal to 2 gallons is computed as:

Where: UEF = the uniform energy factor as computed in accordance with section 6.3.88 of this appendix. 365 = the number of days in a year. V = the volume of hot water drawn during the applicable draw pattern, gallons. = 10 for the very-small-usage draw pattern. = 38 for the low-usage draw pattern. = 55 for the medium-usage draw pattern. = 84 for high-usage draw pattern. ρ = 8.24 lb/gallon, the density of water at 125 °F. Cp = 1.00 Btu/(lb °F), the specific heat of water at 91.5 °F. 67 = the nominal temperature difference between inlet and outlet water

6.3.10 Annual Electrical Energy Consumption. The annual electrical energy consumption in kilowatt-hours for water heaters with rated storage volumes greater than or equal to 2 gallons, Eannual,e, is computed as:

Where: Eannual = the annual energy consumption as determined in accordance with section 6.3.99 of this appendix, Btu (kJ). Qe = the daily electrical energy consumption as defined in section 6.3.5 of this appendix, Btu (kJ). Q = total energy used by the water heater during the 24-hour simulated-use test in accordance with section 6.3.5 of this appendix, Btu (kJ). 3412 = conversion factor from Btu to kWh.

6.3.11 Annual Fossil Fuel Energy Consumption. The annual fossil fuel energy consumption for water heaters with rated storage volumes greater than or equal to 2 gallons, Eannual,f, is computed as:

Eannual,f = Eannual−(Eannual,e * 3412) Where: Eannual = the annual energy consumption as determined in accordance with section 6.3.9 of this appendix, Btu (kJ). Eannual,e = the annual electrical energy consumption as determined in accordance with section 6.3.10 of this appendix, kWh. 3412 = conversion factor from kWh to Btu.

6.4 Computations for Water Heaters with a Rated Storage Volume Less Than 2 Gallons.

6.4.1 Mass of Water Removed

Calculate the mass of water removed using the calculations in section 6.3.2 of this appendix.

6.4.2 Recovery Efficiency. The recovery efficiency, ηr, is computed as:

Where: M1 = mass of water removed during the first draw of the 24-hour simulated-use test, lb (kg). Cp1 = specific heat of the withdrawn water during the first draw of the 24-hour simulated-use test, evaluated at (Tdel,1 + Tin,1)/2, Btu/(lb· °F) (kJ/(kg· °C)). Tdel,1 = average water outlet temperature measured during the first draw of the 24-hour simulated-use test, °F ( °C). Tin,1 = average water inlet temperature measured during the first draw of the 24-hour simulated-use test, °F ( °C). Qr = the total energy used by the water heater during the first recovery period as defined in section 5.4.3 of this appendix, including auxiliary energy such as pilot lights, pumps, fans, etc., Btu (kJ). (Electrical auxiliary energy shall be converted to thermal energy using the following conversion: 1 kWh = 3412 Btu.)

6.4.3 Daily Water Heating Energy Consumption. The daily water heating energy consumption, Qd, is computed as:

Qd = Q Where: Q = Qf + Qe = the energy used by the water heater during the 24-hour simulated-use test. Qf = total fossil fuel energy used by the water heater during the 24-hour simulated-use test, Btu (kJ). Qe = total electrical energy used during the 24-hour simulated-use test, Btu (kJ). (Electrical auxiliary energy shall be converted to thermal energy using the following conversion: 1 kWh = 3412 Btu.)

A modification is needed to take into account that the temperature difference between the outlet water temperature and supply water temperature may not be equivalent to the nominal value of 67 °F (125 °F−58 °F) or 37.3 °C (51.7 °C−14.4 °C). The following equations adjust the experimental data to a nominal 67 °F (37.3 °C) temperature rise.

The energy used to heat water may be computed as:

Where: N = total number of draws in the 24-hour simulated-use test. Mdel,i = the mass of water removed during the ith draw (i = 1 to N) as calculated in section 6.4.1 of this appendix, lb (kg). Cpi = the specific heat of the water withdrawn during the ith draw of the 24-hour simulated-use test, evaluated at (Tdel,i + Tin,i)/2, Btu/(lb· °F) (kJ/(kg· °C)). Tdel,i = the average water outlet temperature measured during the ith draw (i = 1 to N), °F ( °C). Tin,i = the average water inlet temperature measured during the ith draw (i = 1 to N), °F ( °C). ηr = as defined in section 6.4.2 of this appendix.

The energy required to heat the same quantity of water over a 67 °F (37.3 °C) temperature rise is:

Where: N = total number of draws in the 24-hour simulated-use test. Mdel,i = the mass of water removed during the ith draw (i = 1 to N) as calculated in section 6.4.1 of this appendix, lb (kg). Cpi = the specific heat of the water withdrawn during the ith draw of the 24-hour simulated-use test, evaluated at (Tdel,i + Tin,i)/2, Btu/(lb· °F) (kJ/(kg· °C)). ηr = as defined in section 6.4.2 of this appendix.

The difference between these two values is:

QHWD = QHW,67 °FQHW or, QHWD = QHW,37.3 °CQHW

This difference (QHWD) must be added to the daily water heating energy consumption value. Thus, the daily energy consumption value, which takes into account that the temperature rise across the water heater may not be 67 °F (37.3 °C), is:

Qdm = Qda + QHWD

6.4.4 Uniform Energy Factor. The uniform energy factor, UEF, is computed as:

Where: N = total number of draws in the 24-hour simulated-use test. Qdm = the modified daily water heating energy consumption as computed in accordance with section 6.4.3 of this appendix, Btu (kJ). Mdel,i = the mass of water removed during the ith draw (i = 1 to N) as calculated in section 6.4.1 of this appendix, lb (kg). Cpi = the specific heat of the water withdrawn during the ith draw of the 24-hour simulated-use test, evaluated at (125 °F + 58 °F)/2 = 91.5 °F ((51.7 °C + 14.4 °C)/2 = 33.1 °C), Btu/(lb· °F) (kJ/(kg· °C)).

6.4.5 Annual Energy Consumption. The annual energy consumption for water heaters with rated storage volumes less than 2 gallons, Eannual, is computed as:

Where: UEF = the uniform energy factor as computed in accordance with section 6.4.4 of this appendix. 365 = the number of days in a year. V = the volume of hot water drawn during the applicable draw pattern, gallons. = 10 for the very-small-usage draw pattern. = 38 for the low-usage draw pattern. = 55 for the medium-usage draw pattern. = 84 for high-usage draw pattern. ρ = 8.24 lb/gallon, the density of water at 125 °F. Cp = 1.00 Btu/(lb °F), the specific heat of water at 91.5 °F. 67 = the nominal temperature difference between inlet and outlet water.

6.4.6 Annual Electrical Energy Consumption. The annual electrical energy consumption in kilowatt-hours for water heaters with rated storage volumes less than 2 gallons, Eannual,e, is computed as:

Where: Qe = the daily electrical energy consumption as defined in section 6.4.3 of this appendix, Btu (kJ). Eannual = the annual energy consumption as determined in accordance with section 6.4.5 of this appendix, Btu (kJ). Q = total energy used by the water heater during the 24-hour simulated-use test in accordance with section 6.4.3 of this appendix, Btu (kJ). Qdm = the modified daily water heating energy consumption as computed in accordance with section 6.4.3 of this appendix, Btu (kJ). 3412 = conversion factor from Btu to kWh.

6.4.7 Annual Fossil Fuel Energy Consumption. The annual fossil fuel energy consumption for water heaters with rated storage volumes less than 2 gallons, Eannual,f, is computed as:

Where: Eannual = the annual energy consumption as defined in section 6.4.5 of this appendix, Btu (kJ). Eannual,e = the annual electrical energy consumption as defined in section 6.4.6 of this appendix, kWh. 3412 = conversion factor from kWh to Btu.

6.5 Energy Efficiency at Optional Test Conditions. If testing is conducted at optional test conditions in accordance with section 5.6 of this appendix, calculate the energy efficiency at the test condition, EX, using the formulas in sections 6.3 or 6.4 of this appendix (as applicable), except substituting the applicable ambient temperature and supply water temperature used for testing (as specified in section 2.8 of this appendix) for the nominal ambient temperature and supply water temperature conditions used in the equations for determining UEF (i.e., 67.5 °F and 58 °F).

7. Test Set-Up Diagrams [88 span 40473, June 21, 2023, as amended at 89 span 37943, May 6, 2204]

Appendix F - Appendix F to Subpart B of Part 430—Uniform Test Method for Measuring the Energy Consumption of Room Air Conditioners

Note:

On or after September 27, 2021, any representations made with respect to the energy use or efficiency of room air conditioners must be made in accordance with the results of testing pursuant to this appendix.

Prior to September 27, 2021, manufacturers must either test room air conditioners in accordance with this appendix, or the previous version of this appendix as it appeared in the Code of Federal Regulations on January 1, 2020. DOE notes that, because representations made on or after September 27, 2021 must be made in accordance with this appendix, manufacturers may wish to begin using this test procedure immediately.

0. Incorporation by Reference

DOE incorporated by reference the entire standard for AHAM RAC-1, ANSI/ASHRAE 16, ANSI/ASHRAE 41.1, ASHRAE 41.2-1987 (RA 1992), ASHRAE 41.3-2014, ASHRAE 41.6-2014, ASHRAE 41.11-2014 and IEC 62301 in § 430.3. However, only enumerated provisions of AHAM RAC-1 and ANSI/ASHRAE 16 apply to this appendix, as follows:

(1) ANSI/AHAM RAC-1:

(i) Section 4—Testing Conditions, Section 4.1—General

(ii) Section 5—Standard Measurement Test, Section 5.2—Standard Test Conditions: 5.2.1.1

(iii) Section 6—Tests and Measurements, Section 6.1—Cooling capacity

(iv) Section 6— Tests and Measurements, Section 6.2—Electrical Input

(2) ANSI/ASHRAE 16:

(i) Section 3—Definitions

(ii) Section 5—Instruments

(iii) Section 6—Apparatus, Section 6.1—Calorimeters, Sections 6.1.1-6.1.1., 6.1.1.3a, 6.1.1.4-6.1.4, including Table 1

(iv) Section 7—Methods of Testing, Section 7.1—Standard Test Methods, Section 7.1a, 7.1.1a

(v) Section 8—Test Procedures, Section 8.1—General

(vi) Section 8—Test Procedures, Section 8.2—Test Room Requirements

(viii) Section 8—Test Procedures, Section 8.3—Air Conditioner Break-In

(ix) Section 8—Test Procedures, Section 8.4—Air Conditioner Installation

(x) Section 8 —Test Procedures, Section 8.5—Cooling Capacity Test

(xi) Section 9—Data To Be Recorded, Section 9.1

(xii) Section 10—Measurement Uncertainty

(xiii) Normative Appendix A Cooling Capacity Calculations—Calorimeter Test Indoor and Calorimeter Test Outdoor

If there is any conflict between any industry standard(s) and this appendix, follow the language of the test procedure in this appendix, disregarding the conflicting industry standard language. Scope

This appendix contains the test requirements to measure the energy performance of a room air conditioner.

2. Definitions

2.1 “Active mode” means a mode in which the room air conditioner is connected to a mains power source, has been activated and is performing any of the following functions: Cooling or heating the conditioned space, or circulating air through activation of its fan or blower, with or without energizing active air-cleaning components or devices such as ultra-violet (UV) radiation, electrostatic filters, ozone generators, or other air-cleaning devices.

2.2 “ANSI/AHAM RAC-1” means the test standard published jointly by the American National Standards Institute and the Association of Home Appliance Manufacturers, titled “Energy Measurement Test Procedure for Room Air Conditioners,” Standard RAC-1-2020 (incorporated by reference; see § 430.3).

2.3 “ANSI/ASHRAE 16” means the test standard published jointly by the American National Standards Institute and the American Society of Heating, Refrigerating, and Air-Conditioning Engineers titled “Method of Testing for Rating Room Air Conditioners and Packaged Terminal Air Conditioners,” Standard 16-2016 (incorporated by reference; see § 430.3).

2.4 “ANSI/ASHRAE 41.1” means the test standard published jointly by the American National Standards Institute and the American Society of Heating, Refrigerating, and Air-Conditioning Engineers titled “Standard Method for Temperature Measurement,” Standard 41.1-2013 (incorporated by reference; see § 430.3).

2.5 “ASHRAE 41.2-1987 (RA 1992)” means the test standard published jointly by the American National Standards Institute and the American Society of Heating, Refrigerating, and Air-Conditioning Engineers titled “Standard Methods for Laboratory Airflow Measurement,” Standard 41.2-1987 (RA 1992) (incorporated by reference; see § 430.3).

2.6 “ASHRAE 41.3-2014” means the test standard published jointly by the American National Standards Institute and the American Society of Heating, Refrigerating, and Air-Conditioning Engineers titled “Standard Methods for Pressure Measurement,” Standard 41.3-2014 (incorporated by reference; see § 430.3).

2.7 “ASHRAE 41.6-2014” means the test standard published jointly by the American National Standards Institute and the American Society of Heating, Refrigerating, and Air-Conditioning Engineers titled “Standard Method for Humidity Measurement,” Standard 41.6-2014 (incorporated by reference; see § 430.3).

2.8 “ASHRAE 41.11-2014” means the test standard published jointly by the American National Standards Institute and the American Society of Heating, Refrigerating, and Air-Conditioning Engineers titled “Standard Methods for Power Measurement,” Standard 41.11-2014 (incorporated by reference; see § 430.3).

2.9 “Combined energy efficiency ratio” means the energy efficiency of a room air conditioner in British thermal units per watt-hour (Btu/Wh) and determined in section 5.2.2 of this appendix for single-speed room air conditioners and section 5.3.12 of this appendix for variable-speed room air conditioners.

2.10 “Cooling capacity” means the amount of cooling, in British thermal units per hour (Btu/h), provided to a conditioned space, measured under the specified conditions and determined in section 4.1 of this appendix.

2.11 “Cooling mode” means an active mode in which a room air conditioner has activated the main cooling function according to the thermostat or temperature sensor signal or switch (including remote control).

2.12 “Full compressor speed (full)” means the compressor speed at which the unit operates at full load test conditions, when using user settings with a unit thermostat setpoint of 75 °F to achieve maximum cooling capacity, according to the instructions in ANSI/ASHRAE Standard 16-2016.

2.13 “IEC 62301” means the test standard published by the International Electrotechnical Commission, titled “Household electrical appliances—Measurement of standby power,” Publication 62301 (Edition 2.0 2011-01), (incorporated by reference; see § 430.3).

2.14 “Inactive mode” means a standby mode that facilitates the activation of active mode by remote switch (including remote control) or internal sensor or which provides continuous status display.

2.15 “Intermediate compressor speed (intermediate)” means the compressor speed higher than the low compressor speed at which the measured capacity is higher than the capacity at low compressor speed by one third of the difference between Capacity4, the measured cooling capacity at test condition 4 in Table 1 of this appendix, and Capacity1, the measured cooling capacity with the full compressor speed at test condition 1 in Table 1 of this appendix, with a tolerance of plus 5 percent (designs with non-discrete speed stages) or the next highest inverter frequency step (designs with discrete speed steps), achieved by following the instructions certified by the manufacturer.

2.16 “Low compressor speed (low)” means the compressor speed at which the unit operates at low load test conditions, achieved by following the instructions certified by the manufacturer, such that Capacity4, the measured cooling capacity at test condition 4 in Table 1 of this appendix, is no less than 47 percent and no greater than 57 percent of Capacity1, the measured cooling capacity with the full compressor speed at test condition 1 in Table 1 of this appendix.

2.17 “Off mode” means a mode in which a room air conditioner is connected to a mains power source and is not providing any active or standby mode function and where the mode may persist for an indefinite time, including an indicator that only shows the user that the product is in the off position.

2.18 “Single-speed room air conditioner” means a type of room air conditioner that cannot automatically adjust the compressor speed based on detected conditions.

2.19 “Standby mode” means any product mode where the unit is connected to a mains power source and offers one or more of the following user-oriented or protective functions which may persist for an indefinite time:

(a) To facilitate the activation of other modes (including activation or deactivation of active mode) by remote switch (including remote control), internal sensor, or timer. A timer is a continuous clock function (which may or may not be associated with a display) that provides regular scheduled tasks (e.g., switching) and that operates on a continuous basis.

(b) Continuous functions, including information or status displays (including clocks) or sensor-based functions.

2.20 “Theoretical comparable single-speed room air conditioner” means a theoretical single-speed room air conditioner with the same cooling capacity and electrical power input as the variable-speed room air conditioner under test, with no cycling losses considered, at test condition 1 in Table 1 of this appendix.

2.21 “Variable-speed compressor” means a compressor that can vary its rotational speed in non-discrete stages or discrete steps from low to full.

2.22 “Variable-speed room air conditioner” means a type of room air conditioner that can automatically adjust compressor speed based on detected conditions.

3. Test Methods and General Instructions

3.1 Cooling mode. The test method for testing room air conditioners in cooling mode (“cooling mode test”) consists of applying the methods and conditions in AHAM RAC-1 Section 4, Paragraph 4.1 and for single-speed room air conditioners, Section 5, Paragraph 5.2.1.1, and for variable-speed room air conditioners, Section 5, Paragraph 5.2.1.2, except in accordance with ANSI/ASHRAE 16, including the references to ANSI/ASHRAE 41.1, ANSI/ASHRAE 41.2-1987 (RA 1992), ANSI/ASHRAE 41.3-2014, ANSI/ASHRAE 41.6-2014, and ANSI/ASHRAE 41.11-2014, all referenced therein, as defined in sections 2.3 through 2.8 of this appendix. Use the cooling capacity simultaneous indoor calorimeter and outdoor calorimeter test method in Section 7.1.a and Sections 8.1 through 8.5 of ANSI/ASHRAE 16, except as otherwise specified in this appendix. If a unit can operate on multiple operating voltages as distributed in commerce by the manufacturer, test it and rate the corresponding basic models at all nameplate operating voltages. For a variable-speed room air conditioner, test the unit following the cooling mode test a total of four times: One test at each of the test conditions listed in Table 1 of this appendix, consistent with section 4.1 of this appendix.

3.1.1 Through-the-wall installation. Install a non-louvered room air conditioner inside a compatible wall sleeve with the provided or manufacturer-required rear grille, and with only the included trim frame and other manufacturer-provided installation materials, per manufacturer instructions provided to consumers.

3.1.2 Power measurement accuracy. All instruments used for measuring electrical inputs to the test unit, reconditioning equipment, and any other equipment that operates within the calorimeter walls must be accurate to ±0.5 percent of the quantity measured.

3.1.3 Electrical supply. For cooling mode testing, test at each nameplate operating voltage, and maintain the input standard voltage within ±1 percent. Test at the rated frequency, maintained within ±1 percent.

3.1.4 Control settings. If the room air conditioner has network capabilities, all network features must be disabled throughout testing.

3.1.5 Measurement resolution. Record measurements at the resolution of the test instrumentation.

3.1.6 Temperature tolerances. Maintain each of the measured chamber dry-bulb and wet-bulb temperatures within a range of 1.0 °F.

3.2 Standby and off modes.

3.2.1 Install the room air conditioner in accordance with Section 5, Paragraph 5.2 of IEC 62301 and maintain the indoor test conditions (and outdoor test conditions where applicable) as required by Section 4, Paragraph 4.2 of IEC 62301. If testing is not conducted in a facility used for testing cooling mode performance, the test facility must comply with Section 4, Paragraph 4.2 of IEC 62301.

3.2.2 Electrical supply. For standby mode and off mode testing, maintain the electrical supply voltage and frequency according to the requirements in Section 4, Paragraph 4.3.1 of IEC 62301.

3.2.3 Supply voltage waveform. For the standby mode and off mode testing, maintain the electrical supply voltage waveform indicated in Section 4, Paragraph 4.3.2 of IEC 62301.

3.2.4 Wattmeter. The wattmeter used to measure standby mode and off mode power consumption must meet the resolution and accuracy requirements in Section 4, Paragraph 4.4 of IEC 62301.

3.2.5 Air ventilation damper. If the unit is equipped with an outdoor air ventilation damper, close this damper during standby mode and off mode testing.

4. Test Conditions and Measurements

4.1 Cooling mode.

4.1.1 Temperature conditions. Establish the test conditions described in Sections 4 and 5 of AHAM RAC-1 and in accordance with ANSI/ASHRAE 16, including the references to ANSI/ASHRAE 41.1 and ANSI/ASHRAE 41.6-2014, for cooling mode testing, with the following exceptions for variable-speed room air conditioners: Conduct the set of four cooling mode tests with the test conditions presented in Table 1 of this appendix. For test condition 1 and test condition 2, achieve the full compressor speed with user settings, as defined in section 2.12 of this appendix. For test condition 3 and test condition 4, set the required compressor speed in accordance with instructions the manufacturer provided to DOE.

Table 1—Indoor and Outdoor Inlet Air Test Conditions—Variable-Speed Room Air Conditioners

Test
condition
Evaporator inlet
(indoor) air, °F
Condenser inlet
(outdoor) air, °F
Compressor speed Dry bulb Wet bulb Dry bulb Wet bulb Test Condition 180679575Full. Test Condition 280679272.5Full. Test Condition 380678769Intermediate. Test Condition 480678265Low.

4.1.2 Cooling capacity and power measurements. For single-speed units, measure the cooling mode cooling capacity (expressed in Btu/h), Capacity, and electrical power input (expressed in watts), Pcool, in accordance with Section 6, Paragraphs 6.1 and 6.2 of AHAM RAC-1, respectively, and in accordance with ANSI/ASHRAE 16, including the references to ANSI/ASHRAE 41.2-1987 (RA 1992) and ANSI/ASHRAE 41.11-2014. For variable-speed room air conditioners, measure the condition-specific cooling capacity (expressed in Btu/h), Capacitytc, and electrical power input (expressed in watts), Ptc, for each of the four cooling mode rating test conditions (tc), as required in Section 6, Paragraphs 6.1 and 6.2, respectively, of AHAM RAC-1, respectively, and in accordance with ANSI/ASHRAE 16, including the references to ANSI/ASHRAE 41.2-1987 (RA 1992) and ANSI/ASHRAE 41.11-2014.

4.2 Standby and off modes. Establish the testing conditions set forth in section 3.2 of this appendix, ensuring the unit does not enter any active mode during the test. For a unit that drops from a higher power state to a lower power state as discussed in Section 5, Paragraph 5.1, Note 1 of IEC 62301, allow sufficient time for the room air conditioner to reach the lower power state before proceeding with the test measurement. Use the sampling method test procedure specified in Section 5, Paragraph 5.3.2 of IEC 62301 for testing all standby and off modes, with the following modifications: Allow the product to stabilize for 5 to 10 minutes and use an energy use measurement period of 5 minutes.

4.2.1 If the unit has an inactive mode, as defined in section 2.14 of this appendix, measure and record the average inactive mode power, Pia, in watts.

4.2.2 If the unit has an off mode, as defined in section 2.17 of this appendix, measure and record the average off mode power, Pom, in watts.

5. Calculations

5.1 Annual energy consumption in inactive mode and off mode. Calculate the annual energy consumption in inactive mode and off mode, AECia/om, expressed in kilowatt-hours per year (kWh/year).

AECia/om = (Pia × tia + Pom × tom) Where: AECia/om = annual energy consumption in inactive mode and off mode, in kWh/year. Pia = average power in inactive mode, in watts, determined in section 4.2 of this appendix. Pom = average power in off mode, in watts, determined in section 4.2 of this appendix. tia = annual operating hours in inactive mode and multiplied by a 0.001 kWh/Wh conversion factor from watt-hours to kilowatt-hours. This value is 5.115 kWh/W if the unit has inactive mode and no off mode, 2.5575 kWh/W if the unit has both inactive and off mode, and 0 kWh/W if the unit does not have inactive mode. tom = annual operating hours in off mode and multiplied by a 0.001 kWh/Wh conversion factor from watt-hours to kilowatt-hours. This value is 5.115 kWh/W if the unit has off mode and no inactive mode, 2.5575 kWh/W if the unit has both inactive and off mode, and 0 kWh/W if the unit does not have off mode.

5.2 Combined energy efficiency ratio for single-speed room air conditioners. Calculate the combined energy efficiency ratio for single-speed room air conditioners as follows:

5.2.1 Single-speed room air conditioner annual energy consumption in cooling mode. Calculate the annual energy consumption in cooling mode for a single-speed room air conditioner, AECcool, expressed in kWh/year.

AECcool = 0.75 × Pcool Where: AECcool = single-speed room air conditioner annual energy consumption in cooling mode, in kWh/year. Pcool = single-speed room air conditioner average power in cooling mode, in watts, determined in section 4.1.2 of this appendix. 0.75 is 750 annual operating hours in cooling mode multiplied by a 0.001 kWh/Wh conversion factor from watt-hours to kilowatt-hours.

5.2.2 Single-speed room air conditioner combined energy efficiency ratio. Calculate the combined energy efficiency ratio, CEER, expressed in Btu/Wh, as follows:

Where: CEER = combined energy efficiency ratio, in Btu/Wh. Capacity = single-speed room air conditioner cooling capacity, in Btu/h, determined in section 4.1.2 of this appendix. AECcool = single-speed room air conditioner annual energy consumption in cooling mode, in kWh/year, calculated in section 5.2.1 of this appendix. AECia/om = annual energy consumption in inactive mode and off mode, in kWh/year, determined in section 5.1 of this appendix. 0.75 as defined in section 5.2.1 of this appendix.

5.3 Combined energy efficiency ratio for variable-speed room air conditioners. Calculate the combined energy efficiency ratio for variable-speed room air conditioners as follows:

5.3.1 Weighted electrical power input. Calculate the weighted electrical power input in cooling mode, Pwt, expressed in watts, as follows:

Pwt = Σtc Ptc × Wtc Where: Pwt = weighted electrical power input, in watts, in cooling mode. Ptc = electrical power input, in watts, in cooling mode for each test condition in Table 1 of this appendix. Wtc = weighting factors for each cooling mode test condition: 0.08 for test condition 1, 0.20 for test condition 2, 0.33 for test condition 3, and 0.39 for test condition 4. tc represents the cooling mode test condition: “1” for test condition 1 (95 °F condenser inlet dry-bulb temperature), “2” for test condition 2 (92 °F), “3” for test condition 3 (87 °F), and “4” for test condition 4 (82 °F).

5.3.2 Theoretical comparable single-speed room air conditioner. Calculate the cooling capacity, expressed in Btu/h, and the electrical power input, expressed in watts, for a theoretical comparable single-speed room air conditioner at all cooling mode test conditions.

Capacityss__tc = Capacity1 × (1 + (Mc × (95−Ttc))) Pss__tc = P1 × (1−(Mp × (95−Ttc))) Where: Capacityss__tc = theoretical comparable single-speed room air conditioner cooling capacity, in Btu/h, calculated for each of the cooling mode test conditions in Table 1 of this appendix. Capacity1 = variable-speed room air conditioner unit's cooling capacity, in Btu/h, determined in section 4.1.2 of this appendix for test condition 1 in Table 1 of this appendix. Pss__tc = theoretical comparable single-speed room air conditioner electrical power input, in watts, calculated for each of the cooling mode test conditions in Table 1 of this appendix. P1 = variable-speed room air conditioner unit's electrical power input, in watts, determined in section 4.1.2 of this appendix for test condition 1 in Table 1 of this appendix. Mc = adjustment factor to determine the increased capacity at lower outdoor test conditions, 0.0099 per °F. Mp = adjustment factor to determine the reduced electrical power input at lower outdoor test conditions, 0.0076 per °F. 95 is the condenser inlet dry-bulb temperature for test condition 1 in Table 1 of this appendix, 95 °F. Ttc = condenser inlet dry-bulb temperature for each of the test conditions in Table 1 of this appendix (in °F). tc as explained in section 5.3.1 of this appendix.

5.3.3 Variable-speed room air conditioner unit's annual energy consumption for cooling mode at each cooling mode test condition. Calculate the annual energy consumption for cooling mode under each test condition, AECtc, expressed in kilowatt-hours per year (kWh/year), as follows:

AECtc = 0.75 × Ptc Where: AECtc = variable-speed room air conditioner unit's annual energy consumption, in kWh/year, in cooling mode for each test condition in Table 1 of this appendix. Ptc = as defined in section 5.3.1 of this appendix. 0.75 as defined in section 5.2.1 of this appendix. tc as explained in section 5.3.1 of this appendix.

5.3.4 Variable-speed room air conditioner weighted annual energy consumption. Calculate the weighted annual energy consumption in cooling mode for a variable-speed room air conditioner, AECwt, expressed in kWh/year.

AECwt = Σtc AECtc × Wtc Where: AECwt = weighted annual energy consumption in cooling mode for a variable-speed room air conditioner, expressed in kWh/year. AECtc = variable-speed room air conditioner unit's annual energy consumption, in kWh/year, in cooling mode for each test condition in Table 1 of this appendix, determined in section 5.3.3 of this appendix. Wtc = weighting factors for each cooling mode test condition: 0.08 for test condition 1, 0.20 for test condition 2, 0.33 for test condition 3, and 0.39 for test condition 4. tc as explained in section 5.3.1 of this appendix.

5.3.5 Theoretical comparable single-speed room air conditioner annual energy consumption in cooling mode at each cooling mode test condition. Calculate the annual energy consumption in cooling mode for a theoretical comparable single-speed room air conditioner for cooling mode under each test condition, AECss__tc, expressed in kWh/year.

AECss__tc = 0.75 × Pss__tc Where: AECss__tc = theoretical comparable single-speed room air conditioner annual energy consumption, in kWh/year, in cooling mode for each test condition in Table 1 of this appendix. Pss__tc = theoretical comparable single-speed room air conditioner electrical power input, in watts, in cooling mode for each test condition in Table 1 of this appendix, determined in section 5.3.2 of this appendix. 0.75 as defined in section 5.2.1 of this appendix. tc as explained in section 5.3.1 of this appendix.

5.3.6 Variable-speed room air conditioner combined energy efficiency ratio at each cooling mode test condition. Calculate the variable-speed room air conditioner unit's combined energy efficiency ratio, CEERtc, for each test condition, expressed in Btu/Wh.

Where: CEERtc = variable-speed room air conditioner unit's combined energy efficiency ratio, in Btu/Wh, for each test condition in Table 1 of this appendix. Capacitytc = variable-speed room air conditioner unit's cooling capacity, in Btu/h, for each test condition in Table 1 of this appendix, determined in section 4.1.2 of this appendix. AECtc = variable-speed room air conditioner unit's annual energy consumption, in kWh/year, in cooling mode for each test condition in Table 1 of this appendix, determined in section 5.3.3 of this appendix. AECia/om = annual energy consumption in inactive mode and off mode, in kWh/year, determined in section 5.1 of this appendix. 0.75 as defined in section 5.2.1 of this appendix. tc as explained in section 5.3.1 of this appendix.

5.3.7 Theoretical comparable single-speed room air conditioner combined energy efficiency ratio. Calculate the combined energy efficiency ratio for a theoretical comparable single-speed room air conditioner, CEERss__tc, for each test condition, expressed in Btu/Wh.

Where: CEERss__tc = theoretical comparable single-speed room air conditioner combined energy efficiency ratio, in Btu/Wh, for each test condition in Table 1 of this appendix. Capacityss__tc = theoretical comparable single-speed room air conditioner cooling capacity, in Btu/h, for each test condition in Table 1 of this appendix, determined in section 5.3.2 of this appendix. AECss__tc = theoretical comparable single-speed room air conditioner annual energy consumption, in kWh/year, in cooling mode for each test condition in Table 1 of this appendix, determined in section 5.3.5 of this appendix. AECia/om = annual energy consumption in inactive mode and off mode, in kWh/year, determined in section 5.1 of this appendix. 0.75 as defined in section 5.2.1 of this appendix. tc as explained in section 5.3.1 of this appendix.

5.3.8 Theoretical comparable single-speed room air conditioner adjusted combined energy efficiency ratio. Calculate the adjusted combined energy efficiency ratio, for a theoretical comparable single-speed room air conditioner, CEERss__tc__adj, with cycling losses considered, for each test condition, expressed in Btu/Wh.

CEERss__tc__adj = CEERss__tc × CLFtc Where: CEERss__tc__adj = theoretical comparable single-speed room air conditioner adjusted combined energy efficiency ratio, in Btu/Wh, for each test condition in Table 1 of this appendix. CEERss__tc = theoretical comparable single-speed room air conditioner combined energy efficiency ratio, in Btu/Wh, for each test condition in Table 1 of this appendix, determined in section 5.3.7 of this appendix. CLFtc = cycling loss factor for each test condition; 1 for test condition 1, 0.956 for test condition 2, 0.883 for test condition 3, and 0.810 for test condition 4. tc as explained in section 5.3.1 of this appendix.

5.3.9 Weighted combined energy efficiency ratio. Calculate the weighted combined energy efficiency ratio for the variable-speed room air conditioner unit, CEERwt, and theoretical comparable single-speed room air conditioner, CEERss__wt, expressed in Btu/Wh.

CEERwt = Σtc CEERtc × Wtc CEERss__wt = Σtc CEERss__tc__adj × Wtc Where: CEERwt = variable-speed room air conditioner unit's weighted combined energy efficiency ratio, in Btu/Wh. CEERss__wt = theoretical comparable single-speed room air conditioner weighted combined energy efficiency ratio, in Btu/Wh. CEERtc = variable-speed room air conditioner unit's combined energy efficiency ratio, in Btu/Wh, at each test condition in Table 1 of this appendix, determined in section 5.3.6 of this appendix. CEERss__tc__adj = theoretical comparable single-speed room air conditioner adjusted combined energy efficiency ratio, in Btu/Wh, at each test condition in Table 1 of this appendix, determined in section 5.3.8 of this appendix. Wtc as defined in section 5.3.4 of this appendix. tc as explained in section 5.3.1 of this appendix.

5.3.10 Variable-speed room air conditioner performance adjustment factor. Calculate the variable-speed room air conditioner unit's performance adjustment factor, Fp.

Where: Fp = variable-speed room air conditioner unit's performance adjustment factor. CEERwt = variable-speed room air conditioner unit's weighted combined energy efficiency ratio, in Btu/Wh, determined in section 5.3.9 of this appendix. CEERss__wt = theoretical comparable single-speed room air conditioner weighted combined energy efficiency ratio, in Btu/Wh, determined in section 5.3.9 of this appendix.

5.3.11 Variable-speed room air conditioner combined energy efficiency ratio. Calculate the combined energy efficiency ratio, CEER, expressed in Btu/Wh, for variable-speed air conditioners.

CEER = CEER1 × (1 + Fp) Where: CEER = combined energy efficiency ratio, in Btu/Wh. CEER1 = variable-speed room air conditioner combined energy efficiency ratio for test condition 1 in Table 1 of this appendix, in Btu/Wh, determined in section 5.3.6 of this appendix. Fp = variable-speed room air conditioner performance adjustment factor, determined in section 5.3.10 of this appendix. [86 FR 16476, Mar. 29, 2021, as amended at 86 FR 24484, May 7, 2021; 88 FR 59791, Aug. 30, 2023]

Appendix G - Appendix G to Subpart B of Part 430—Uniform Test Method for Measuring the Energy Consumption of Unvented Home Heating Equipment

1. Testing conditions.

1.1 Installation.

1.1.1 Electric heater. Install heater according to manufacturer's instructions. Heaters shall be connected to an electrical supply circuit of nameplate voltage with a wattmeter installed in the circuit. The wattmeter shall have a maximum error not greater than one percent.

1.1.2 Unvented gas heater. Install heater according to manufacturer's instructions. Heaters shall be connected to a gas supply line with a gas displacement meter installed between the supply line and the heater according to manufacturer's specifications. The gas displacement meter shall have a maximum error not greater than one percent. Gas heaters with electrical auxiliaries shall be connected to an electrical supply circuit of nameplate voltage with a wattmeter installed in the circuit. The wattmeter shall have a maximum error not greater than one percent.

1.1.3 Unvented oil heater. Install heater according to manufacturer's instructions. Oil heaters with electric auxiliaries shall be connected to an electrical supply circuit of nameplate voltage with a wattmeter installed in the circuit. The wattmeter shall have a maximum error not greater than one percent.

1.2 Temperature regulating controls. All temperature regulating controls shall be shorted out of the circuit or adjusted so that they will not operate during the test period.

1.3 Fan controls. All fan controls shall be set at the highest fan speed setting.

1.4 Energy supply.

1.4.1 Electrical supply. Supply power to the heater within one percent of the nameplate voltage.

1.4.2 Natural gas supply. For an unvented gas heater utilizing natural gas, maintain the gas supply to the heater with a normal inlet test pressure immediately ahead of all controls at 7 to 10 inches of water column. The regulator outlet pressure at normal supply test pressure shall be approximately that recommended by the manufacturer. The natural gas supplied should have a higher heating value within ±5 percent of 1,025 Btu's per standard cubic foot. Determine the higher heating value, in Btu's per standard cubic foot, for the natural gas to be used in the test, with an error no greater than one percent. Alternatively, the test can be conducted using “bottled” natural gas of a higher heating value within ±5 percent of 1,025 Btu's per standard cubic foot as long as the actual higher heating value of the bottled natural gas has been determined with an error no greater than one percent as certified by the supplier.

1.4.3 Propane gas supply. For an unvented gas heater utilizing propane, maintain the gas supply to the heater with a normal inlet test pressure immediately ahead of all controls at 11 to 13 inches of water column. The regulator outlet pressure at normal supply test pressure shall be that recommended by the manufacturer. The propane supplied should have a higher heating value of within±5 percent of 2,500 Btu's per standard cubic foot. Determine the higher heating value in Btu's per standard foot, for the propane to be used in the test, with an error no greater than one percent. Alternatively, the test can be conducted using “bottled” propane of a higher heating value within ±5 percent of 2,500 Btu's per standard cubic foot as long as the actual higher heating value of the bottled propane has been determined with an error no greater than one percent as certified by the supplier.

1.4.4 Oil supply. For an unvented oil heater utilizing kerosene, determine the higher heating value in Btu's per gallon with an error no greater than one percent. Alternatively, the test can be conducted using a tested fuel of a higher heating value within ±5 percent of 137,400 Btu's per gallon as long as the actual higher heating value of the tested fuel has been determined with an error no greater than one percent as certified by the supplier.

1.5 Energy flow instrumentation. Install one or more energy flow instruments which measure, as appropriate and with an error no greater than one percent, the quantity of electrical energy, natural gas, propane gas, or oil supplied to the heater.

2. Testing and measurements.

2.1 Electric power measurement. Establish the test conditions set forth in section 1 of this appendix. Allow an electric heater to warm up for at least five minutes before recording the maximum electric power measurement from the wattmeter. Record the maximum electric power (PE) expressed in kilowatts.

Allow the auxiliary electrical system of a forced air unvented gas, propane, or oil heater to operate for at least five minutes before recording the maximum auxiliary electric power measurement from the wattmeter. Record the maximum auxiliary electric power (PA) expressed in kilowatts.

2.2 Natural gas, propane, and oil measurement. Establish the test conditions as set forth in section 1 of this appendix. A natural gas, propane, or oil heater shall be operated for one hour. Using either the nameplate rating or the energy flow instrumentation set forth in section 1.5 of this appendix and the fuel supply rating set forth in sections 1.4.2, 1.4.3, or 1.4.4 of this appendix, as appropriate, determine the maximum fuel input (PF) of the heater under test in Btu's per hour. The energy flow instrumentation shall measure the maximum fuel input with an error no greater than one percent.

2.3 Pilot light measurement. Except as provided in section 2.3.1 of this appendix, measure the energy input rate to the pilot light (Qp), with an error no greater than 3 percent, for unvented heaters so equipped.

2.3.1 The measurement of Qp is not required for unvented heaters where the pilot light is designed to be turned off by the user when the heater is not in use (i.e., for units where turning the control to the OFF position will shut off the gas supply to the burner(s) and the pilot light). This provision applies only if an instruction to turn off the unit is provided on the heater near the gas control value (e.g., by label) by the manufacturer.

2.4 Electrical standby mode power measurement. Except as provided in section 2.4.1 of this appendix, for all electric heaters and unvented heaters with electrical auxiliaries, measure the standby power (PW,SB) in accordance with the procedures in IEC 62301 Second Edition (incorporated by reference; see § 430.3), with all electrical auxiliaries not activated. Voltage shall be as specified in section 1.4.1 Electrical supply of this appendix. The recorded standby power (PW,SB) shall be rounded to the second decimal place, and for loads greater than or equal to 10W, at least three significant figures shall be reported.

2.4.1 The measurement of PW,SB is not required for heaters designed to be turned off by the user when the heater is not in use (i.e., for units where turning the control to the OFF position will shut off the electrical supply to the heater). This provision applies only if an instruction to turn off the unit is provided on the heater (e.g., by label) by the manufacturer.

3. Calculations.

3.1 Annual energy consumption for primary electric heaters. For primary electric heaters, calculate the annual energy consumption (EE) expressed in kilowatt-hours per year and defined as:

EE = 2080(0.77)DHR where: 2080 = national average annual heating load hours 0.77 = adjustment factor DHR = design heating requirement and is equal to PE /1.2 in kilowatts. PE = as defined in 2.1 of this appendix 1.2 = typical oversizing factor for primary electric heaters

3.2 Annual energy consumption for primary electric heaters by geographic region of the United States. For primary electric heaters, calculate the annual energy consumption by geographic region of the United States (ER) expressed in kilowatt-hours per year and defined as:

ER = HLH(0.77) (DHR) where: HLH = heating load hours for a specific region determined from Figure 1 of this appendix in hours 0.77 = as defined in 3.1 of this appendix DHR = as defined in 3.1 of this appendix

3.3 Rated output for electric heaters. Calculate the rated output (Qout) for electric heaters, expressed in Btu's per hour, and defined as:

Qout = PE (3,412 Btu/kWh) where: PE = as defined in 2.1 of this appendix

3.4 Rated output for unvented heaters using either natural gas, propane, or oil. For unvented heaters using either natural gas, propane, or oil equipped without auxiliary electrical systems, the rated output (Qout), expressed in Btu's per hour, is equal to PF, as determined in section 2.2 of this appendix.

For unvented heaters using either natural gas, propane, or oil equipped with auxiliary electrical systems, calculate the rated output (Qout), expressed in Btu's per hour, and defined as:

Qout = PF + PA (3,412 Btu/kWh) where: PF = as defined in 2.2 of this appendix in Btu/hr PA = as defined in 2.1 of this appendix in Btu/hr (Energy Policy and Conservation Act, Pub. L. 94-163, as amended by Pub. L. 94-385; Federal Energy Administration Act of 1974, Pub. L. 93-275, as amended by Pub. L. 94-385; Department of Energy Organization Act, Pub. L. 95-91; E.O. 11790, 39 FR 23185) [43 FR 20132, May 10, 1978. Redesignated and amended at 44 FR 37938, June 29, 1979; 49 FR 12157, Mar. 28, 1984; 77 FR 74571, Dec. 17, 2012]

Appendix H - Appendix H to Subpart B of Part 430—Uniform Test Method for Measuring the Power Consumption of Television Sets

Note:

On or after April 14, 2023 and prior to September 11, 2023, any representations made with respect to the energy use or energy efficiency of a television must be based upon results generated under this appendix as it appeared in 10 CFR part 430 edition revised as of January 1, 2023, or this appendix. Beginning September 11, 2023 any representations made with respect to the energy use or efficiency of a television must be based upon results generated under this appendix. Given that beginning September 11, 2023, representations with respect to the energy use or efficiency of televisions must be made in accordance with tests conducted pursuant to this appendix, manufacturers may wish to begin using this test procedure as soon as possible.

0. Incorporation by Reference

DOE incorporated by reference in § 430.3, ANSI/CTA-2037-D in its entirety. However, only enumerated provisions of ANSI/CTA-2037-D are applicable to this appendix, as follows:

0.1 ANSI/CTA-2037-D

(a) Section 5 as referenced in section 2 of this appendix;

(b) Sections 6 and 8 through 11 as referenced in section 3 of this appendix;

(c) Section 7 as referenced in sections 3 and 4 of this appendix; and

(d) Annex A as referenced in section 4 of this appendix.

0.2 [Reserved] 1. Scope

This appendix covers the test requirements used to measure the energy and power consumption of television sets that have a diagonal screen size of at least fifteen inches; and are powered by mains power (including TVs with auxiliary batteries but not TVs with main batteries).

2. Definitions and Symbols

2.1. Definitions. The following terms are defined according to section 5.1 of ANSI/CTA-2037-D.

(a) Annual energy consumption (b) Automatic brightness control (c) Brightest selectable picture setting (d) Default preset picture setting (e) Dynamic Luminance (f) Energy-Efficient-Ethernet (g) Filmmaker Mode (h) Forced menu (i) Gloss Unit (GU) (j) HDR10 (k) High Dynamic Range (l) Home configuration (m) Hybrid Log Gamma (HLG) (n) Illuminance (o) International System of Units (p) Luminance (q) Main battery (r) Motion-Based Dynamic Dimming (s) Neutral density filter (t) Off Mode (u) On Mode (v) Perceptual Quantization Video (w) Preset picture setting (x) Quick start (y) Retail Configuration (z) Snoot (aa) Software (ab) Wake-By-Remote-Control-App (ac) Wake-By-Smart-Speaker (ad) Wake-On-Cast

2.2. Symbol usage. The symbols and abbreviations in section 5.2 of ANSI/CTA-2037-D apply to this test procedure.

3. Test Conduct

Determine the dynamic luminance and on mode and standby mode power consumption of TVs by following the procedure specified in sections 6 through 11 of ANSI/CTA-2037-D.

4. Calculation of Measured Values

Calculate the on mode power consumption, dynamic luminance, standby mode power consumption, and annual energy consumption as specified in Annex A of ANSI/CTA-2037-D. The following additional requirements are also applicable.

4.1. Round on mode power value as specified in Annex A of ANSI/CTA-2037-D.

4.2. Round dynamic luminance to the nearest tenth.

4.3. Round standby mode power as specified in section 7.1.2 of ANSI/CTA-2037-D.

4.4. Round annual energy consumption as specified in Annex A of ANSI/CTA-2037-D.

[88 FR 16109, Mar. 15, 2023]

Appendix I - Appendix I to Subpart B of Part 430—Uniform Test Method for Measuring the Energy Consumption of Microwave Ovens

Note:

After September 26, 2022, representations made with respect to the energy use of microwave ovens must fairly disclose the results of testing pursuant to this appendix.

On or after April 29, 2022 and prior to September 26, 2022 representations, including compliance certifications, made with respect to the energy use of microwave ovens must fairly disclose the results of testing pursuant to either this appendix or appendix I as it appeared at 10 CFR part 430, subpart B, in the 10 CFR parts 200 to 499 edition revised as of January 1, 2020. Representations made with respect to the energy use of microwave ovens within that range of time must fairly disclose the results of testing under the selected version. Given that after September 26, 2022 representations with respect to the energy use of microwave ovens must be made in accordance with tests conducted pursuant to this appendix, manufacturers may wish to begin using this test procedure as soon as possible.

1. Definitions

The following definitions apply to the test procedures in this appendix, including the test procedures incorporated by reference:

1.1 Active mode means a mode in which the product is connected to a mains power source, has been activated, and is performing the main function of producing heat by means of a gas flame, electric resistance heating, electric inductive heating, or microwave energy.

1.2 Built-in means the product is enclosed in surrounding cabinetry, walls, or other similar structures on at least three sides, and can be supported by surrounding cabinetry or the floor.

1.3 Combined cooking product means a household cooking appliance that combines a cooking product with other appliance functionality, which may or may not include another cooking product. Combined cooking products include the following products: Conventional range, microwave/conventional cooking top, microwave/conventional oven, and microwave/conventional range.

1.4 Drop-in means the product is supported by horizontal surface cabinetry.

1.5 IEC 62301 (First Edition) means the test standard published by the International Electrotechnical Commission, titled “Household electrical appliances—Measurement of standby power,” Publication 62301 (First Edition 2005-06) (incorporated by reference; see § 430.3).

1.6 IEC 62301 (Second Edition) means the test standard published by the International Electrotechnical Commission, titled “Household electrical appliances—Measurement of standby power,” Publication 62301 (Edition 2.0 2011-01) (incorporated by reference; see § 430.3).

1.7 Normal non-operating temperature means a temperature of all areas of an appliance to be tested that is within 5 °F (2.8 °C) of the temperature that the identical areas of the same basic model of the appliance would attain if it remained in the test room for 24 hours while not operating with all oven doors closed.

1.8 Off mode means any mode in which a cooking product is connected to a mains power source and is not providing any active mode or standby function, and where the mode may persist for an indefinite time. An indicator that only shows the user that the product is in the off position is included within the classification of an off mode.

1.9 Standby mode means any mode in which a cooking product is connected to a mains power source and offers one or more of the following user-oriented or protective functions which may persist for an indefinite time:

(1) Facilitation of the activation of other modes (including activation or deactivation of active mode) by remote switch (including remote control), internal sensor, or timer;

(2) Provision of continuous functions, including information or status displays (including clocks) or sensor-based functions. A timer is a continuous clock function (which may or may not be associated with a display) that allows for regularly scheduled tasks and that operates on a continuous basis.

2. Test Conditions

2.1 Installation. Install a drop-in or built-in cooking product in a test enclosure in accordance with manufacturer's instructions. If the manufacturer's instructions specify that the cooking product may be used in multiple installation conditions, install the appliance according to the built-in configuration. Completely assemble the product with all handles, knobs, guards, and similar components mounted in place. Position any electric resistance heaters and baffles in accordance with the manufacturer's instructions.

2.1.1 Microwave ovens, excluding any microwave oven component of a combined cooking product. Install the microwave oven in accordance with the manufacturer's instructions and connect to an electrical supply circuit with voltage as specified in section 2.2.1 of this appendix. Install the microwave oven in accordance with Section 5, Paragraph 5.2 of IEC 62301 (Second Edition) (incorporated by reference; see § 430.3), disregarding the provisions regarding batteries and the determination, classification, and testing of relevant modes. If the microwave oven can communicate through a network (e.g., Bluetooth® or internet connection), disable the network function, if it is possible to disable it by means provided in the manufacturer's user manual, for the duration of testing. If the network function cannot be disabled, or means for disabling the function are not provided in the manufacturer's user manual, test the microwave oven with the network function in the factory default setting or in the as-shipped condition as instructed in Section 5, paragraph 5.2 of IEC 62301 (Second Edition). Configure the unit such that the clock display remains on during testing, regardless of manufacturer's instructions or default setting or supplied setting, unless the clock display powers down automatically with no option for the consumer to override this function. Install a watt meter in the circuit that meets the requirements of section 2.8.1.2 of this appendix.

2.2 Energy supply.

2.2.1 Electrical supply.

2.2.1.1 Voltage. For microwave oven testing, maintain the electrical supply to the unit at 240/120 volts ±1 percent. Maintain the electrical supply frequency for all products at 60 hertz ±1 percent.

2.3 Air circulation. Maintain air circulation in the room sufficient to secure a reasonably uniform temperature distribution, but do not cause a direct draft on the unit under test.

2.4 Ambient room test conditions.

2.4.1 Standby mode and off mode ambient temperature. For standby mode and off mode testing, maintain room ambient air temperature conditions as specified in Section 4, Paragraph 4.2 of IEC 62301 (Second Edition) (incorporated by reference; see § 430.3).

2.5 Normal non-operating temperature. All areas of the appliance to be tested must attain the normal non-operating temperature, as defined in section 1.7 of this appendix, before any testing begins. Measure the applicable normal non-operating temperature using the equipment specified in sections 2.6.2.1 of this appendix.

2.6 Instrumentation. Perform all test measurements using the following instruments, as appropriate:

2.6.1 Electrical Measurements.

2.6.1.1 Standby mode and off mode watt meter. The watt meter used to measure standby mode and off mode power must meet the requirements specified in Section 4, Paragraph 4.4 of IEC 62301 (Second Edition) (incorporated by reference; see § 430.3). For microwave oven standby mode and off mode testing, if the power measuring instrument used for testing is unable to measure and record the crest factor, power factor, or maximum current ratio during the test measurement period, measure the crest factor, power factor, and maximum current ratio immediately before and after the test measurement period to determine whether these characteristics meet the requirements specified in Section 4, Paragraph 4.4 of IEC 62301 (Second Edition).

2.6.2 Temperature measurement equipment.

2.6.2.1 Room temperature indicating system. For the test of microwave ovens, the room temperature indicating system must have an error no greater than ±1 °F (±0.6 °C) over the range 65° to 90 °F (18 °C to 32 °C).

3. Test Methods and Measurements

3.1. Test methods.

3.1.1 Microwave oven.

3.1.1.1 Microwave oven test standby mode and off mode power except for any microwave oven component of a combined cooking product. Establish the testing conditions set forth in section 2, Test Conditions, of this appendix. For microwave ovens that drop from a higher power state to a lower power state as discussed in Section 5, Paragraph 5.1, Note 1 of IEC 62301 (Second Edition) (incorporated by reference; see § 430.3), allow sufficient time for the microwave oven to reach the lower power state before proceeding with the test measurement. Follow the test procedure as specified in Section 5, Paragraph 5.3.2 of IEC 62301 (Second Edition). For units in which power varies as a function of displayed time in standby mode, set the clock time to 3:23 and use the average power approach described in Section 5, Paragraph 5.3.2(a) of IEC 62301 (First Edition), but with a single test period of 10 minutes +0/−2 sec after an additional stabilization period until the clock time reaches 3:33. If a microwave oven is capable of operation in either standby mode or off mode, as defined in sections 1.9 and 1.8 of this appendix, respectively, or both, test the microwave oven in each mode in which it can operate.

3.2 Test measurements.

3.2.1 Microwave oven standby mode and off mode power except for any microwave oven component of a combined cooking product. Make measurements as specified in Section 5, Paragraph 5.3 of IEC 62301 (Second Edition) (incorporated by reference; see § 430.3). If the microwave oven is capable of operating in standby mode, as defined in section 1.9 of this appendix, measure the average standby mode power of the microwave oven, PSB, in watts as specified in section 3.1.1.1 of this appendix. If the microwave oven is capable of operating in off mode, as defined in section 1.8 of this appendix, measure the average off mode power of the microwave oven, POM, as specified in section 3.1.1.1.

3.3 Recorded values.

3.3.1 For microwave ovens except for any microwave oven component of a combined cooking product, record the average standby mode power, PSB, for the microwave oven standby mode, as determined in section 3.2.1 of this appendix for a microwave oven capable of operating in standby mode. Record the average off mode power, POM, for the microwave oven off mode power test, as determined in section 3.2.1 of this appendix for a microwave oven capable of operating in off mode.

[85 FR 50766, Aug. 18, 2020, as amended at 87 FR 18271, Mar. 30, 2022; 87 FR 51538, Aug. 22, 2022]

Appendix I1 - Appendix I1 to Subpart B of Part 430—Uniform Test Method for Measuring the Energy Consumption of Conventional Cooking Products

Note:

Any representation related to energy consumption of conventional cooking tops, including the conventional cooking top component of combined cooking products, made after February 20, 2023 must be based upon results generated under this test procedure. Upon the compliance date(s) of any energy conservation standard(s) for conventional cooking tops, including the conventional cooking top component of combined cooking products, use of the applicable provisions of this test procedure to demonstrate compliance with the energy conservation standard is required.

0. Incorporation by Reference

DOE incorporated by reference in § 430.3, the entire test standard for IEC 60350-2; IEC 62301 (First Edition); and IEC 62301 (Second Edition). However, only enumerated provisions of those standards are applicable to this appendix, as follows. If there is a conflict, the language of the test procedure in this appendix takes precedence over the referenced test standards.

0.1 IEC 60350-2

(a) Section 5.1 as referenced in section 2.4.1 of this appendix;

(b) Section 5.3 as referenced in sections 2.7.1.1, 2.7.3.1, 2.7.3.3, 2.7.3.4, 2.7.4, and 2.7.5 of this appendix;

(c) Section 5.5 as referenced in section 2.5.1 of this appendix;

(d) Section 5.6.1 as referenced in section 2.6.1 of this appendix;

(e) Section 5.6.1.5 as referenced in section 3.1.1.2 of this appendix;

(f) Section 6.3 as referenced in section 3.1.1.1.1 of this appendix;

(g) Section 6.3.1 as referenced in section 3.1.1.1.1 of this appendix;

(h) Section 6.3.2 as referenced in section 3.1.1.1.1 of this appendix;

(i) Section 7.5.1 as referenced in section 2.6.2 of this appendix;

(j) Section 7.5.2 as referenced in section 3.1.4.4 of this appendix;

(k) Section 7.5.2.1 as referenced in sections 1 and 3.1.4.2 of this appendix;

(l) Section 7.5.2.2 as referenced in section 3.1.4.4 of this appendix;

(m) Section 7.5.4.1 as referenced in sections 1 and 3.1.4.5 of this appendix;

(n) Annex A as referenced in section 3.1.1.2 of this appendix;

(o) Annex B as referenced in sections 2.6.1 and 2.8.3 of this appendix; and

(p) Annex C as referenced in section 3.1.4.1 of this appendix.

0.2 IEC 62301 (First Edition)

(a) Paragraph 5.3 as referenced in section 3.2 of this appendix; and

(b) Paragraph 5.3.2 as referenced in section 3.2 of this appendix.

0.3 IEC 62301 (Second Edition)

(a) Paragraph 4.2 as referenced in section 2.4.2 of this appendix;

(b) Paragraph 4.3.2 as referenced in section 2.2.1.1.2 of this appendix;

(c) Paragraph 4.4 as referenced in section 2.7.1.2 of this appendix;

(d) Paragraph 5.1 as referenced in section 3.2 of this appendix; and

(e) Paragraph 5.3.2 as referenced in section 3.2 of this appendix.

1. Definitions

The following definitions apply to the test procedures in this appendix, including the test procedures incorporated by reference:

Active mode means a mode in which the product is connected to a mains power source, has been activated, and is performing the main function of producing heat by means of a gas flame, electric resistance heating, or electric inductive heating.

Built-in means the product is enclosed in surrounding cabinetry, walls, or other similar structures on at least three sides, and can be supported by surrounding cabinetry or the floor.

Combined cooking product means a household cooking appliance that combines a cooking product with other appliance functionality, which may or may not include another cooking product. Combined cooking products include the following products: conventional range, microwave/conventional cooking top, microwave/conventional oven, and microwave/conventional range.

Combined low-power mode means the aggregate of available modes other than active mode, but including the delay start mode portion of active mode.

Cooking area means an area on a conventional cooking top surface heated by an inducted magnetic field where cookware is placed for heating, where more than one cookware item can be used simultaneously and controlled separately from other cookware placed on the cooking area, and that may or may not include limitative markings.

Cooking top control means a part of the conventional cooking top used to adjust the power and the temperature of the cooking zone or cooking area for one cookware item.

Cooking zone means a part of a conventional cooking top surface that is either a single electric resistance heating element, multiple concentric sizes of electric resistance heating elements, an inductive heating element, or a gas surface unit that is defined by limitative markings on the surface of the cooking top and can be controlled independently of any other cooking area or cooking zone.

Cycle finished mode means a standby mode in which a conventional cooking top provides continuous status display following operation in active mode.

Drop-in means the product is supported by horizontal surface cabinetry.

Freestanding means the product is supported by the floor and is not specified in the manufacturer's instructions as able to be installed such that it is enclosed by surrounding cabinetry, walls, or other similar structures.

Inactive mode means a standby mode that facilitates the activation of active mode by remote switch (including remote control), internal sensor, or timer, or that provides continuous status display.

Infinite power settings means a cooking zone control without discrete power settings, which allows for selection of any power setting up to the maximum power setting.

Maximum-below-threshold power setting means the power setting on a conventional cooking top that is the highest power setting that results in smoothened water temperature data that do not meet the evaluation criteria specified in Section 7.5.4.1 of IEC 60350-2.

Maximum power setting means the maximum possible power setting if only one cookware item is used on the cooking zone or cooking area of a conventional cooking top, including any optional power boosting features. For conventional electric cooking tops with multi-ring cooking zones or cooking areas, the maximum power setting is the maximum power corresponding to the concentric heating element with the largest diameter, which may correspond to a power setting which may include one or more of the smaller concentric heating elements. For conventional gas cooking tops with multi-ring cooking zones, the maximum power setting is the maximum heat input rate when the maximum number of rings of the cooking zone are ignited.

Minimum-above-threshold power setting means the power setting on a conventional cooking top that is the lowest power setting that results in smoothened water temperature data that meet the evaluation criteria specified in Section 7.5.4.1 of IEC 60350-2. This power setting is also referred to as the simmering setting.

Multi-ring cooking zone means a cooking zone on a conventional cooking top with multiple concentric sizes of electric resistance heating elements or gas burner rings.

Off mode means any mode in which a product is connected to a mains power source and is not providing any active mode or standby function, and where the mode may persist for an indefinite time. An indicator that only shows the user that the product is in the off position is included within the classification of an off mode.

Power setting means a setting on a cooking zone control that offers a gas flame, electric resistance heating, or electric inductive heating.

Simmering period means, for each cooking zone, the 20-minute period during the simmering test starting at time t90.

Smoothened water temperature means the 40-second moving-average temperature as calculated in Section 7.5.4.1 of IEC 60350-2, rounded to the nearest 0.1 degree Celsius.

Specialty cooking zone means a warming plate, grill, griddle, or any cooking zone that is designed for use only with non-circular cookware, such as a bridge zone. Specialty cooking zones are not tested under this appendix.

Stable temperature means a temperature that does not vary by more than 1 °C over a 5-minute period.

Standard cubic foot of gas means the quantity of gas that occupies 1 cubic foot when saturated with water vapor at a temperature of 60 °F and a pressure of 14.73 pounds per square inch (30 inches of mercury or 101.6 kPa).

Standby mode means any mode in which a product is connected to a mains power source and offers one or more of the following user-oriented or protective functions which may persist for an indefinite time:

(1) Facilitation of the activation of other modes (including activation or deactivation of active mode) by remote switch (including remote control), internal sensor, or timer;

(2) Provision of continuous functions, including information or status displays (including clocks) or sensor-based functions. A timer is a continuous clock function (which may or may not be associated with a display) that allows for regularly scheduled tasks and that operates on a continuous basis.

Target turndown temperature (Tctarget) means the temperature as calculated according to Section 7.5.2.1 of IEC 60350-2 and section 3.1.4.2 of this appendix, for each cooking zone.

Thermocouple means a device consisting of two dissimilar metals which are joined together and, with their associated wires, are used to measure temperature by means of electromotive force.

Time t90 means the first instant during the simmering test for each cooking zone at which the smoothened water temperature is greater than or equal to 90 °C.

Turndown temperature (Tc) means, for each cooking zone, the measured water temperature at the time at which the tester begins adjusting the cooking top controls to change the power setting.

2. Test Conditions and Instrumentation

2.1 Installation. Install the conventional cooking top or combined cooking product in accordance with the manufacturer's instructions. If the manufacturer's instructions specify that the product may be used in multiple installation conditions, install the product according to the built-in configuration. Completely assemble the product with all handles, knobs, guards, and similar components mounted in place. Position any electric resistance heaters, gas burners, and baffles in accordance with the manufacturer's instructions. If the product can communicate through a network (e.g., Bluetooth® or internet connection), disable the network function, if it is possible to disable it by means provided in the manufacturer's user manual, for the duration of testing. If the network function cannot be disabled, or if means for disabling the function are not provided in the manufacturer's user manual, the product shall be tested in the factory default setting or in the as-shipped condition.

2.1.1 Freestanding combined cooking product. Install a freestanding combined cooking product with the back directly against, or as near as possible to, a vertical wall which extends at least 1 foot above the product and 1 foot beyond both sides of the product, and with no side walls.

2.1.2 Drop-in or built-in combined cooking product. Install a drop-in or built-in combined cooking product in a test enclosure in accordance with manufacturer's instructions.

2.1.3 Conventional cooking top. Install a conventional cooking top with the back directly against, or as near as possible to, a vertical wall which extends at least 1 foot above the product and 1 foot beyond both sides of the product.

2.2 Energy supply.

2.2.1 Electrical supply.

2.2.1.1 Supply voltage.

2.2.1.1.1 Active mode supply voltage. During active mode testing, maintain the electrical supply to the product at either 240 volts ±1 percent or 120 volts ±1 percent, according to the manufacturer's instructions, except for products which do not allow for a mains electrical supply. The actual voltage shall be maintained and recorded throughout the test. Instantaneous voltage fluctuations caused by the turning on or off of electrical components shall not be considered.

2.2.1.1.2 Standby mode and off mode supply voltage. During standby mode and off mode testing, maintain the electrical supply to the product at either 240 volts ±1 percent, or 120 volts ±1 percent, according to the manufacturer's instructions. Maintain the electrical supply voltage waveform specified in Section 4, Paragraph 4.3.2 of IEC 62301 (Second Edition), disregarding the provisions regarding batteries and the determination, classification, and testing of relevant modes. If the power measuring instrument used for testing is unable to measure and record the total harmonic content during the test measurement period, total harmonic content may be measured and recorded immediately before and after the test measurement period.

2.2.1.2 Supply frequency. Maintain the electrical supply frequency for all tests at 60 hertz ±1 percent.

2.2.2 Gas supply.

2.2.2.1 Natural gas. Maintain the natural gas pressure immediately ahead of all controls of the unit under test at 7 to 10 inches of water column, except as specified in section 3.1.3 of this appendix. The natural gas supplied should have a higher heating value (dry-basis) of approximately 1,025 Btu per standard cubic foot. Obtain the higher heating value on a dry basis of gas, Hn, in Btu per standard cubic foot, for the natural gas to be used in the test either from measurements made by the manufacturer conducting the test using equipment that meets the requirements described in section 2.7.2.2 of this appendix or by the use of bottled natural gas whose gross heating value is certified to be at least as accurate a value that meets the requirements in section 2.7.2.2 of this appendix.

2.2.2.2 Propane. Maintain the propane pressure immediately ahead of all controls of the unit under test at 11 to 13 inches of water column, except as specified in section 3.1.3 of this appendix. The propane supplied should have a higher heating value (dry-basis) of approximately 2,500 Btu per standard cubic foot. Obtain the higher heating value on a dry basis of gas, Hp, in Btu per standard cubic foot, for the propane to be used in the test either from measurements made by the manufacturer conducting the test using equipment that meets the requirements described in section 2.7.2.2 of this appendix, or by the use of bottled propane whose gross heating value is certified to be at least as accurate a value that meets the requirements described in section 2.7.2.2 of this appendix.

2.3 Air circulation. Maintain air circulation in the room sufficient to secure a reasonably uniform temperature distribution, but do not cause a direct draft on the unit under test.

2.4 Ambient room test conditions.

2.4.1 Active mode ambient conditions. During active mode testing, maintain the ambient room air pressure specified in Section 5.1 of IEC 60350-2, and maintain the ambient room air temperature at 25 ± 5 °C with a target temperature of 25 °C.

2.4.2 Standby mode and off mode ambient conditions. During standby mode and off mode testing, maintain the ambient room air temperature conditions specified in Section 4, Paragraph 4.2 of IEC 62301 (Second Edition).

2.5 Product temperature.

2.5.1 Product temperature stability. Prior to any testing, the product must achieve a stable temperature meeting the ambient room air temperature specified in section 2.4 of this appendix. For all conventional cooking tops, forced cooling may be used to assist in reducing the temperature of the product between tests, as specified in Section 5.5 of IEC 60350-2. Forced cooling must not be used during the period of time used to assess temperature stability.

2.5.2 Product temperature measurement. Measure the product temperature in degrees Celsius using the equipment specified in section 2.7.3.3 of this appendix at the following locations.

2.5.2.1 Measure the product temperature at the center of the cooking zone under test for any gas burner adjustment in section 3.1.3 of this appendix and per-cooking zone energy consumption test in section 3.1.4 of this appendix, except that the product temperature measurement is not required for any potential simmering setting pre-selection test in section 3.1.4.3 of this appendix. For a conventional gas cooking top, measure the product temperature inside the burner body of the cooking zone under test, after temporarily removing any burner cap on that cooking zone.

2.5.2.2 Measure the temperature at the center of each cooking zone for the standby mode and off mode power test in section 3.2 of this appendix. For a conventional gas cooking top, measure the temperature inside the burner body of each cooking zone, after temporarily removing any burner cap on that cooking zone. Calculate the product temperature as the average of the temperatures at the center of each cooking zone.

2.6 Test loads.

2.6.1 Test vessels. The test vessel for active mode testing of each cooking zone must meet the specifications in Section 5.6.1 and Annex B of IEC 60350-2.

2.6.2 Water load. The water used to fill the test vessels for active mode testing must meet the specifications in Section 7.5.1 of IEC 60350-2. The water temperature at the start of each test, except for the gas burner adjustment in section 3.1.3 of this appendix and the potential simmering setting pre-selection test in section 3.1.4.3 of this appendix, must have an initial temperature equal to 25 ± 0.5 °C.

2.7 Instrumentation. Perform all test measurements using the following instruments, as appropriate:

2.7.1 Electrical measurements.

2.7.1.1 Active mode watt-hour meter. The watt-hour meter for measuring the active mode electrical energy consumption must have a resolution as specified in Table 1 of Section 5.3 of IEC 60350-2. Measurements shall be made as specified in Table 2 of Section 5.3 of IEC 60350-2.

2.7.1.2 Standby mode and off mode watt meter. The watt meter used to measure standby mode and off mode power must meet the specifications in Section 4, Paragraph 4.4 of IEC 62301 (Second Edition). If the power measuring instrument used for testing is unable to measure and record the crest factor, power factor, or maximum current ratio during the test measurement period, measure the crest factor, power factor, and maximum current ratio immediately before and after the test measurement period to determine whether these characteristics meet the specifications in Section 4, Paragraph 4.4 of IEC 62301 (Second Edition).

2.7.2 Gas measurements.

2.7.2.1 Gas meter. The gas meter used for measuring gas consumption must have a resolution of 0.01 cubic foot or less and a maximum error no greater than 1 percent of the measured valued for any demand greater than 2.2 cubic feet per hour.

2.7.2.2 Standard continuous flow calorimeter. The maximum error of the basic calorimeter must be no greater than 0.2 percent of the actual heating value of the gas used in the test. The indicator readout must have a maximum error no greater than 0.5 percent of the measured value within the operating range and a resolution of 0.2 percent of the full-scale reading of the indicator instrument.

2.7.2.3 Gas line temperature. The incoming gas temperature must be measured at the gas meter. The instrument for measuring the gas line temperature shall have a maximum error no greater than ±2 °F over the operating range.

2.7.2.4 Gas line pressure. The incoming gas pressure must be measured at the gas meter. The instrument for measuring the gas line pressure must have a maximum error no greater than 0.1 inches of water column.

2.7.3 Temperature measurements.

2.7.3.1 Active mode ambient room temperature. The room temperature indicating system must meet the specifications in Table 1 of Section 5.3 of IEC 60350-2. Measurements shall be made as specified in Table 2 of Section 5.3 of IEC 60350-2.

2.7.3.2 Standby mode and off mode ambient room temperature. The room temperature indicating system must have an error no greater than ±1 °F (±0.6 °C) over the range 65° to 90 °F (18 °C to 32 °C).

2.7.3.3 Product temperature. The temperature indicating system must have an error no greater than ±1 °F (±0.6 °C) over the range 65° to 90 °F (18 °C to 32 °C). Measurements shall be made as specified in Table 2 of Section 5.3 of IEC 60350-2.

2.7.3.4 Water temperature. Measure the test vessel water temperature with a thermocouple that meets the specifications in Table 1 of Section 5.3 of IEC 60350-2. Measurements shall be made as specified in Table 2 of Section 5.3 of IEC 60350-2.

2.7.4 Room air pressure. The room air pressure indicating system must meet the specifications in Table 1 of Section 5.3 of IEC 60350-2.

2.7.5 Water mass. The scale used to measure the mass of the water load must meet the specifications in Table 1 of Section 5.3 of IEC 60350-2.

2.8 Power settings.

2.8.1 On a multi-ring cooking zone on a conventional gas cooking top, all power settings are considered, whether they ignite all rings of orifices or not.

2.8.2 On a multi-ring cooking zone on a conventional electric cooking top, only power settings corresponding to the concentric heating element with the largest diameter are considered, which may correspond to operation with one or more of the smaller concentric heating elements energized.

2.8.3 On a cooking zone with infinite power settings where the available range of rotation from maximum to minimum is more than 150 rotational degrees, evaluate power settings that are spaced by 10 rotational degrees. On a cooking zone with infinite power settings where the available range of rotation from maximum to minimum is less than or equal to 150 rotational degrees, evaluate power settings that are spaced by 5 rotational degrees, starting with the first position that meets the definition of a power setting, irrespective of how the knob is labeled. Polar coordinate paper, as provided in Annex B of IEC 60350-2 may be used to mark power settings.

3. Test Methods and Measurements

3.1 Active mode. Perform the following test methods for conventional cooking tops and the conventional cooking top component of a combined cooking product.

3.1.1 Test vessel and water load selection.

3.1.1.1 Conventional electric cooking tops.

3.1.1.1.1 For cooking zones, measure the size of each cooking zone as specified in Section 6.3.2 of IEC 60350-2, not including any specialty cooking zones as defined in section 1 of this appendix. For circular cooking zones on smooth cooking tops, the cooking zone size is determined using the outer diameter of the printed marking, as specified in Section 6.3 of IEC 60350-2. For open coil cooking zones, the cooking zone size is determined using the widest diameter of the coil, see Figure 3.1.1.1. For non-circular cooking zones, the cooking zone size is determined by the measurement of the shorter side or minor axis. For cooking areas, determine the number of cooking zones as specified in Section 6.3.1 of IEC 60350-2.

3.1.1.1.2 Determine the test vessel diameter in millimeters (mm) and water load mass in grams (g) for each measured cooking zone. For cooking zones, test vessel selection is based on cooking zone size as specified in Table 3 in Section 5.6.1.5 of IEC 60350-2. For cooking areas, test vessel selection is based on the number of cooking zones as specified in Annex A of IEC 60350-2. If a selected test vessel (including its lid) cannot be centered on the cooking zone due to interference with a structural component of the cooking top, the test vessel with the largest diameter that can be centered on the cooking zone shall be used. The allowable tolerance on the water load weight is ±0.5 g.

3.1.1.2 Conventional gas cooking tops.

3.1.1.2.1 Record the nominal heat input rate for each cooking zone, not including any specialty cooking zones as defined in section 1 of this appendix.

3.1.1.2.2 Determine the test vessel diameter in mm and water load mass in g for each measured cooking zone according to Table 3.1 of this appendix. If a selected test vessel cannot be centered on the cooking zone due to interference with a structural component of the cooking top, the test vessel with the largest diameter that can be centered on the cooking zone shall be used. The allowable tolerance on the water load weight is ±0.5 g.

Table 3.1—Test Vessel Selection for Conventional Gas Cooking Tops

Nominal gas burner input rate
(Btu/h)
Test vessel diameter
(mm)
Water load mass
(g)
Minimum
(>)
Maximum
(≤)
5,6002102,050 5,6008,0502402,700 8,05014,3002703,420 14,3003004,240

3.1.2 Unit Preparation. Before the first measurement is taken, all cooking zones must be operated simultaneously for at least 10 minutes at maximum power. This step shall be conducted once per product.

3.1.3 Gas burner adjustment. Prior to active mode testing of each tested burner of a conventional gas cooking top, the burner heat input rate must be adjusted, if necessary, to within 2 percent of the nominal heat input rate of the burner as specified by the manufacturer. Prior to ignition and any adjustment of the burner heat input rate, the conventional cooking top must achieve the product temperature specified in section 2.5 of this appendix. Ignite and operate the gas burner under test with the test vessel and water mass specified in section 3.1.1 of this appendix. Measure the heat input rate of the gas burner under test starting 5 minutes after ignition. If the measured input rate of the gas burner under test is within 2 percent of the nominal heat input rate of the burner as specified by the manufacturer, no adjustment of the heat input rate shall be made.

3.1.3.1 Conventional gas cooking tops with an adjustable internal pressure regulator. If the measured heat input rate of the burner under test is not within 2 percent of the nominal heat input rate of the burner as specified by the manufacturer, adjust the product's internal pressure regulator such that the heat input rate of the burner under test is within 2 percent of the nominal heat input rate of the burner as specified by the manufacturer. Adjust the burner with sufficient air flow to prevent a yellow flame or a flame with yellow tips. Complete section 3.1.4 of this appendix while maintaining the same gas pressure regulator adjustment.

3.1.3.2 Conventional gas cooking tops with a non-adjustable internal pressure regulator or without an internal pressure regulator. If the measured heat input rate of the burner under test is not within 2 percent of the nominal heat input rate of the burner as specified by the manufacturer, remove the product's internal pressure regulator, or block it in the open position, and initially maintain the gas pressure ahead of all controls of the unit under test approximately equal to the manufacturer's recommended manifold pressure. Adjust the gas supply pressure such that the heat input rate of the burner under test is within 2 percent of the nominal heat input rate of the burner as specified by the manufacturer. Adjust the burner with sufficient air flow to prevent a yellow flame or a flame with yellow tips. Complete section 3.1.4 of this appendix while maintaining the same gas pressure regulator adjustment.

3.1.4 Per-cooking zone energy consumption test. Establish the test conditions set forth in section 2 of this appendix. Turn off the gas flow to the conventional oven(s), if so equipped. The product temperature must meet the specifications in section 2.5 of this appendix.

3.1.4.1 Test vessel placement. Position the test vessel with water load for the cooking zone under test, selected and prepared as specified in section 3.1.1 of this appendix, in the center of the cooking zone, and as specified in Annex C to IEC 60350-2.

3.1.4.2 Overshoot test. Use the test methods set forth in Section 7.5.2.1 of IEC 60350-2 to determine the target turndown temperature for each cooking zone, Tctarget, in degrees Celsius, as follows.

Tctarget = 93 °C − (Tmax − T70) Where: Tmax is highest recorded temperature value, in degrees Celsius; and T70 is the average recorded temperature between the time 10 seconds before the power is turned off and the time 10 seconds after the power is turned off.

If T70 is within the tolerance of 70 ± 0.5 °C, the target turndown temperature is the highest of 80 °C and the calculated Tctarget, rounded to the nearest integer. If T70 is outside of the tolerance, the overshoot test is considered invalid and must be repeated after allowing the product to return to ambient conditions.

3.1.4.3 Potential simmering setting pre-selection test. The potential simmering setting for each cooking zone may be determined using the potential simmering setting pre-selecting test. If a potential simmering setting is already known, it may be used instead of completing sections 3.1.4.3.1 through 3.1.4.3.4 of this appendix.

3.1.4.3.1 Use the test vessel with water load for the cooking zone under test, selected, prepared, and positioned as specified in sections 3.1.1 and 3.1.4.1 of this appendix. The temperature of the conventional cooking top is not required to meet the specification for the product temperature in section 2.5 of this appendix for the potential simmering setting pre-selection test. Operate the cooking zone under test with the lowest available power setting. Measure the energy consumption for 10 minutes ±2 seconds.

3.1.4.3.2 Calculate the power density of the power setting, j, on a conventional electric cooking top, Qej, in watts per square centimeter, as:

Where: a = the surface area of the test vessel bottom, in square centimeters; and Ej = the electrical energy consumption during the 10-minute test, in Wh.

3.1.4.3.3 Calculate the power density of the power setting, j, on a conventional gas cooking top, Qgj, in Btu/h per square centimeter, as:

Where: a = the surface area of the test vessel bottom, in square centimeters; Vj = the volume of gas consumed during the 10-minute test, in cubic feet; CF = the gas correction factor to standard temperature and pressure, as calculated in section 4.1.1.2.1 of this appendix; H = either Hn or Hp, the heating value of the gas used in the test as specified in sections 2.2.2.1 and 2.2.2.2 of this appendix, in Btu per standard cubic foot of gas; Eej = the electrical energy consumption of the conventional gas cooking top during the 10-minute test, in Wh; and Ke = 3.412 Btu/Wh, conversion factor of watt-hours to Btu.

3.1.4.3.4 Repeat the measurement for each successively higher power setting until Qej exceeds 0.8 W/cm 2 for conventional electric cooking tops or Qgj exceeds 4.0 Btu/h·cm 2 for conventional gas cooking tops.

For conventional cooking tops with rotating knobs for selecting the power setting, the selection knob shall be turned to the maximum power setting in between each test, to avoid hysteresis. The selection knob shall be turned in the direction from higher power to lower power to select the power setting for the test. If the appropriate power setting is passed, the selection knob shall be turned to the maximum power setting again before repeating the power setting selection.

Of the last two power settings tested, the potential simmering setting is the power setting that produces a power density closest to 0.8 W/cm 2 for conventional electric cooking tops or 4.0 Btu/h·cm 2 for conventional gas cooking tops. The closest power density may be higher or lower than the applicable threshold value.

3.1.4.4 Simmering test. The product temperature must meet the specifications in section 2.5 of this appendix at the start of each simmering test. For each cooking zone, conduct the test method specified in Section 7.5.2 of IEC 60350-2, using the potential simmering setting identified in section 3.1.4.3 of this appendix for the initial simmering setting used in Section 7.5.2.2 of IEC 60350-2.

For conventional cooking tops with rotating knobs for selecting the power setting, the selection knob shall be turned in the direction from higher power to lower power to select the potential simmering setting for the test, to avoid hysteresis. If the appropriate setting is passed, the test is considered invalid and must be repeated after allowing the product to return to ambient conditions.

3.1.4.5 Evaluation of the simmering test. Evaluate the test conducted under section 3.1.4.4 of this appendix as set forth in Section 7.5.4.1 of IEC 60350-2 according to Figure 3.1.4.5 of this appendix. If the measured turndown temperature, Tc, is not within -0.5 °C and +1 °C of the target turndown temperature, Tctarget, the test is considered invalid and must be repeated after allowing the product to return to ambient conditions.

3.2 Standby mode and off mode power. Establish the standby mode and off mode testing conditions set forth in section 2 of this appendix. For products that take some time to enter a stable state from a higher power state as discussed in Section 5, Paragraph 5.1, Note 1 of IEC 62301 (Second Edition), allow sufficient time for the product to reach the lower power state before proceeding with the test measurement. Follow the test procedure as specified in Section 5, Paragraph 5.3.2 of IEC 62301 (Second Edition) for testing in each possible mode as described in sections 3.2.1 and 3.2.2 of this appendix. For units in which power varies as a function of displayed time in standby mode, set the clock time to 3:23 at the end of an initial stabilization period, as specified in Section 5, Paragraph 5.3 of IEC 62301 (First Edition). After an additional 10-minute stabilization period, measure the power use for a single test period of 10 minutes +0/−2 seconds that starts when the clock time first reads 3:33. Use the average power approach described in Section 5, Paragraph 5.3.2(a) of IEC 62301 (First Edition).

3.2.1 If the product has an inactive mode, as defined in section 1 of this appendix, measure the average inactive mode power, PIA, in watts.

3.2.2 If the product has an off mode, as defined in section 1 of this appendix, measure the average off mode power, POM, in watts.

3.3 Recorded values.

3.3.1 Active mode.

3.3.1.1 For a conventional gas cooking top tested with natural gas, record the natural gas higher heating value in Btu per standard cubic foot, Hn, as determined in section 2.2.2.1 of this appendix for the natural gas supply, for each test. For a conventional gas cooking top tested with propane, record the propane higher heating value in Btu per standard cubic foot, Hp, as determined in section 2.2.2.2 of this appendix for the propane supply, for each test.

3.3.1.2 Record the test room temperature in degrees Celsius and relative air pressure in hectopascals (hPa) during each test.

3.3.1.3 Per-cooking zone energy consumption test.

3.3.1.3.1 Record the product temperature in degrees Celsius, TP, prior to the start of each overshoot test or simmering test, as determined in section 2.5 of this appendix.

3.3.1.3.2 Overshoot test. For each cooking zone, record the initial temperature of the water in degrees Celsius, Ti; the average water temperature between the time 10 seconds before the power is turned off and the time 10 seconds after the power is turned off in degrees Celsius, T70; the highest recorded water temperature in degrees Celsius, Tmax; and the target turndown temperature in degrees Celsius, Tctarget.

3.3.1.3.3 Simmering test. For each cooking zone, record the temperature of the water throughout the test, in degrees Celsius, and the values in sections 3.3.1.3.3.1 through 3.3.1.3.3.7 of this appendix for the Energy Test Cycle, if an Energy Test Cycle is measured in section 3.1.4.5 of this appendix, otherwise for both the maximum-below-threshold power setting and the minimum-above-threshold power setting. Because t90 may not be known until completion of the simmering test, water temperature, any electrical energy consumption, and any gas volumetric consumption measurements may be recorded for several minutes after the end of the simmering period to ensure that the full simmering period is recorded.

3.3.1.3.3.1 The power setting under test.

3.3.1.3.3.2 The initial temperature of the water, in degrees Celsius, Ti.

3.3.1.3.3.3 The time at which the tester begins adjusting the cooking top control to change the power setting, to the nearest second, tc and the turndown temperature, in degrees Celsius, Tc.

3.3.1.3.3.4 The time at which the simmering period starts, to the nearest second, t90.

3.3.1.3.3.5 The time at which the simmering period ends, to the nearest second, tS and the smoothened water temperature at the end of the simmering period, in degrees Celsius, TS.

3.3.1.3.3.6 For a conventional electric cooking top, the electrical energy consumption from the start of the test to tS, E, in watt-hours.

3.3.1.3.3.7 For a conventional gas cooking top, the volume of gas consumed from the start of the test to tS, V, in cubic feet of gas; and any electrical energy consumption of the cooking top from the start of the test to tS, Ee, in watt-hours.

3.3.2 Standby mode and off mode. Make measurements as specified in section 3.2 of this appendix. If the product is capable of operating in inactive mode, as defined in section 1 of this appendix, record the average inactive mode power, PIA, in watts as specified in section 3.2.1 of this appendix. If the product is capable of operating in off mode, as defined in section 1 of this appendix, record the average off mode power, POM, in watts as specified in section 3.2.2 of this appendix.

4. Calculation of Derived Results From Test Measurements

4.1. Active mode energy consumption of conventional cooking tops and any conventional cooking top component of a combined cooking product.

4.1.1 Per-cycle active mode energy consumption of a conventional cooking top and any conventional cooking top component of a combined cooking product.

4.1.1.1 Conventional electric cooking top per-cycle active mode energy consumption.

4.1.1.1.1 Conventional electric cooking top per-cooking zone normalized active mode energy consumption. For each cooking zone, calculate the per-cooking zone normalized active mode energy consumption of a conventional electric cooking top, E, in watt-hours, using the following equation:

E = EETC for cooking zones where an Energy Test Cycle was measured in section 3.1.4.5 of this appendix, and for cooking zones where a minimum-above-threshold cycle and a maximum-below-threshold cycle were measured in section 3.1.4.5 of this appendix. Where: EETC = the electrical energy consumption of the Energy Test Cycle from the start of the test to the end of the test for the cooking zone, as determined in section 3.1.4.5 of this appendix, in watt-hours; EMAT = the electrical energy consumption of the minimum-above-threshold power setting from the start of the test to the end of the test for the cooking zone, as determined in section 3.1.4.5 of this appendix, in watt-hours; EMBT = the electrical energy consumption of the maximum-below-threshold power setting from the start of the test to the end of the test for the cooking zone, as determined in section 3.1.4.5 of this appendix, in watt-hours; TS,MAT = the smoothened water temperature at the end of the minimum-above-threshold power setting test for the cooking zone, in degrees Celsius; and TS,MBT = the smoothened water temperature at the end of the maximum-below-threshold power setting test for the cooking zone, in degrees Celsius.

4.1.1.1.2 Calculate the per-cycle active mode total energy consumption of a conventional electric cooking top, ECET, in watt-hours, using the following equation:

Where: n = the total number of cooking zones tested on the conventional cooking top; Ez = the normalized energy consumption representative of the Energy Test Cycle for each cooking zone, as calculated in section 4.1.1.1.1 of this appendix, in watt-hours; mz is the mass of water used for each cooking zone, in grams; and 2853 = the representative water load mass, in grams.

4.1.1.2 Conventional gas cooking top per-cycle active mode energy consumption.

4.1.1.2.1 Gas correction factor to standard temperature and pressure. Calculate the gas correction factor to standard temperature and pressure, which converts between standard cubic feet and measured cubic feet of gas for a given set of test conditions:

Where: Pgas = the measured line gas gauge pressure, in inches of water column; 0.0361= the conversion factor from inches of water column to pounds per square inch; Patm = the measured atmospheric pressure, in pounds per square inch; Pbase = 14.73 pounds per square inch, the standard sea level air pressure; Tbase = 519.67 degrees Rankine (or 288.7 Kelvin); Tgas = the measured line gas temperature, in degrees Fahrenheit (or degrees Celsius); and Tk = the adder converting from degrees Fahrenheit to degrees Rankine, 459.7 (or from degrees Celsius to Kelvin, 273.16).

4.1.1.2.2 Conventional gas cooking top per-cooking zone normalized active mode gas energy consumption. For each cooking zone, calculate the per-cooking zone normalized active mode gas energy consumption of a conventional gas cooking top, Eg, in Btu, using the following equation:

Eg = Egt,ETC for cooking zones where an Energy Test Cycle was measured in section 3.1.4.5 of this appendix, and for cooking zones where a minimum-above-threshold cycle and a maximum-below-threshold cycle were measured in section 3.1.4.5 of this appendix. Where: Egt,ETC = the as-tested gas energy consumption of the Energy Test Cycle for the cooking zone, in Btu, calculated as the product of: V, the gas consumption of the Energy Test Cycle, as determined in section 3.1.4.5 of this appendix, in cubic feet; CF, the gas correction factor to standard temperature and pressure for the test, as calculated in section 4.1.1.2.1 of this appendix; and H, either Hn or Hp, the heating value of the gas used in the test as specified in sections 2.2.2.1 and 2.2.2.2 of this appendix, expressed in Btu per standard cubic foot of gas; Egt,MAT = the as-tested gas energy consumption of the minimum-above-threshold power setting for the cooking zone, in Btu, calculated as the product of: V, the gas consumption of the minimum-above-threshold power setting, as determined in section 3.1.4.5 of this appendix, in cubic feet; CF, the gas correction factor to standard temperature and pressure for the test, as calculated in section 4.1.1.2.1 of this appendix; and H, either Hn or Hp, the heating value of the gas used in the test as specified in sections 2.2.2.1 and 2.2.2.2 of this appendix, expressed in Btu per standard cubic foot of gas; Egt,MBT = the as-tested gas energy consumption of the maximum-below-threshold power setting for the cooking zone, in Btu, calculated as the product of: V, the gas consumption of the maximum-below-threshold power setting, as determined in section 3.1.4.5 of this appendix, in cubic feet; CF, the gas correction factor to standard temperature and pressure for the test, as calculated in section 4.1.1.2.1 of this appendix; and H, either Hn or Hp, the heating value of the gas used in the test as specified in sections 2.2.2.1 and 2.2.2.2 of this appendix, expressed in Btu per standard cubic foot of gas; TS,MAT = the smoothened water temperature at the end of the minimum-above-threshold power setting test for the cooking zone, in degrees Celsius; and TS,MBT = the smoothened water temperature at the end of the maximum-below-threshold power setting test for the cooking zone, in degrees Celsius.

4.1.1.2.3 Conventional gas cooking top per-cooking zone active mode normalized electrical energy consumption. For each cooking zone, calculate the per-cooking zone normalized active mode electrical energy consumption of a conventional gas cooking top, Ee, in watt-hours, using the following equation:

Ee = Ee,ETC for cooking zones where an Energy Test Cycle was measured in section 3.1.4.5 of this appendix, and for cooking zones where a minimum-above-threshold cycle and a maximum-below-threshold cycle were measured in section 3.1.4.5 of this appendix. Where: Ee,ETC = the electrical energy consumption of the Energy Test Cycle from the start of the test to the end of the test for the cooking zone, as determined in section 3.1.4.5 of this appendix, in watt-hours; Ee,MAT = the electrical energy consumption of the minimum-above-threshold power setting from the start of the test to the end of the test for the cooking zone, as determined in section 3.1.4.5 of this appendix, in watt-hours; Ee,MBT = the electrical energy consumption of the maximum-below-threshold power setting from the start of the test to the end of the test for the cooking zone, as determined in section 3.1.4.5 of this appendix, in watt-hours; TS,MAT = the smoothened water temperature at the end of the minimum-above-threshold power setting test for the cooking zone, in degrees Celsius; and TS,MBT = the smoothened water temperature at the end of the maximum-below-threshold power setting test for the cooking zone, in degrees Celsius.

4.1.1.2.4 Conventional gas cooking top per-cycle active mode gas energy consumption. Calculate the per-cycle active mode gas energy consumption of a conventional gas cooking top, ECGG, in Btu, using the following equation:

Where: n, mz, and 2853 are defined in section 4.1.1.1.2 of this appendix; and Egz = the normalized gas energy consumption representative of the Energy Test Cycle for each cooking zone, as calculated in section 4.1.1.2.2 of this appendix, in Btu.

4.1.1.2.5 Conventional gas cooking top per-cycle active mode electrical energy consumption. Calculate the per-cycle active mode electrical energy consumption of a conventional gas cooking top, ECGE, in watt-hours, using the following equation:

Where: n, mz, and 2853 are defined in section 4.1.1.1.2 of this appendix; and Eez = the normalized electrical energy consumption representative of the Energy Test Cycle for each cooking zone, as calculated in section 4.1.1.2.3 of this appendix, in watt-hours.

4.1.1.2.6 Conventional gas cooking top per-cycle active-mode total energy consumption. Calculate the per-cycle active mode total energy consumption of a conventional gas cooking top, ECGT, in Btu, using the following equation:

ECGT = ECGG + (ECGE × Ke) Where: ECGG = the per-cycle active mode gas energy consumption of a conventional gas cooking top as determined in section 4.1.1.2.4 of this appendix, in Btu; ECGE = the per-cycle active mode electrical energy consumption of a conventional gas cooking top as determined in section 4.1.1.2.5 of this appendix, in watt-hours; and Ke = 3.412 Btu/Wh, conversion factor of watt-hours to Btu.

4.1.2 Annual active mode energy consumption of a conventional cooking top and any conventional cooking top component of a combined cooking product.

4.1.2.1 Conventional electric cooking top annual active mode energy consumption. Calculate the annual active mode total energy consumption of a conventional electric cooking top, EAET, in kilowatt-hours per year, using the following equation:

EAET = ECET × K × NC Where: ECET = the conventional electric cooking top per-cycle active mode total energy consumption, as determined in section 4.1.1.1.2 of this appendix, in watt-hours; K = 0.001 kWh/Wh conversion factor for watt-hours to kilowatt-hours; and NC = 418 cooking cycles per year, the average number of cooking cycles per year normalized for duration of a cooking event estimated for conventional cooking tops.

4.1.2.2 Conventional gas cooking top annual active mode energy consumption.

4.1.2.2.1 Conventional gas cooking top annual active mode gas energy consumption. Calculate the annual active mode gas energy consumption of a conventional gas cooking top, EAGG, in kBtu per year, using the following equation:

EAGG = ECGG × K × NC Where: K and NC are defined in section 4.1.2.1 of this appendix; and ECGG = the conventional gas cooking top per-cycle active mode gas energy consumption, as determined in section 4.1.1.2.4 of this appendix, in Btu.

4.1.2.2.2 Conventional gas cooking top annual active mode electrical energy consumption. Calculate the annual active mode electrical energy consumption of a conventional gas cooking top, EAGE, in kilowatt-hours per year, using the following equation:

EAGE = ECGE × K × NC Where: K and NC are defined in section 4.1.2.1 of this appendix; and ECGE = the conventional gas cooking top per-cycle active mode electrical energy consumption, as determined in section 4.1.1.2.5 of this appendix, in watt-hours.

4.1.2.2.3 Conventional gas cooking top annual active mode total energy consumption. Calculate the annual active mode total energy consumption of a conventional gas cooking top, EAGT, in kBtu per year, using the following equation:

EAGT = EAGG + (EAGE × Ke) Where: EAGG = the conventional gas cooking top annual active mode gas energy consumption as determined in section 4.1.2.2.1 of this appendix, in kBtu per year; EAGE = the conventional gas cooking top annual active mode electrical energy consumption as determined in section 4.1.2.2.2 of this appendix, in kilowatt-hours per year; and Ke is defined in section 4.1.1.2.6 of this appendix.

4.2 Annual combined low-power mode energy consumption of a conventional cooking top and any conventional cooking top component of a combined cooking product.

4.2.1 Conventional cooking top annual combined low-power mode energy consumption. Calculate the annual combined low-power mode energy consumption for a conventional cooking top, ETLP, in kilowatt-hours per year, using the following equation:

ETLP = [(PIA × FIA) + (POM × FOM)] × K × ST Where: PIA = inactive mode power, in watts, as measured in section 3.2.1 of this appendix; POM = off mode power, in watts, as measured in section 3.2.2 of this appendix; FIA and FOM are the portion of annual hours spent in inactive mode and off mode hours respectively, as defined in Table 4.2.1 of this appendix; K = 0.001 kWh/Wh conversion factor for watt-hours to kilowatt-hours; and ST = 8,544, total number of inactive mode and off mode hours per year for a conventional cooking top.

Table 4.2.1—Annual Hour Multipliers

Types of low-power mode(s) available FIAFOMBoth inactive and off mode0.50.5 Inactive mode only10 Off mode only01

4.2.2 Conventional cooking top component of a combined cooking product annual combined low-power mode energy consumption. Calculate the annual combined low-power mode energy consumption for the conventional cooking top component of a combined cooking product, ETLP, in kilowatt-hours per year, using the following equation:

ETLP = [(PIA × FIA) + (POM × FOM)] × K × STOT × HC Where: PIA, POM, FIA, FOM, and K are defined in section 4.2.1 of this appendix; STOT = the total number of inactive mode and off mode hours per year for a combined cooking product, as defined in Table 4.2.2 of this appendix; and HC = the percentage of hours per year assigned to the conventional cooking top component of a combined cooking product, as defined in Table 4.2.2 of this appendix.

Table 4.2.2—Combined Cooking Product Usage Factors

Type of combined cooking product STOTHCCooking top and conventional oven (conventional range)8,39260 Cooking top and microwave oven8,48177 Cooking top, conventional oven, and microwave oven8,32951

4.3 Integrated annual energy consumption of a conventional cooking top and any conventional cooking top component of a combined cooking product.

4.3.1 Conventional electric cooking top integrated annual energy consumption. Calculate the integrated annual energy consumption, IAEC, of a conventional electric cooking top, in kilowatt-hours per year, using the following equation:

IAEC = EAET + ETLP Where: EAET = the conventional electric cooking top annual active mode energy consumption, as determined in section 4.1.2.1 of this appendix; and ETLP = the annual combined low-power mode energy consumption of a conventional cooking top or any conventional cooking top component of a combined cooking product, as determined in section 4.2 of this appendix.

4.3.2 Conventional gas cooking top integrated annual energy consumption. Calculate the integrated annual energy consumption, IAEC, of a conventional gas cooking top, in kBtu per year, defined as:

IAEC = EAGT + (ETLP × Ke)

Where: EAGT = the conventional gas cooking top annual active mode total energy consumption, as determined in section 4.1.2.2.3 of this appendix; ETLP = the annual combined low-power mode energy consumption of a conventional cooking top or any conventional cooking top component of a combined cooking product, as determined in section 4.2 of this appendix; and Ke is defined in section 4.1.1.2.6 of this appendix. [87 FR 51538, Aug. 22, 2022, as amended at 88 FR 7847, Feb. 7, 2023]

Appendix J - Appendix J to Subpart B of Part 430—Uniform Test Method for Measuring the Energy Consumption of Automatic and Semi-Automatic Clothes Washers

Note 1 to appendix J to subpart B of part 430:

Manufacturers must use the results of testing under appendix J2 to this subpart to determine compliance with the residential clothes washer standards provided at § 430.32(g)(1) and the commercial clothes washer standards provided at § 431.156(b).

Manufacturers must use the results of testing under this appendix to determine compliance with the residential clothes washer standards provided at § 430.32(g)(2) and for any amended commercial clothes washer standards provided at § 431.156 that are published after January 1, 2022.

Any representations related to energy or water consumption of residential or commercial clothes washers must be made in accordance with the appropriate appendix that applies (i.e., this appendix or appendix J2 to this subpart) when determining compliance with the relevant standard. Manufacturers may also use this appendix to certify compliance with the residential clothes washer standards provided at § 430.32(g)(2) or any amended standards for commercial clothes washers prior to the applicable compliance date for those standards.

0. Incorporation by Reference

DOE incorporated by reference in § 430.3, the entire test standard for IEC 62301. However, only enumerated provisions of this standard are applicable to this appendix, as follows. In cases in which there is a conflict, the language of the test procedure in this appendix takes precedence over the referenced test standard.

0.1 IEC 62301:

(a) Section 4.2 as referenced in section 2.4 of this appendix;

(b) Section 4.3.2 as referenced in section 2.1.2 of this appendix;

(c) Section 4.4 as referenced in section 2.5.3 of this appendix;

(d) Section 5.1 as referenced in section 3.5.2 of this appendix;

(e) Section 5.2 as referenced in section 2.10.2 of this appendix; and

(f) Section 5.3.2 as referenced in section 3.5.3 of this appendix.

0.2 [Reserved]

1. Definitions

Active mode means a mode in which the clothes washer is connected to a mains power source, has been activated, and is performing one or more of the main functions of washing, soaking, tumbling, agitating, rinsing, and/or removing water from the clothing, or is involved in functions necessary for these main functions, such as admitting water into the washer or pumping water out of the washer. Active mode also includes delay start and cycle finished modes.

Active-mode energy efficiency ratio means the quotient of the weighted-average load size divided by the total clothes washer energy consumption per cycle, with such energy consumption expressed as the sum of the machine electrical energy consumption, the hot water energy consumption, and the energy required for removal of the remaining moisture in the wash load.

Active washing mode means a mode in which the clothes washer is performing any of the operations included in a complete cycle intended for washing a clothing load, including the main functions of washing, soaking, tumbling, agitating, rinsing, and/or removing water from the clothing.

Bone-dry means a condition of a load of test cloth that has been dried in a dryer at maximum temperature for a minimum of 10 minutes, removed and weighed before cool down, and then dried again for 10 minute periods until the final weight change of the load is 1 percent or less.

Clothes container means the compartment within the clothes washer that holds the clothes during the operation of the machine.

Cold rinse means the coldest rinse temperature available on the machine, as indicated to the user on the clothes washer control panel.

Combined low-power mode means the aggregate of available modes other than active washing mode, including inactive mode, off mode, delay start mode, and cycle finished mode.

Cycle finished mode means an active mode that provides continuous status display, intermittent tumbling, or air circulation following operation in active washing mode.

Delay start mode means an active mode in which activation of active washing mode is facilitated by a timer.

Energy efficiency ratio means the quotient of the weighted-average load size divided by the total clothes washer energy consumption per cycle, with such energy consumption expressed as the sum of:

(a) The machine electrical energy consumption;

(b) The hot water energy consumption;

(c) The energy required for removal of the remaining moisture in the wash load; and

(d) The combined low-power mode energy consumption.

Energy test cycle means the complete set of wash/rinse temperature selections required for testing, as determined according to section 2.12 of this appendix.

Fixed water fill control system means a clothes washer water fill control system that automatically terminates the fill when the water reaches a pre-defined level that is not based on the size or weight of the clothes load placed in the clothes container, without allowing or requiring the user to determine or select the water fill level.

Inactive mode means a standby mode that facilitates the activation of active mode by remote switch (including remote control), internal sensor, or timer, or that provides continuous status display.

Load usage factor means the percentage of the total number of wash loads that a user would wash a particular size (weight) load.

Lot means a quantity of cloth that has been manufactured with the same batches of cotton and polyester during one continuous process.

Manual water fill control system means a clothes washer water fill control system that requires the user to determine or select the water fill level.

Non-user-adjustable adaptive water fill control system means a clothes washer water fill control system that is capable of automatically adjusting the water fill level based on the size or weight of the clothes load placed in the clothes container.

Normal cycle means the cycle recommended by the manufacturer (considering manufacturer instructions, control panel labeling, and other markings on the clothes washer) for normal, regular, or typical use for washing up to a full load of normally soiled cotton clothing. For machines where multiple cycle settings are recommended by the manufacturer for normal, regular, or typical use for washing up to a full load of normally soiled cotton clothing, then the Normal cycle is the cycle selection that results in the lowest EER or AEER value.

Off mode means a mode in which the clothes washer is connected to a mains power source and is not providing any active or standby mode function, and where the mode may persist for an indefinite time.

Standby mode means any mode in which the clothes washer is connected to a mains power source and offers one or more of the following user oriented or protective functions that may persist for an indefinite time:

(a) Facilitating the activation of other modes (including activation or deactivation of active mode) by remote switch (including remote control), internal sensor, or timer;

(b) Continuous functions, including information or status displays (including clocks) or sensor-based functions.

A timer is a continuous clock function (which may or may not be associated with a display) that provides regular scheduled tasks (e.g., switching) and that operates on a continuous basis.

Temperature use factor means, for a particular wash/rinse temperature setting, the percentage of the total number of wash loads that an average user would wash with that setting.

User-adjustable adaptive water fill control system means a clothes washer fill control system that allows the user to adjust the amount of water that the machine provides, which is based on the size or weight of the clothes load placed in the clothes container.

Wash time means the wash portion of active washing mode, which begins when the cycle is initiated and includes the agitation or tumble time, which may be periodic or continuous during the wash portion of active washing mode.

Water efficiency ratio means the quotient of the weighted-average load size divided by the total weighted per-cycle water consumption for all wash cycles in gallons.

2. Testing Conditions and Instrumentation

2.1 Electrical energy supply.

2.1.1 Supply voltage and frequency. Maintain the electrical supply at the clothes washer terminal block within 2 percent of 120, 120/240, or 120/208Y volts as applicable to the particular terminal block wiring system and within 2 percent of the nameplate frequency as specified by the manufacturer. If the clothes washer has a dual voltage conversion capability, conduct test at the highest voltage specified by the manufacturer.

2.1.2 Supply voltage waveform. For the combined low-power mode testing, maintain the electrical supply voltage waveform indicated in Section 4, Paragraph 4.3.2 of IEC 62301. If the power measuring instrument used for testing is unable to measure and record the total harmonic content during the test measurement period, total harmonic content may be measured and recorded immediately before and after the test measurement period.

2.2 Supply water. Maintain the temperature of the hot water supply at the water inlets between 120 °F (48.9 °C) and 125 °F (51.7 °C), targeting the midpoint of the range. Maintain the temperature of the cold water supply at the water inlets between 55 °F (12.8 °C) and 60 °F (15.6 °C), targeting the midpoint of the range.

2.3 Water pressure. Maintain the static water pressure at the hot and cold water inlet connection of the clothes washer at 35 pounds per square inch gauge (psig) ± 2.5 psig (241.3 kPa ± 17.2 kPa) when the water is flowing.

2.4 Test room temperature. For all clothes washers, maintain the test room ambient air temperature at 75 ± 5 °F (23.9 ± 2.8 °C) for active mode testing and combined low-power mode testing. Do not use the test room ambient air temperature conditions specified in Section 4, Paragraph 4.2 of IEC 62301 for combined low-power mode testing.

2.5 Instrumentation. Perform all test measurements using the following instruments, as appropriate:

2.5.1 Weighing scales.

2.5.1.1 Weighing scale for test cloth. The scale used for weighing test cloth must have a resolution of no larger than 0.2 oz (5.7 g) and a maximum error no greater than 0.3 percent of the measured value.

2.5.1.2 Weighing scale for clothes container capacity measurement. The scale used for performing the clothes container capacity measurement must have a resolution no larger than 0.50 lbs (0.23 kg) and a maximum error no greater than 0.5 percent of the measured value.

2.5.2 Watt-hour meter. The watt-hour meter used to measure electrical energy consumption must have a resolution no larger than 1 Wh (3.6 kJ) and a maximum error no greater than 2 percent of the measured value for any demand greater than 50 Wh (180.0 kJ).

2.5.3 Watt meter. The watt meter used to measure combined low-power mode power consumption must comply with the requirements specified in Section 4, Paragraph 4.4 of IEC 62301. If the power measuring instrument used for testing is unable to measure and record the crest factor, power factor, or maximum current ratio during the test measurement period, the crest factor, power factor, and maximum current ratio may be measured and recorded immediately before and after the test measurement period.

2.5.4 Water and air temperature measuring devices. The temperature devices used to measure water and air temperature must have an error no greater than ±1 °F (±0.6 °C) over the range being measured.

2.5.4.1 Non-reversible temperature indicator labels, adhered to the inside of the clothes container, may be used to confirm that an extra-hot wash temperature greater than or equal to 140 °F has been achieved during the wash cycle, under the following conditions. The label must remain waterproof, intact, and adhered to the wash drum throughout an entire wash cycle; provide consistent maximum temperature readings; and provide repeatable temperature indications sufficient to demonstrate that a wash temperature of greater than or equal to 140 °F has been achieved. The label must have been verified to consistently indicate temperature measurements with an accuracy of ±1 °F. If using a temperature indicator label to test a front-loading clothes washer, adhere the label along the interior surface of the clothes container drum, midway between the front and the back of the drum, adjacent to one of the baffles. If using a temperature indicator label to test a top-loading clothes washer, adhere the label along the interior surface of the clothes container drum, on the vertical portion of the sidewall, as close to the bottom of the container as possible.

2.5.4.2 Submersible temperature loggers placed inside the wash drum may be used to confirm that an extra-hot wash temperature greater than or equal to 140 °F has been achieved during the wash cycle, under the following conditions. The submersible temperature logger must have a time resolution of at least 1 data point every 5 seconds and a temperature measurement accuracy of ±1 °F. Due to the potential for a waterproof capsule to provide a thermal insulating effect, failure to measure a temperature of 140 °F does not necessarily indicate the lack of an extra-hot wash temperature. However, such a result would not be conclusive due to the lack of verification of the water temperature requirement, in which case an alternative method must be used to confirm that an extra-hot wash temperature greater than or equal to 140 °F has been achieved during the wash cycle.

2.5.5 Water meter. A water meter must be installed in both the hot and cold water lines to measure water flow and/or water consumption. The water meters must have a resolution no larger than 0.1 gallons (0.4 liters) and a maximum error no greater than 2 percent for the water flow rates being measured. If the volume of hot water for any individual cycle within the energy test cycle is less than 0.1 gallons (0.4 liters), the hot water meter must have a resolution no larger than 0.01 gallons (0.04 liters).

2.5.6 Water pressure gauge. A water pressure gauge must be installed in both the hot and cold water lines to measure water pressure. The water pressure gauges must have a resolution of 1 pound per square inch gauge (psig) (6.9 kPa) and a maximum error no greater than 5 percent of any measured value.

2.6 Bone-dryer. The dryer used for drying the cloth to bone-dry must heat the test cloth load above 210 °F (99 °C).

2.7 Test cloths. The test cloth material and dimensions must conform to the specifications in appendix J3 to this subpart. The energy test cloth and the energy stuffer cloths must be clean and must not be used for more than 60 test runs (after preconditioning as specified in section 5 of appendix J3 to this subpart). All energy test cloth must be permanently marked identifying the lot number of the material. Mixed lots of material must not be used for testing a clothes washer. The moisture absorption and retention must be evaluated for each new lot of test cloth using the standard extractor Remaining Moisture Content (RMC) procedure specified in appendix J3 to this subpart.

2.8 Test Loads.

2.8.1 Test load sizes. Create small and large test loads as defined in Table 5.1 of this appendix based on the clothes container capacity as measured in section 3.1 of this appendix. Record the bone-dry weight for each test load.

2.8.2 Test load composition. Test loads must consist primarily of energy test cloths and no more than five energy stuffer cloths per load to achieve the proper weight.

2.9 Preparation and loading of test loads. Use the following procedures to prepare and load each test load for testing in section 3 of this appendix.

2.9.1 Test loads for energy and water consumption measurements must be bone-dry prior to the first cycle of the test, and dried to a maximum of 104 percent of bone-dry weight for subsequent testing.

2.9.2 Prepare the energy test cloths for loading by grasping them in the center, lifting, and shaking them to hang loosely, as illustrated in Figure 2.9.2 of this appendix.

For all clothes washers, follow any manufacturer loading instructions provided to the user regarding the placement of clothing within the clothes container. In the absence of any manufacturer instructions regarding the placement of clothing within the clothes container, the following loading instructions apply.

2.9.2.1 To load the energy test cloths in a top-loading clothes washer, arrange the cloths circumferentially around the axis of rotation of the clothes container, using alternating lengthwise orientations for adjacent pieces of cloth. Complete each cloth layer across its horizontal plane within the clothes container before adding a new layer. Figure 2.9.2.1 of this appendix illustrates the correct loading technique for a vertical-axis clothes washer.

2.9.2.2 To load the energy test cloths in a front-loading clothes washer, grasp each test cloth in the center as indicted in section 2.9.2 of this appendix, and then place each cloth into the clothes container prior to activating the clothes washer.

2.10 Clothes washer installation. Install the clothes washer in accordance with manufacturer's instructions.

2.10.1 Water inlet connections. If the clothes washer has 2 water inlets, connect the inlets to the hot water and cold water supplies, in accordance with the manufacturer's instructions. If the clothes washer has only 1 water inlet, connect the inlet to the cold water supply, in accordance with the manufacturer's instructions. Use the water inlet hoses provided with the clothes washer; otherwise use commercially available water inlet hoses, not to exceed 72 inches in length, in accordance with manufacturer's instructions.

2.10.2 Low-power mode testing. For combined low-power mode testing, install the clothes washer in accordance with Section 5, Paragraph 5.2 of IEC 62301, disregarding the provisions regarding batteries and the determination, classification, and testing of relevant modes.

2.11 Clothes washer pre-conditioning. If the clothes washer has not been filled with water in the preceding 96 hours, or if it has not been in the test room at the specified ambient conditions for 8 hours, pre-condition it by running it through a cold rinse cycle and then draining it to ensure that the hose, pump, and sump are filled with water.

2.12 Determining the energy test cycle.

2.12.1 Automatic clothes washers. To determine the energy test cycle, evaluate the wash/rinse temperature selection flowcharts in the order in which they are presented in this section. Use the large load size to evaluate each flowchart. The determination of the energy test cycle must take into consideration all cycle settings available to the end user, including any cycle selections or cycle modifications provided by the manufacturer via software or firmware updates to the product, for the basic model under test. The energy test cycle does not include any cycle that is recommended by the manufacturer exclusively for cleaning, deodorizing, or sanitizing the clothes washer.

2.12.2. Semi-automatic clothes washers. The energy test cycle for semi-automatic clothes washers includes only the Cold Wash/Cold Rinse (“Cold”) test cycle. Energy and water use for all other wash/rinse temperature combinations are calculated numerically in section 3.4.2 of this appendix.

3. Test Measurements

3.1 Clothes container capacity. Measure the entire volume that a clothes load could occupy within the clothes container during active mode washer operation according to the following procedures:

3.1.1 Place the clothes washer in such a position that the uppermost edge of the clothes container opening is leveled horizontally, so that the container will hold the maximum amount of water. For front-loading clothes washers, the door seal and shipping bolts or other forms of bracing hardware to support the wash drum during shipping must remain in place during the capacity measurement. If the design of a front-loading clothes washer does not include shipping bolts or other forms of bracing hardware to support the wash drum during shipping, a laboratory may support the wash drum by other means, including temporary bracing or support beams. Any temporary bracing or support beams must keep the wash drum in a fixed position, relative to the geometry of the door and door seal components, that is representative of the position of the wash drum during normal operation. The method used must avoid damage to the unit that would affect the results of the energy and water testing. For a front-loading clothes washer that does not include shipping bolts or other forms of bracing hardware to support the wash drum during shipping, the laboratory must fully document the alternative method used to support the wash drum during capacity measurement, include such documentation in the final test report, and pursuant to § 429.71 of this chapter, the manufacturer must retain such documentation as part its test records.

3.1.2 Line the inside of the clothes container with a 2 mil thickness (0.051 mm) plastic bag. All clothes washer components that occupy space within the clothes container and that are recommended for use during a wash cycle must be in place and must be lined with a 2 mil thickness (0.051 mm) plastic bag to prevent water from entering any void space.

3.1.3 Record the total weight of the machine before adding water.

3.1.4 Fill the clothes container manually with either 60 °F ± 5 °F (15.6 °C ± 2.8 °C) or 100 °F ± 10 °F (37.8 °C ± 5.5 °C) water, with the door open. For a top-loading vertical-axis clothes washer, fill the clothes container to the uppermost edge of the rotating portion, including any balance ring. Figure 3.1.4.1 of this appendix illustrates the maximum fill level for top-loading clothes washers.

For a front-loading horizontal-axis clothes washer, fill the clothes container to the highest point of contact between the door and the door gasket. If any portion of the door or gasket would occupy the measured volume space when the door is closed, exclude from the measurement the volume that the door or gasket portion would occupy. For a front-loading horizontal-axis clothes washer with a concave door shape, include any additional volume above the plane defined by the highest point of contact between the door and the door gasket, if that area can be occupied by clothing during washer operation. For a top-loading horizontal-axis clothes washer, include any additional volume above the plane of the door hinge that clothing could occupy during washer operation. Figure 3.1.4.2 of this appendix illustrates the maximum fill volumes for all horizontal-axis clothes washer types.

For all clothes washers, exclude any volume that cannot be occupied by the clothing load during operation.

3.1.5 Measure and record the weight of water, W, in pounds.

3.1.6 Calculate the clothes container capacity as follows:

C = W/d Where: C = Capacity in cubic feet (liters). W = Mass of water in pounds (kilograms). d = Density of water (62.0 lbs/ft 3 for 100 °F (993 kg/m 3 for 37.8 °C) or 62.3 lbs/ft 3 for 60 °F (998 kg/m 3 for 15.6 °C)).

3.1.7 Calculate the clothes container capacity, C, to the nearest 0.01 cubic foot for the purpose of determining test load sizes per Table 5.1 of this appendix and for all subsequent calculations that include the clothes container capacity.

3.2 Cycle settings.

3.2.1 Wash/rinse temperature selection. For automatic clothes washers, set the wash/rinse temperature selection control to obtain the desired wash/rinse temperature selection within the energy test cycle.

3.2.2 Wash time setting.

3.2.2.1 If the cycle under test offers a range of wash time settings, the wash time setting shall be the higher of either the minimum or 70 percent of the maximum wash time available for the wash cycle under test, regardless of the labeling of suggested dial locations. If 70 percent of the maximum wash time is not available on a dial with a discrete number of wash time settings, choose the next-highest setting greater than 70 percent.

3.2.2.2 If the clothes washer is equipped with an electromechanical dial or timer controlling wash time that rotates in both directions, reset the dial to the minimum wash time and then turn it in the direction of increasing wash time to reach the appropriate setting. If the appropriate setting is passed, return the dial to the minimum wash time and then turn in the direction of increasing wash time until the appropriate setting is reached.

3.2.3 Water fill level settings. The water fill level settings depend on the clothes washer's water fill control system, as determined in Table 3.2.3.

Table 3.2.3—Clothes Washer Water Fill Control Settings

Settings are
user-adjustable
Settings are not
user-adjustable
Water fill level unaffected by the size or weight of the clothing loadManual water fillFixed water fill. Water fill level is determined automatically by the clothes washer based on the size and weight of the clothing loadUser-adjustable adaptive water fillNon-user-adjustable adaptive water fill.

3.2.3.1 Clothes washers with a manual water fill control system. For the large test load size, set the water fill level selector to the maximum water fill level setting available for the wash cycle under test. If the water fill level selector has two settings available for the wash cycle under test, for the small test load size, select the minimum water fill level setting available for the wash cycle under test.

If the water fill level selector has more than two settings available for the wash cycle under test, for the small test load size, select the second-lowest water fill level setting.

3.2.3.2 Clothes washers with a fixed water fill control system. The water level is automatically determined by the water fill control system.

3.2.3.3 Clothes washers with a user-adjustable adaptive water fill control system. For the large test load size, set the water fill selector to the setting that uses the most water. For the small test load size, set the water fill selector to the setting that uses the least water.

3.2.3.4 Clothes washers with a non-user-adjustable adaptive water fill control system. The water level is automatically determined by the water fill control system.

3.2.3.5 Clothes washers with multiple water fill control systems. If a clothes washer allows user selection among multiple water fill control systems, test all water fill control systems and, for each one, calculate the energy consumption (HET, MET, DET, and ETLP) and water consumption (QT) values as set forth in section 4 of this appendix. Then, calculate the average of the tested values (one from each water fill control system) for each variable (HET, MET, DET, ETLP, and QT) and use the average value for each variable in the final calculations in section 4 of this appendix.

3.2.4 Manufacturer default settings. For clothes washers with electronic control systems, use the manufacturer default settings for any cycle selections, except for (1) the temperature selection, (2) the wash water fill levels, or (3) network settings. If the clothes washer has network capabilities, the network settings must be disabled throughout testing if such settings can be disabled by the end-user and the product's user manual provides instructions on how to do so. For all other cycle selections, the manufacturer default settings must be used for wash conditions such as agitation/tumble operation, soil level, spin speed, wash times, rinse times, optional rinse settings, water heating time for water heating clothes washers, and all other wash parameters or optional features applicable to that wash cycle. Any optional wash cycle feature or setting (other than wash/rinse temperature, water fill level selection, or network settings on clothes washers with network capabilities) that is activated by default on the wash cycle under test must be included for testing unless the manufacturer instructions recommend not selecting this option, or recommend selecting a different option, for washing normally soiled cotton clothing. For clothes washers with control panels containing mechanical switches or dials, any optional settings, except for the temperature selection or the wash water fill levels, must be in the position recommended by the manufacturer for washing normally soiled cotton clothing. If the manufacturer instructions do not recommend a particular switch or dial position to be used for washing normally soiled cotton clothing, the setting switch or dial must remain in its as-shipped position.

3.2.5 For each wash cycle tested, include the entire active washing mode and exclude any delay start or cycle finished modes.

3.2.6 Anomalous Test Cycles. If during a wash cycle the clothes washer: (a) Signals to the user by means of a visual or audio alert that an out-of-balance condition has been detected; or (b) terminates prematurely and thus does not include the agitation/tumble operation, spin speed(s), wash times, and rinse times applicable to the wash cycle under test, discard the test data and repeat the wash cycle. Document in the test report the rejection of data from any wash cycle during testing and the reason for the rejection.

3.3 Test cycles for automatic clothes washers. Perform testing on each wash/rinse temperature selection available in the energy test cycle as defined in section 2.12.1 of this appendix. Test each load size as defined in section 2.8 of this appendix with its associated water fill level defined in section 3.2.3 of this appendix. Assign the bone-dry weight according to the value measured in section 2.8 of this appendix. Place the test load in the clothes washer and initiate the cycle under test. Measure the values for hot water consumption, cold water consumption, electrical energy consumption, and cycle time for the complete cycle. Record the weight of the test load immediately after completion of the cycle. Table 3.3 of this appendix provides the symbol definitions for each measured value.

Table 3.3—Symbol Definitions of Measured Values for Automatic Clothes Washer Test Cycles

Wash/rinse
temperature
selection
Load size Bone-dry weight Hot water Cold water Electrical
energy
Cycle time Cycle
complete
weight
Extra-Hot/ColdLargeWIxLHxLCxLExLTxLWCxLSmallWIxSHxSCxSExSTxSWCxSHot/ColdLargeWIhLHhLChLEhLThLWChLSmallWIhSHhSChSEhSThSWChSWarm/Cold *LargeWIwLHwLCwLEwLTwLWCwLSmallWIwSHwSCwSEwSTwSWCwSWarm/Warm *LargeWIwwLHwwLCwwLEwwLTwwLWCwwLSmallWIwwSHwwSCwwSEwwSTwwSWCwwSCold/ColdLargeWIcLHcLCcLEcLTcLWCcLSmallWIcSHcSCcSEcSTcSWCcS

* If two cycles are tested to represent the Warm/Cold selection or the Warm/Warm selection, calculate the average of the two tested cycles and use that value for all further calculations.

3.4 Test cycles for semi-automatic clothes washers.

3.4.1 Test Measurements. Perform testing on each wash/rinse temperature selection available in the energy test cycle as defined in section 2.12.2 of this appendix. Test each load size as defined in section 2.8 of this appendix with the associated water fill level defined in section 3.2.3 of this appendix. Assign the bone-dry weight according to the value measured in section 2.8 of this appendix. Place the test load in the clothes washer and initiate the cycle under test. Measure the values for cold water consumption, electrical energy consumption, and cycle time for the complete cycle. Record the weight of the test load immediately after completion of the cycle. Table 3.4.1 of this appendix provides symbol definitions for each measured value for the Cold temperature selection.

Table 3.4.1—Symbol Definitions of Measured Values for Semi-Automatic Clothes Washer Test Cycles

Temperature selection Load size Bone-dry
weight
Hot water Cold water Electrical
energy
Cycle time Cycle
complete
weight
ColdLargeWIcLnot measuredCcLEcLTcLWCcLSmallWIcSnot measuredCcSEcSTcSWCcS

3.4.2 Calculation of Hot and Warm measured values. In lieu of testing, the measured values for the Hot and Warm cycles are calculated based on the measured values for the Cold cycle, as defined in section 3.4.1 of this appendix. Table 3.4.2 of this appendix provides the symbol definitions and calculations for each value for the Hot and Warm temperature selections.

Table 3.4.2—Symbol Definitions and Calculation of Measured Values for Semi-Automatic Clothes Washer Test Cycles

Temperature selection Load Size Bone-Dry
weight
Hot water Cold water Electrical energy Cycle time Cycle
complete
weight
HotLargeWIhL = WIcLHhL = CcLEhL = EcLThL = TcLWChL = WCcLSmallWIhS = WIcSHhS = CcSEhS = EcSThS = TcSWChS = WCcSWarmLargeWIwL = WIcLHwL = CcL ÷ 2CwL = CcL ÷ 2EwL = EcLTwL = TcLWCwL = WCcLSmallWIwS = WIcSHwS = CcS ÷ 2CwS = CcS ÷ 2EwS = EcSTwS = TcSWCwS = WCcS

3.5 Combined low-power mode power. Connect the clothes washer to a watt meter as specified in section 2.5.3 of this appendix. Establish the testing conditions set forth in sections 2.1, 2.4, and 2.10.2 of this appendix.

3.5.1 Perform combined low-power mode testing after completion of an active mode wash cycle included as part of the energy test cycle; after removing the test load; without changing the control panel settings used for the active mode wash cycle; with the door closed; and without disconnecting the electrical energy supply to the clothes washer between completion of the active mode wash cycle and the start of combined low-power mode testing.

3.5.2 For a clothes washer that takes some time to automatically enter a stable inactive mode or off mode state from a higher power state as discussed in Section 5, Paragraph 5.1, note 1 of IEC 62301, allow sufficient time for the clothes washer to automatically reach the default inactive/off mode state before proceeding with the test measurement.

3.5.3 Once the stable inactive/off mode state has been reached, measure and record the default inactive/off mode power, Pdefault, in watts, following the test procedure for the sampling method specified in Section 5, Paragraph 5.3.2 of IEC 62301.

3.5.4 For a clothes washer with a switch, dial, or button that can be optionally selected by the end user to achieve a lower-power inactive/off mode state than the default inactive/off mode state measured in section 3.5.3 of this appendix, after performing the measurement in section 3.5.3 of this appendix, activate the switch, dial, or button to the position resulting in the lowest power consumption and repeat the measurement procedure described in section 3.5.3 of this appendix. Measure and record the lowest-power inactive/off mode power, Plowest, in Watts.

3.6 Energy consumption for the purpose of determining the cycle selection(s) to be included in the energy test cycle. This section is implemented only in cases where the energy test cycle flowcharts in section 2.12.1 of this appendix require the determination of the wash/rinse temperature selection with the highest energy consumption.

3.6.1 For the wash/rinse temperature selection being considered under this section, establish the testing conditions set forth in section 2 of this appendix. Select the applicable cycle selection and wash/rinse temperature selection. For all wash/rinse temperature selections, select the cycle settings as described in section 3.2 of this appendix.

3.6.2 Measure each wash cycle's electrical energy consumption (EL) and hot water consumption (HL). Calculate the total energy consumption for each cycle selection (ETL), as follows:

ETL = EL + (HL × T × K) Where: EL is the electrical energy consumption, expressed in kilowatt-hours per cycle. HL is the hot water consumption, expressed in gallons per cycle. T = nominal temperature rise = 65 °F (36.1 °C). K = Water specific heat in kilowatt-hours per gallon per degree F = 0.00240 kWh/gal − °F (0.00114 kWh/L − °C). 4. Calculation of Derived Results From Test Measurements

4.1 Hot water and machine electrical energy consumption of clothes washers.

4.1.1 Per-cycle temperature-weighted hot water consumption for all load sizes tested. Calculate the per-cycle temperature-weighted hot water consumption for the large test load size, VhL, and the small test load size, VhS, expressed in gallons per cycle (or liters per cycle) and defined as:

(a) VhL = [HxL × TUFX] + [HhL × TUFh] + [HwL × TUFw] + [HwwL × TUFww] + [HcL × TUFc] (b) VhS = [HxS × TUFX] + [HhS × TUFh] + [HwS × TUFw] + [HwwS × TUFww] + [HcS × TUFc] Where:

HxL, HhL, HwL, HwwL, HcL, HxS, HhS, HwS, HwwS, and HcS are the hot water consumption values, in gallons per-cycle (or liters per cycle) as measured in section 3.3 of this appendix for automatic clothes washers or section 3.4 of this appendix for semi-automatic clothes washers.

TUFX, TUFh, TUFw, TUFww, and TUFc are temperature use factors for Extra-Hot Wash/Cold Rinse, Hot Wash/Cold Rinse, Warm Wash/Cold Rinse, Warm Wash/Warm Rinse, and Cold Wash/Cold Rinse temperature selections, respectively, as defined in Table 4.1.1 of this appendix.

Table 4.1.1—Temperature Use Factors

Wash/rinse temperature selections available in the energy test cycle Clothes washers with cold rinse only Clothes washers with both cold and warm rinse C/C H/C
C/C
H/C
W/C
C/C
*
XH/C
H/C
C/C
XH/C
H/C
W/C
C/C
H/C
W/C
W/W
C/C
XH/C
H/C
W/W
C/C
XH/C
H/C
W/C
W/W
C/C
TUFx (Extra-Hot/Cold)0.140.050.140.05 TUFh (Hot/Cold)0.630.14** 0.490.090.14** 0.220.09 TUFw (Warm/Cold)0.490.490.220.22 TUFww (Warm/Warm)0.270.270.27 TUFc (Cold/Cold)1.000.370.370.370.370.370.370.37

* This column applies to all semi-automatic clothes washers.

** On clothes washers with only two wash temperature selections <140 °F, the higher of the two wash temperatures is classified as a Hot Wash/Cold Rinse, in accordance with the wash/rinse temperature definitions within the energy test cycle.

4.1.2 Total per-cycle hot water energy consumption for all load sizes tested. Calculate the total per-cycle hot water energy consumption for the large test load size, HEL, and the small test load size, HES, expressed in kilowatt-hours per cycle and defined as:

(a) HEL = [VhL × T × K] = Total energy when the large test load is tested. (b) HES = [VhS × T × K] = Total energy when the small test load is tested. Where: VhL and VhS are defined in section 4.1.1 of this appendix. T = Temperature rise = 65 °F (36.1 °C). K = Water specific heat in kilowatt-hours per gallon per degree F = 0.00240 kWh/gal − °F (0.00114 kWh/L − °C).

4.1.3 Total weighted per-cycle hot water energy consumption. Calculate the total weighted per-cycle hot water energy consumption, HET, expressed in kilowatt-hours per cycle and defined as:

HET = [HEL × LUFL] + [HES × LUFS] Where: HEL and HES are defined in section 4.1.2 of this appendix. LUFL = Load usage factor for the large test load = 0.5. LUFS = Load usage factor for the small test load = 0.5.

4.1.4 Total per-cycle hot water energy consumption using gas-heated or oil-heated water, for product labeling requirements. Calculate for the energy test cycle the per-cycle hot water consumption, HETG, using gas-heated or oil-heated water, expressed in Btu per cycle (or megajoules per cycle) and defined as:

HETG = HET × 1/e × 3412 Btu/kWh or HETG = HET × 1/e × 3.6 MJ/kWh. Where: e = Nominal gas or oil water heater efficiency = 0.75. HET = As defined in section 4.1.3 of this appendix.

4.1.5 Per-cycle machine electrical energy consumption for all load sizes tested. Calculate the total per-cycle machine electrical energy consumption for the large test load size, MEL, and the small test load size, MES, expressed in kilowatt-hours per cycle and defined as:

(a) MEL = [ExL × TUFX] + [EhL × TUFh] + [EwL × TUFw] + [EwwL × TUFww] + [EcL × TUFc] (b) MES = [ExS × TUFX] + [EhS × TUFh] + [EwS × TUFw] + [EwwS × TUFww] + [EcS × TUFc] Where: ExL, EhL, EwL, EwwL, EcL, ExS, EhS, EwS, EwwS, and EcS are the electrical energy consumption values, in kilowatt-hours per cycle as measured in section 3.3 of this appendix for automatic clothes washers or section 3.4 of this appendix for semi-automatic clothes washers. TUFX, TUFh, TUFw, TUFww, and TUFc are defined in Table 4.1.1 of this appendix.

4.1.6 Total weighted per-cycle machine electrical energy consumption. Calculate the total weighted per-cycle machine electrical energy consumption, MET, expressed in kilowatt-hours per cycle and defined as:

MET = [MEL × LUFL] + [MES × LUFS] Where: MEL and MES are defined in section 4.1.5 of this appendix. LUFL and LUFS are defined in section 4.1.3 of this appendix.

4.2 Water consumption of clothes washers.

4.2.1 Per cycle total water consumption for each large load size tested. Calculate the per-cycle total water consumption of the large test load for the Extra-Hot Wash/Cold Rinse cycle, QxL, Hot Wash/Cold Rinse cycle, QhL, Warm Wash/Cold Rinse cycle, QwL, Warm Wash/Warm Rinse cycle, QwwL, and Cold Wash/Cold Rinse cycle, QcL, defined as:

(a) QxL = HxL + CxL (b) QhL = HhL + ChL (c) QwL = HwL + CwL (d) QwwL = HwwL + CwwL (e) QcL = HcL + CcL Where: HxL, HhL, HwL, HwwL, HcL, CxL, ChL, CwL, CwwL, and CcL are defined in section 3.3 of this appendix for automatic clothes washers or section 3.4 of this appendix for semi-automatic clothes washers.

4.2.2 Per cycle total water consumption for each small load size tested. Calculate the per-cycle total water consumption of the small test load for the Extra-Hot Wash/Cold Rinse cycle, QxS, Hot Wash/Cold Rinse cycle, QhS, Warm Wash/Cold Rinse cycle, QwS, Warm Wash/Warm Rinse cycle, QwwS, and Cold Wash/Cold Rinse cycle, QcS, defined as:

(a) QxS = HxS + CxS (b) QhS = HhS + ChS (c) QwS = HwS + CwS (d) QwwS = HwwS + CwwS (e) QcS = HcS + CcS Where: HxS, HhS, HwS, HwwS, HcS, CxS, ChS, CwS, CwwS, and CcS are defined in section 3.3 of this appendix for automatic clothes washers or section 3.4 of this appendix for semi-automatic clothes washers.

4.2.3 Per-cycle total water consumption for all load sizes tested. Calculate the total per-cycle water consumption for the large test load size, QL, and the small test load size, QS, expressed in gallons per cycle (or liters per cycle) and defined as:

(a) QL = [QxL × TUFx] + [QhL × TUFh] + [QwL × TUFw] + [QwwL × TUFww] + [QcL × TUFc] (b) QS = [QxS × TUFx] + [QhS × TUFh] + [QwS × TUFw] + [QwwS × TUFww] + [QcS × TUFc] Where: QxL, QhL, QwL, QwwL, and QcL are defined in section 4.2.1 of this appendix. QxS, QhS, QwS, QwwS, and QcS are defined in section 4.2.2 of this appendix. TUFx, TUFh, TUFw, TUFww, and TUFc are defined in Table 4.1.1 of this appendix.

4.2.4 Total weighted per-cycle water consumption. Calculate the total per-cycle water consumption, QT, expressed in gallons per cycle (or liters per cycle) and defined as:

QT = [QL × LUFL] + [QS × LUFS] Where: QL and QS are defined in section 4.2.3 of this appendix. LUFL and LUFS are defined in section 4.1.3 of this appendix.

4.3 Remaining moisture content (RMC).

4.3.1 Per cycle remaining moisture content for each large load size tested. Calculate the per-cycle remaining moisture content of the large test load for the Extra-Hot Wash/Cold Rinse cycle, RMCxL, Hot Wash/Cold Rinse cycle, RMChL, Warm Wash/Cold Rinse cycle, RMCwL, Warm Wash/Warm Rinse cycle, RMCwwL, and Cold Wash/Cold Rinse cycle, RMCcL, defined as:

(a) RMCxL = (WCxL − WIxL)/WIxL (b) RMChL = (WChL − WIhL)/WIhL (c) RMCwL = (WCwL − WIwL)/WIwL (d) RMCwwL = (WCwwL − WIwwL)/WIwwL (e) RMCcL = (WCcL − WIcL)/WIcL Where: WCxL, WChL, WCwL, WCwwL, WCcL, WIxL, WIhL, WIwL, WIwwL, and WIcL are the bone-dry weights and cycle completion weights as measured in section 3.3 of this appendix for automatic clothes washers or section 3.4 of this appendix for semi-automatic clothes washers.

4.3.2 Per cycle remaining moisture content for each small load size tested. Calculate the per-cycle remaining moisture content of the small test load for the Extra-Hot Wash/Cold Rinse cycle, RMCxS, Hot Wash/Cold Rinse cycle, RMChS, Warm Wash/Cold Rinse cycle, RMCwS, Warm Wash/Warm Rinse cycle, RMCwwS, and Cold Wash/Cold Rinse cycle, RMCcS, defined as:

(a) RMCxS = (WCxS—WIxS)/WIxS (b) RMChS = (WChS—WIhS)/WIhS (c) RMCwS = (WCwS—WIwS)/WIwS (d) RMCwwS = (WCwwS—WIwwS)/WIwwS (e) RMCcS = (WCcS—WIcS)/WIcS Where: WCxS, WChS, WCwS, WCwwS, WCcS, WIxS, WIhS, WIwS, WIwwS, and WIcS are the bone-dry weights and cycle completion weights as measured in section 3.3 of this appendix for automatic clothes washers or section 3.4 of this appendix for semi-automatic clothes washers.

4.3.3 Per-cycle remaining moisture content for all load sizes tested. Calculate the per-cycle temperature-weighted remaining moisture content for the large test load size, RMCL, and the small test load size, RMCS, defined as:

(a) RMCL = [RMCxL × TUFX] + [RMChL × TUFh] + [RMCwL × TUFw] + [RMCwwL × TUFww] + [RMCcL × TUFc] (b) RMCS = [RMCxS × TUFX] + [RMChS × TUFh] + [RMCwS × TUFw] + [RMCwwS × TUFww] + [RMCcS × TUFc] Where: RMCxL, RMChL, RMCwL, RMCwwL, and RMCcL are defined in section 4.3.1 of this appendix. RMCxS, RMChS, RMCwS, RMCwwS, and RMCcS are defined in section 4.3.2 of this appendix. TUFX, TUFh, TUFw, TUFww, and TUFc are defined in Table 4.1.1 of this appendix.

4.3.4 Weighted per-cycle remaining moisture content. Calculate the weighted per-cycle remaining moisture content, RMCT, defined as:

RMCT = [RMCL × LUFL] + [RMCS × LUFS] Where: RMCL and RMCS are defined in section 4.3.3 of this appendix. LUFL and LUFS are defined in section 4.1.3 of this appendix.

4.3.5 Apply the RMC correction curve as described in section 9 of appendix J3 to this subpart to calculate the corrected remaining moisture content, RMCcorr, expressed as a percentage as follows:

RMCcorr = (A × RMCT + B) × 100% Where: A and B are the coefficients of the RMC correction curve as defined in section 8.7 of appendix J3 to this subpart. RMCT = As defined in section 4.3.4 of this appendix.

4.4 Per-cycle energy consumption for removal of moisture from test load. Calculate the per-cycle energy required to remove the remaining moisture of the test load, DET, expressed in kilowatt-hours per cycle and defined as:

DET = [(LUFL × Large test load weight) + (LUFS × Small test load weight)] × (RMCcorr−2%) × (DEF) × (DUF) Where: LUFL and LUFS are defined in section 4.1.3 of this appendix. Large and small test load weights are defined in Table 5.1 of this appendix. RMCcorr = As defined in section 4.3.5 of this appendix. DEF = Nominal energy required for a clothes dryer to remove moisture from clothes = 0.5 kWh/lb (1.1 kWh/kg). DUF = Dryer usage factor, percentage of washer loads dried in a clothes dryer = 0.91.

4.5 Cycle time.

4.5.1 Per-cycle temperature-weighted cycle time for all load sizes tested. Calculate the per-cycle temperature-weighted cycle time for the large test load size, TL, and the small test load size, TS, expressed in minutes, and defined as:

(a) TL = [TxL × TUFX] + [ThL × TUFh] + [TwL × TUFw] + [TwwL × TUFww] + [TcL × TUFc] (b) TS = [TxS × TUFX] + [ThS × TUFh] + [TwS × TUFw] + [TwwS × TUFww] + [TcS × TUFc] Where: TxL, ThL, TwL, TwwL, TcL, TxS, ThS, TwS, TwwS, and TcS are the cycle time values, in minutes as measured in section 3.3 of this appendix for automatic clothes washers or section 3.4 of this appendix for semi-automatic clothes washers. TUFX, TUFh, TUFw, TUFww, and TUFc are temperature use factors for Extra-Hot Wash/Cold Rinse, Hot Wash/Cold Rinse, Warm Wash/Cold Rinse, Warm Wash/Warm Rinse, and Cold Wash/Cold Rinse temperature selections, respectively, as defined in Table 4.1.1 of this appendix.

4.5.2 Total weighted per-cycle cycle time. Calculate the total weighted per-cycle cycle time, TT, expressed in minutes, rounded to the nearest minute, and defined as:

TT = [TL × LUFL] + [TS × LUFS] Where: TL and TS are defined in section 4.5.1 of this appendix. LUFL and LUFS are defined in section 4.1.3 of this appendix.

4.6 Combined low-power mode energy consumption.

4.6.1 Annual hours in default inactive/off mode. Calculate the annual hours spent in default inactive/off mode, Sdefault, expressed in hours and defined as:

Sdefault = [8,760−(234 × TT/60)]/N Where: TT = As defined in section 4.5.2 of this appendix, in minutes. N = Number of inactive/off modes, defined as 1 if no optional lowest-power inactive/off mode is available; otherwise 2. 8,760 = Total number of hours in a year. 234 = Representative average number of clothes washer cycles in a year. 60 = Conversion from minutes to hours.

4.6.2 Per-cycle combined low-power mode energy consumption. Calculate the per-cycle combined low-power mode energy consumption, ETLP, expressed in kilowatt-hours per cycle and defined as:

ETLP = [(Pdefault × Sdefault) + (Plowest × Slowest)] × Kp/234 Where: Pdefault = Default inactive/off mode power, in watts, as measured in section 3.5.3 of this appendix. Plowest = Lowest-power inactive/off mode power, in watts, as measured in section 3.5.4 of this appendix for clothes washers with a switch, dial, or button that can be optionally selected by the end user to achieve a lower-power inactive/off mode than the default inactive/off mode; otherwise, Plowest = 0. Sdefault = Annual hours in default inactive/off mode, as calculated in section 4.6.1 of this appendix. Slowest = Annual hours in lowest-power inactive/off mode, defined as 0 if no optional lowest-power inactive/off mode is available; otherwise equal to Sdefault, as calculated in section 4.6.1 of this appendix. Kp = Conversion factor of watt-hours to kilowatt-hours = 0.001. 234 = Representative average number of clothes washer cycles in a year.

4.7 Water efficiency ratio. Calculate the water efficiency ratio, WER, expressed in pounds per gallon per cycle (or kilograms per liter per cycle), as:

WER = [(LUFL × Large test load weight) + (LUFS × Small test load weight)]/QT Where: LUFL and LUFS are defined in section 4.1.3 of this appendix. Large and small test load weights are defined in Table 5.1 of this appendix. QT = As defined in section 4.2.4 of this appendix.

4.8 Active-mode energy efficiency ratio. Calculate the active-mode energy efficiency ratio, AEER, expressed in pounds per kilowatt-hour per cycle (or kilograms per kilowatt-hour per cycle) and defined as:

AEER = [(LUFL × Large test load weight) + (LUFS × Small test load weight)]/(MET + HET + DET) Where: LUFL and LUFS are defined in section 4.1.3 of this appendix. Large and small test load weights are defined in Table 5.1 of this appendix. MET = As defined in section 4.1.6 of this appendix. HET = As defined in section 4.1.3 of this appendix. DET = As defined in section 4.4 of this appendix.

4.9 Energy efficiency ratio. Calculate the energy efficiency ratio, EER, expressed in pounds per kilowatt-hour per cycle (or kilograms per kilowatt-hour per cycle) and defined as:

EER = [(LUFL × Large test load weight) + (LUFS × Small test load weight)]/(MET + HET + DET + ETLP) Where: LUFL and LUFS are defined in section 4.1.3 of this appendix. Large and small test load weights are defined in Table 5.1 of this appendix. MET = As defined in section 4.1.6 of this appendix. HET = As defined in section 4.1.3 of this appendix. DET = As defined in section 4.4 of this appendix. ETLP = As defined in section 4.6.2 of this appendix. 5. Test Loads

Table 5.1—Test Load Sizes

Container volume Small load Large load cu. ft. liter lb kg lb kg ≥ < ≥ < 0.00-0.800.00-22.73.001.363.001.36 0.80-0.9022.7-25.53.101.413.351.52 0.90-1.0025.5-28.33.201.453.701.68 1.00-1.1028.3-31.13.301.504.001.81 1.10-1.2031.1-34.03.401.544.301.95 1.20-1.3034.0-36.83.451.564.602.09 1.30-1.4036.8-39.63.551.614.952.25 1.40-1.5039.6-42.53.651.665.252.38 1.50-1.6042.5-45.33.751.705.552.52 1.60-1.7045.3-48.13.801.725.852.65 1.70-1.8048.1-51.03.901.776.202.81 1.80-1.9051.0-53.84.001.816.502.95 1.90-2.0053.8-56.64.101.866.803.08 2.00-2.1056.6-59.54.201.917.103.22 2.10-2.2059.5-62.34.301.957.453.38 2.20-2.3062.3-65.14.351.977.753.52 2.30-2.4065.1-68.04.452.028.053.65 2.40-2.5068.0-70.84.552.068.353.79 2.50-2.6070.8-73.64.652.118.703.95 2.60-2.7073.6-76.54.702.139.004.08 2.70-2.8076.5-79.34.802.189.304.22 2.80-2.9079.3-82.14.902.229.604.35 2.90-3.0082.1-85.05.002.279.904.49 3.00-3.1085.0-87.85.102.3110.254.65 3.10-3.2087.8-90.65.202.3610.554.79 3.20-3.3090.6-93.45.252.3810.854.92 3.30-3.4093.4-96.35.352.4311.155.06 3.40-3.5096.3-99.15.452.4711.505.22 3.50-3.6099.1-101.95.552.5211.805.35 3.60-3.70101.9-104.85.652.5612.105.49 3.70-3.80104.8-107.65.702.5912.405.62 3.80-3.90107.6-110.45.802.6312.755.78 3.90-4.00110.4-113.35.902.6813.055.92 4.00-4.10113.3-116.16.002.7213.356.06 4.10-4.20116.1-118.96.102.7713.656.19 4.20-4.30118.9-121.86.152.7914.006.35 4.30-4.40121.8-124.66.252.8314.306.49 4.40-4.50124.6-127.46.352.8814.606.62 4.50-4.60127.4-130.36.452.9314.906.76 4.60-4.70130.3-133.16.552.9715.256.92 4.70-4.80133.1-135.96.602.9915.557.05 4.80-4.90135.9-138.86.703.0415.857.19 4.90-5.00138.8-141.66.803.0816.157.33 5.00-5.10141.6-144.46.903.1316.507.48 5.10-5.20144.4-147.27.003.1816.807.62 5.20-5.30147.2-150.17.053.2017.107.76 5.30-5.40150.1-152.97.153.2417.407.89 5.40-5.50152.9-155.77.253.2917.708.03 5.50-5.60155.7-158.67.353.3318.058.19 5.60-5.70158.6-161.47.453.3818.358.32 5.70-5.80161.4-164.27.503.4018.658.46 5.80-5.90164.2-167.17.603.4518.958.60 5.90-6.00167.1-169.97.703.4919.308.75 6.00-6.10169.9-172.77.803.5419.608.89 6.10-6.20172.7-175.67.903.5819.909.03 6.20-6.30175.6-178.47.953.6120.209.16 6.30-6.40178.4-181.28.053.6520.559.32 6.40-6.50181.2-184.18.153.7020.859.46 6.50-6.60184.1-186.98.253.7421.159.59 6.60-6.70186.9-189.78.303.7621.459.73 6.70-6.80189.7-192.68.403.8121.809.89 6.80-6.90192.6-195.48.503.8622.1010.02 6.90-7.00195.4-198.28.603.9022.4010.16 7.00-7.10198.2-201.08.703.9522.7010.30 7.10-7.20201.0-203.98.803.9923.0510.46 7.20-7.30203.9-206.78.854.0123.3510.59 7.30-7.40206.7-209.58.954.0623.6510.73 7.40-7.50209.5-212.49.054.1123.9510.86 7.50-7.60212.4-215.29.154.1524.3011.02 7.60-7.70215.2-218.09.254.2024.6011.16 7.70-7.80218.0-220.99.304.2224.9011.29 7.80-7.90220.9-223.79.404.2625.2011.43 7.90-8.00223.7-226.59.504.3125.5011.57

Notes: (1) All test load weights are bone-dry weights.

(2) Allowable tolerance on the test load weights is ±0.10 lbs (0.05 kg).

[87 FR 33381, June 1, 2022, as amended at 87 FR 78820, Dec. 23, 2022; 89 FR 84076, Oct. 21, 2024]

Appendix J1 - Appendix J1 to Subpart B of Part 430 [Reserved]

Appendix J2 - Appendix J2 to Subpart B of Part 430—Uniform Test Method for Measuring the Energy Consumption of Automatic and Semi-automatic Clothes Washers

Note 1 to appendix J2 to subpart B of part 430:

Manufacturers must use the results of testing under this appendix to determine compliance with the residential clothes washer standards provided at § 430.32(g)(1) and the commercial clothes washer standards provided at § 431.156(b).

Manufacturers must use the results of testing under Appendix J to this subpart to determine compliance with the residential clothes washer standards provided at § 430.32(g)(2) and for any amended commercial clothes washer standards provided at § 431.156 that are published after January 1, 2022.

Any representations related to energy or water consumption of residential or commercial clothes washers must be made in accordance with the appropriate appendix that applies (i.e., appendix J to this subpart or this appendix) when determining compliance with the relevant standard.

0. Incorporation by Reference

DOE incorporated by reference in § 430.3, the entire test standard for IEC 62301. However, only enumerated provisions of this standard are applicable to this appendix, as follows. In cases in which there is a conflict, the language of the test procedure in this appendix takes precedence over the referenced test standard.

0.1 IEC 62301:

(a) Section 4.2 as referenced in section 2.4 of this appendix;

(b) Section 4.3.2 as referenced in section 2.1.2 of this appendix;

(c) Section 4.4 as referenced in section 2.5.3 of this appendix;

(d) Section 5.1 as referenced in section 3.9.2 of this appendix;

(e) Section 5.2 as referenced in section 2.10 of this appendix; and

(f) Section 5.3.2 as referenced in section 3.9.3 of this appendix.

0.2 [Reserved]

1. Definitions

Active mode means a mode in which the clothes washer is connected to a mains power source, has been activated, and is performing one or more of the main functions of washing, soaking, tumbling, agitating, rinsing, and/or removing water from the clothing, or is involved in functions necessary for these main functions, such as admitting water into the washer or pumping water out of the washer. Active mode also includes delay start and cycle finished modes.

Active washing mode means a mode in which the clothes washer is performing any of the operations included in a complete cycle intended for washing a clothing load, including the main functions of washing, soaking, tumbling, agitating, rinsing, and/or removing water from the clothing.

Adaptive water fill control system means a clothes washer automatic water fill control system that is capable of automatically adjusting the water fill level based on the size or weight of the clothes load placed in the clothes container.

Automatic water fill control system means a clothes washer water fill control system that does not allow or require the user to determine or select the water fill level, and includes adaptive water fill control systems and fixed water fill control systems.

Bone-dry means a condition of a load of test cloth that has been dried in a dryer at maximum temperature for a minimum of 10 minutes, removed and weighed before cool down, and then dried again for 10 minute periods until the final weight change of the load is 1 percent or less.

Clothes container means the compartment within the clothes washer that holds the clothes during the operation of the machine.

Cold rinse means the coldest rinse temperature available on the machine, as indicated to the user on the clothes washer control panel.

Combined low-power mode means the aggregate of available modes other than active washing mode, including inactive mode, off mode, delay start mode, and cycle finished mode.

Cycle finished mode means an active mode that provides continuous status display, intermittent tumbling, or air circulation following operation in active washing mode.

Delay start mode means an active mode in which activation of active washing mode is facilitated by a timer.

Energy test cycle means the complete set of wash/rinse temperature selections required for testing, as determined according to section 2.12 of this appendix.

Fixed water fill control system means a clothes washer automatic water fill control system that automatically terminates the fill when the water reaches a pre-defined level that is not based on the size or weight of the clothes load placed in the clothes container, without allowing or requiring the user to determine or select the water fill level.

Inactive mode means a standby mode that facilitates the activation of active mode by remote switch (including remote control), internal sensor, or timer, or that provides continuous status display.

Integrated modified energy factor means the quotient of the cubic foot (or liter) capacity of the clothes container divided by the total clothes washer energy consumption per cycle, with such energy consumption expressed as the sum of:

(a) The machine electrical energy consumption;

(b) The hot water energy consumption;

(c) The energy required for removal of the remaining moisture in the wash load; and

(d) The combined low-power mode energy consumption.

Integrated water factor means the quotient of the total weighted per-cycle water consumption for all wash cycles in gallons divided by the cubic foot (or liter) capacity of the clothes washer.

Load usage factor means the percentage of the total number of wash loads that a user would wash a particular size (weight) load.

Lot means a quantity of cloth that has been manufactured with the same batches of cotton and polyester during one continuous process.

Manual water fill control system means a clothes washer water fill control system that requires the user to determine or select the water fill level.

Modified energy factor means the quotient of the cubic foot (or liter) capacity of the clothes container divided by the total clothes washer energy consumption per cycle, with such energy consumption expressed as the sum of the machine electrical energy consumption, the hot water energy consumption, and the energy required for removal of the remaining moisture in the wash load.

Non-water-heating clothes washer means a clothes washer that does not have an internal water heating device to generate hot water.

Normal cycle means the cycle recommended by the manufacturer (considering manufacturer instructions, control panel labeling, and other markings on the clothes washer) for normal, regular, or typical use for washing up to a full load of normally soiled cotton clothing. For machines where multiple cycle settings are recommended by the manufacturer for normal, regular, or typical use for washing up to a full load of normally soiled cotton clothing, then the Normal cycle is the cycle selection that results in the lowest IMEF or MEFJ2 value.

Off mode means a mode in which the clothes washer is connected to a mains power source and is not providing any active or standby mode function, and where the mode may persist for an indefinite time.

Standby mode means any mode in which the clothes washer is connected to a mains power source and offers one or more of the following user oriented or protective functions that may persist for an indefinite time:

(a) Facilitating the activation of other modes (including activation or deactivation of active mode) by remote switch (including remote control), internal sensor, or timer;

(b) Continuous functions, including information or status displays (including clocks) or sensor-based functions.

(c) A timer is a continuous clock function (which may or may not be associated with a display) that provides regular scheduled tasks (e.g., switching) and that operates on a continuous basis.

Temperature use factor means, for a particular wash/rinse temperature setting, the percentage of the total number of wash loads that an average user would wash with that setting.

User-adjustable adaptive water fill control system means a clothes washer fill control system that allows the user to adjust the amount of water that the machine provides, which is based on the size or weight of the clothes load placed in the clothes container.

Wash time means the wash portion of active washing mode, which begins when the cycle is initiated and includes the agitation or tumble time, which may be periodic or continuous during the wash portion of active washing mode.

Water factor means the quotient of the total weighted per-cycle water consumption for cold wash divided by the cubic foot (or liter) capacity of the clothes washer.

Water-heating clothes washer means a clothes washer where some or all of the hot water for clothes washing is generated by a water heating device internal to the clothes washer.

2. Testing Conditions and Instrumentation

2.1 Electrical energy supply.

2.1.1 Supply voltage and frequency. Maintain the electrical supply at the clothes washer terminal block within 2 percent of 120, 120/240, or 120/208Y volts as applicable to the particular terminal block wiring system and within 2 percent of the nameplate frequency as specified by the manufacturer. If the clothes washer has a dual voltage conversion capability, conduct test at the highest voltage specified by the manufacturer.

2.1.2 Supply voltage waveform. For the combined low-power mode testing, maintain the electrical supply voltage waveform indicated in Section 4, Paragraph 4.3.2 of IEC 62301. If the power measuring instrument used for testing is unable to measure and record the total harmonic content during the test measurement period, total harmonic content may be measured and recorded immediately before and after the test measurement period.

2.2 Supply water. Maintain the temperature of the hot water supply at the water inlets between 130 °F (54.4 °C) and 135 °F (57.2 °C), targeting the midpoint of the range. Maintain the temperature of the cold water supply at the water inlets between 55 °F (12.8 °C) and 60 °F (15.6 °C), targeting the midpoint of the range.

2.3 Water pressure. Maintain the static water pressure at the hot and cold water inlet connection of the clothes washer at 35 pounds per square inch gauge (psig) ± 2.5 psig (241.3 kPa ± 17.2 kPa) when the water is flowing.

2.4 Test room temperature. For all clothes washers, maintain the test room ambient air temperature at 75 ± 5 °F (23.9 ± 2.8 °C) for active mode testing and combined low-power mode testing. Do not use the test room ambient air temperature conditions specified in Section 4, Paragraph 4.2 of IEC 62301 for combined low-power mode testing.

2.5 Instrumentation. Perform all test measurements using the following instruments, as appropriate:

2.5.1 Weighing scales.

2.5.1.1 Weighing scale for test cloth. The scale used for weighing test cloth must have a resolution of no larger than 0.2 oz (5.7 g) and a maximum error no greater than 0.3 percent of the measured value.

2.5.1.2 Weighing scale for clothes container capacity measurement. The scale used for performing the clothes container capacity measurement must have a resolution no larger than 0.50 lbs (0.23 kg) and a maximum error no greater than 0.5 percent of the measured value.

2.5.2 Watt-hour meter. The watt-hour meter used to measure electrical energy consumption must have a resolution no larger than 1 Wh (3.6 kJ) and a maximum error no greater than 2 percent of the measured value for any demand greater than 50 Wh (180.0 kJ).

2.5.3 Watt meter. The watt meter used to measure combined low-power mode power consumption must comply with the requirements specified in Section 4, Paragraph 4.4 of IEC 62301 (incorporated by reference, see § 430.3). If the power measuring instrument used for testing is unable to measure and record the crest factor, power factor, or maximum current ratio during the test measurement period, the crest factor, power factor, and maximum current ratio may be measured and recorded immediately before and after the test measurement period.

2.5.4 Water and air temperature measuring devices. The temperature devices used to measure water and air temperature must have an error no greater than ±1 °F (±0.6 °C) over the range being measured.

2.5.4.1 Non-reversible temperature indicator labels, adhered to the inside of the clothes container, may be used to confirm that an extra-hot wash temperature greater than 135 °F has been achieved during the wash cycle, under the following conditions. The label must remain waterproof, intact, and adhered to the wash drum throughout an entire wash cycle; provide consistent maximum temperature readings; and provide repeatable temperature indications sufficient to demonstrate that a wash temperature of greater than 135 °F has been achieved. The label must have been verified to consistently indicate temperature measurements with an accuracy of ±1 °F if the label provides a temperature indicator at 135 °F. If the label does not provide a temperature indicator at 135 °F, the label must have been verified to consistently indicate temperature measurements with an accuracy of ±1 °F if the next-highest temperature indicator is greater than 135 °F and less than 140 °F, or ±3 °F if the next-highest temperature indicator is 140 °F or greater. If the label does not provide a temperature indicator at 135 °F, failure to activate the next-highest temperature indicator does not necessarily indicate the lack of an extra-hot wash temperature. However, such a result would not be conclusive due to the lack of verification of the water temperature requirement, in which case an alternative method must be used to confirm that an extra-hot wash temperature greater than 135 °F has been achieved during the wash cycle. If using a temperature indicator label to test a front-loading clothes washer, adhere the label along the interior surface of the clothes container drum, midway between the front and the back of the drum, adjacent to one of the baffles. If using a temperature indicator label to test a top-loading clothes washer, adhere the label along the interior surface of the clothes container drum, on the vertical portion of the sidewall, as close to the bottom of the container as possible.

2.5.4.2 Submersible temperature loggers placed inside the wash drum may be used to confirm that an extra-hot wash temperature greater than 135 °F has been achieved during the wash cycle, under the following conditions. The submersible temperature logger must have a time resolution of at least 1 data point every 5 seconds and a temperature measurement accuracy of ±1 °F. Due to the potential for a waterproof capsule to provide a thermal insulating effect, failure to measure a temperature of 135 °F does not necessarily indicate the lack of an extra-hot wash temperature. However, such a result would not be conclusive due to the lack of verification of the water temperature requirement, in which case an alternative method must be used to confirm that an extra-hot wash temperature greater than 135 °F has been achieved during the wash cycle.

2.5.5 Water meter. A water meter must be installed in both the hot and cold water lines to measure water flow and/or water consumption. The water meters must have a resolution no larger than 0.1 gallons (0.4 liters) and a maximum error no greater than 2 percent for the water flow rates being measured. If the volume of hot water for any individual cycle within the energy test cycle is less than 0.1 gallons (0.4 liters), the hot water meter must have a resolution no larger than 0.01 gallons (0.04 liters).

2.5.6 Water pressure gauge. A water pressure gauge must be installed in both the hot and cold water lines to measure water pressure. The water pressure gauges must have a resolution of 1 pound per square inch gauge (psig) (6.9 kPa) and a maximum error no greater than 5 percent of any measured value.

2.6 Bone dryer temperature. The dryer used for bone drying must heat the test cloth load above 210 °F (99 °C).

2.7 Test cloths. The test cloth material and dimensions must conform to the specifications in appendix J3 to this subpart. The energy test cloth and the energy stuffer cloths must be clean and must not be used for more than 60 test runs (after preconditioning as specified in section 5 of appendix J3 to this subpart). All energy test cloth must be permanently marked identifying the lot number of the material. Mixed lots of material must not be used for testing a clothes washer. The moisture absorption and retention must be evaluated for each new lot of test cloth using the standard extractor Remaining Moisture Content (RMC) procedure specified in appendix J3 to this subpart.

2.8 Test load sizes. Use Table 5.1 of this appendix to determine the maximum, minimum, and, when required, average test load sizes based on the clothes container capacity as measured in section 3.1 of this appendix. Test loads must consist of energy test cloths and no more than five energy stuffer cloths per load to achieve the proper weight.

Use the test load sizes and corresponding water fill settings defined in Table 2.8 of this appendix when measuring water and energy consumption. Use only the maximum test load size when measuring RMC.

Table 2.8—Required Test Load Sizes and Water Fill Settings

Water fill control system type Test load size Water fill setting Manual water fill control systemMax
Min
Max.
Min.
Automatic water fill control systemMax
Avg
Min
As determined by the clothes washer.

2.9 Use of test loads.

2.9.1 Test loads for energy and water consumption measurements must be bone dry prior to the first cycle of the test, and dried to a maximum of 104 percent of bone dry weight for subsequent testing.

2.9.2 Prepare the energy test cloths for loading by grasping them in the center, lifting, and shaking them to hang loosely, as illustrated in Figure 2.9.2 of this appendix.

For all clothes washers, follow any manufacturer loading instructions provided to the user regarding the placement of clothing within the clothes container. In the absence of any manufacturer instructions regarding the placement of clothing within the clothes container, the following loading instructions apply.

2.9.2.1 To load the energy test cloths in a top-loading clothes washer, arrange the cloths circumferentially around the axis of rotation of the clothes container, using alternating lengthwise orientations for adjacent pieces of cloth. Complete each cloth layer across its horizontal plane within the clothes container before adding a new layer. Figure 2.9.2.1 of this appendix illustrates the correct loading technique for a vertical-axis clothes washer.

2.9.2.2 To load the energy test cloths in a front-loading clothes washer, grasp each test cloth in the center as indicted in section 2.9.2 of this appendix, and then place each cloth into the clothes container prior to activating the clothes washer.

2.10 Clothes washer installation. Install the clothes washer in accordance with manufacturer's instructions. For combined low-power mode testing, install the clothes washer in accordance with Section 5, Paragraph 5.2 of IEC 62301 (incorporated by reference; see § 430.3), disregarding the provisions regarding batteries and the determination, classification, and testing of relevant modes.

2.11 Clothes washer pre-conditioning.

2.11.1 Non-water-heating clothes washer. If the clothes washer has not been filled with water in the preceding 96 hours, pre-condition it by running it through a cold rinse cycle and then draining it to ensure that the hose, pump, and sump are filled with water.

2.11.2 Water-heating clothes washer. If the clothes washer has not been filled with water in the preceding 96 hours, or if it has not been in the test room at the specified ambient conditions for 8 hours, pre-condition it by running it through a cold rinse cycle and then draining it to ensure that the hose, pump, and sump are filled with water.

2.12 Determining the energy test cycle. To determine the energy test cycle, evaluate the wash/rinse temperature selection flowcharts in the order in which they are presented in this section. Except for Cold Wash/Cold Rinse, use the maximum load size to evaluate each flowchart. The determination of the energy test cycle must take into consideration all cycle settings available to the end user, including any cycle selections or cycle modifications provided by the manufacturer via software or firmware updates to the product, for the basic model under test. The energy test cycle does not include any cycle that is recommended by the manufacturer exclusively for cleaning, deodorizing, or sanitizing the clothes washer.

3. Test Measurements

3.1 Clothes container capacity. Measure the entire volume that a clothes load could occupy within the clothes container during active mode washer operation according to the following procedures:

3.1.1 Place the clothes washer in such a position that the uppermost edge of the clothes container opening is leveled horizontally, so that the container will hold the maximum amount of water. For front-loading clothes washers, the door seal and shipping bolts or other forms of bracing hardware to support the wash drum during shipping must remain in place during the capacity measurement.

If the design of a front-loading clothes washer does not include shipping bolts or other forms of bracing hardware to support the wash drum during shipping, a laboratory may support the wash drum by other means, including temporary bracing or support beams. Any temporary bracing or support beams must keep the wash drum in a fixed position, relative to the geometry of the door and door seal components, that is representative of the position of the wash drum during normal operation. The method used must avoid damage to the unit that would affect the results of the energy and water testing.

For a front-loading clothes washer that does not include shipping bolts or other forms of bracing hardware to support the wash drum during shipping, the laboratory must fully document the alternative method used to support the wash drum during capacity measurement, include such documentation in the final test report, and pursuant to § 429.71 of this chapter, the manufacturer must retain such documentation as part its test records.

3.1.2 Line the inside of the clothes container with a 2 mil thickness (0.051 mm) plastic bag. All clothes washer components that occupy space within the clothes container and that are recommended for use during a wash cycle must be in place and must be lined with a 2 mil thickness (0.051 mm) plastic bag to prevent water from entering any void space.

3.1.3 Record the total weight of the machine before adding water.

3.1.4 Fill the clothes container manually with either 60 °F ± 5 °F (15.6 °C ± 2.8 °C) or 100 °F ± 10 °F (37.8 °C ± 5.5 °C) water, with the door open. For a top-loading vertical-axis clothes washer, fill the clothes container to the uppermost edge of the rotating portion, including any balance ring. Figure 3.1.4.1 of this appendix illustrates the maximum fill level for top-loading clothes washers.

For a front-loading horizontal-axis clothes washer, fill the clothes container to the highest point of contact between the door and the door gasket. If any portion of the door or gasket would occupy the measured volume space when the door is closed, exclude from the measurement the volume that the door or gasket portion would occupy. For a front-loading horizontal-axis clothes washer with a concave door shape, include any additional volume above the plane defined by the highest point of contact between the door and the door gasket, if that area can be occupied by clothing during washer operation. For a top-loading horizontal-axis clothes washer, include any additional volume above the plane of the door hinge that clothing could occupy during washer operation. Figure 3.1.4.2 of this appendix illustrates the maximum fill volumes for all horizontal-axis clothes washer types.

For all clothes washers, exclude any volume that cannot be occupied by the clothing load during operation.

3.1.5 Measure and record the weight of water, W, in pounds.

3.1.6 Calculate the clothes container capacity as follows:

C = W/d where: C = Capacity in cubic feet (liters). W = Mass of water in pounds (kilograms). d = Density of water (62.0 lbs/ft 3 for 100 °F (993 kg/m 3 for 37.8 °C) or 62.3 lbs/ft 3 for 60 °F (998 kg/m 3 for 15.6 °C)).

3.1.7 Calculate the clothes container capacity, C, to the nearest 0.01 cubic foot for the purpose of determining test load sizes per Table 5.1 of this appendix and for all subsequent calculations that include the clothes container capacity.

3.2 Procedure for measuring water and energy consumption values on all automatic and semi-automatic washers.

3.2.1 Perform all energy consumption tests under the energy test cycle.

3.2.2 Perform the test sections listed in Table 3.2.2 in accordance with the wash/rinse temperature selections available in the energy test cycle.

Table 3.2.2—Test Section Reference

Wash/rinse temperature
selections available in the
energy test cycle
Corresponding test section
reference
Extra-Hot/Cold3.3 Hot/Cold3.4 Warm/Cold3.5 Warm/Warm3.6 Cold/Cold3.7 Test Sections Applicable to all Clothes WashersRemaining Moisture Content3.8 Combined Low-Power Mode Power3.9

3.2.3 Hot and cold water faucets.

3.2.3.1 For automatic clothes washers, open both the hot and cold water faucets.

3.2.3.2 For semi-automatic washers:

(1) For hot inlet water temperature, open the hot water faucet completely and close the cold water faucet;

(2) For warm inlet water temperature, open both hot and cold water faucets completely;

(3) For cold inlet water temperature, close the hot water faucet and open the cold water faucet completely.

3.2.4 Wash/rinse temperature selection. Set the wash/rinse temperature selection control to obtain the desired wash/rinse temperature selection within the energy test cycle.

3.2.5 Wash time setting.

3.2.5.1 If the cycle under test offers a range of wash time settings, the wash time setting shall be the higher of either the minimum or 70 percent of the maximum wash time available for the wash cycle under test, regardless of the labeling of suggested dial locations. If 70 percent of the maximum wash time is not available on a dial with a discrete number of wash time settings, choose the next-highest setting greater than 70 percent.

3.2.5.2 If the clothes washer is equipped with an electromechanical dial or timer controlling wash time that rotates in both directions, reset the dial to the minimum wash time and then turn it in the direction of increasing wash time to reach the appropriate setting. If the appropriate setting is passed, return the dial to the minimum wash time and then turn in the direction of increasing wash time until the appropriate setting is reached.

3.2.6 Water fill levels.

3.2.6.1 Clothes washers with manual water fill control system. Set the water fill selector to the maximum water level available for the wash cycle under test for the maximum test load size and the minimum water level available for the wash cycle under test for the minimum test load size.

3.2.6.2 Clothes washers with automatic water fill control system.

3.2.6.2.1 Not user adjustable. The maximum, minimum, and average water levels as described in the following sections refer to the amount of water fill that is automatically selected by the control system when the respective test loads are used.

3.2.6.2.2 User-adjustable adaptive. Conduct four tests on clothes washers with user-adjustable adaptive water fill controls. Conduct the first test using the maximum test load and with the adaptive water fill control system set in the setting that uses the most water. Conduct the second test using the minimum test load and with the adaptive water fill control system set in the setting that uses the least water. Conduct the third test using the average test load and with the adaptive water fill control system set in the setting that uses the most water. Conduct the fourth test using the average test load and with the adaptive water fill control system set in the setting that uses the least water. Average the results of the third and fourth tests to obtain the energy and water consumption values for the average test load size.

3.2.6.3 Clothes washers with automatic water fill control system and alternate manual water fill control system. If a clothes washer with an automatic water fill control system allows user selection of manual controls as an alternative, test both manual and automatic modes and, for each mode, calculate the energy consumption (HET, MET, and DE) and water consumption (QT) values as set forth in section 4 of this appendix. Then, calculate the average of the two values (one from each mode, automatic and manual) for each variable (HET, MET, DE, and QT) and use the average value for each variable in the final calculations in section 4 of this appendix.

3.2.7 Manufacturer default settings. For clothes washers with electronic control systems, use the manufacturer default settings for any cycle selections, except for (1) the temperature selection, (2) the wash water fill levels, (3) if necessary, the spin speeds on wash cycles used to determine remaining moisture content, or (4) network settings. If the clothes washer has network capabilities, the network settings must be disabled throughout testing if such settings can be disabled by the end-user and the product's user manual provides instructions on how to do so. For all other cycle selections, the manufacturer default settings must be used for wash conditions such as agitation/tumble operation, soil level, spin speed on wash cycles used to determine energy and water consumption, wash times, rinse times, optional rinse settings, water heating time for water heating clothes washers, and all other wash parameters or optional features applicable to that wash cycle. Any optional wash cycle feature or setting (other than wash/rinse temperature, water fill level selection, spin speed on wash cycles used to determine remaining moisture content, or network settings on clothes washers with network capabilities) that is activated by default on the wash cycle under test must be included for testing unless the manufacturer instructions recommend not selecting this option, or recommend selecting a different option, for washing normally soiled cotton clothing. For clothes washers with control panels containing mechanical switches or dials, any optional settings, except for (1) the temperature selection, (2) the wash water fill levels, or (3) if necessary, the spin speeds on wash cycles used to determine remaining moisture content, must be in the position recommended by the manufacturer for washing normally soiled cotton clothing. If the manufacturer instructions do not recommend a particular switch or dial position to be used for washing normally soiled cotton clothing, the setting switch or dial must remain in its as-shipped position.

3.2.8 For each wash cycle tested, include the entire active washing mode and exclude any delay start or cycle finished modes.

3.2.9 Anomalous Test Cycles. If during a wash cycle the clothes washer: (a) Signals to the user by means of a visual or audio alert that an out-of-balance condition has been detected; or (b) terminates prematurely and thus does not include the agitation/tumble operation, spin speed(s), wash times, and rinse times applicable to the wash cycle under test, discard the test data and repeat the wash cycle. Document in the test report the rejection of data from any wash cycle during testing and the reason for the rejection.

3.3 Extra-Hot Wash/Cold Rinse. Measure the water and electrical energy consumption for each water fill level and test load size as specified in sections 3.3.1 through 3.3.3 of this appendix for the Extra-Hot Wash/Cold Rinse as defined within the energy test cycle.

3.3.1 Maximum test load and water fill. Measure the values for hot water consumption (HmX), cold water consumption (CmX), and electrical energy consumption (EmX) for an Extra-Hot Wash/Cold Rinse cycle, with the controls set for the maximum water fill level. Use the maximum test load size as specified in Table 5.1 of this appendix.

3.3.2 Minimum test load and water fill. Measure the values for hot water consumption (Hmn), cold water consumption (Cmn), and electrical energy consumption (Emn) for an Extra-Hot Wash/Cold Rinse cycle, with the controls set for the minimum water fill level. Use the minimum test load size as specified in Table 5.1 of this appendix.

3.3.3 Average test load and water fill. For a clothes washer with an automatic water fill control system, measure the values for hot water consumption (Hma), cold water consumption (Cma), and electrical energy consumption (Ema) for an Extra-Hot Wash/Cold Rinse cycle. Use the average test load size as specified in Table 5.1 of this appendix.

3.4 Hot Wash/Cold Rinse. Measure the water and electrical energy consumption for each water fill level and test load size as specified in sections 3.4.1 through 3.4.3 of this appendix for the Hot Wash/Cold Rinse temperature selection, as defined within the energy test cycle.

3.4.1 Maximum test load and water fill. Measure the values for hot water consumption (HhX), cold water consumption (ChX), and electrical energy consumption (EhX) for a Hot Wash/Cold Rinse cycle, with the controls set for the maximum water fill level. Use the maximum test load size as specified in Table 5.1 of this appendix.

3.4.2 Minimum test load and water fill. Measure the values for hot water consumption (Hhn), cold water consumption (Chn), and electrical energy consumption (Ehn) for a Hot Wash/Cold Rinse cycle, with the controls set for the minimum water fill level. Use the minimum test load size as specified in Table 5.1 of this appendix.

3.4.3 Average test load and water fill. For a clothes washer with an automatic water fill control system, measure the values for hot water consumption (Hha), cold water consumption (Cha), and electrical energy consumption (Eha) for a Hot Wash/Cold Rinse cycle. Use the average test load size as specified in Table 5.1 of this appendix.

3.5 Warm Wash/Cold Rinse. Measure the water and electrical energy consumption for each water fill level and test load size as specified in sections 3.5.1 through 3.5.3 of this appendix for the applicable Warm Wash/Cold Rinse temperature selection(s), as defined within the energy test cycle.

For a clothes washer with fewer than four discrete Warm Wash/Cold Rinse temperature selections, test all Warm Wash/Cold Rinse selections. For a clothes washer that offers four or more Warm Wash/Cold Rinse selections, test at all discrete selections, or test at the 25 percent, 50 percent, and 75 percent positions of the temperature selection device between the hottest hot (≤135 °F (57.2 °C)) wash and the coldest cold wash. If a selection is not available at the 25, 50 or 75 percent position, in place of each such unavailable selection, use the next warmer setting. For each reportable value to be used for the Warm Wash/Cold Rinse temperature selection, calculate the average of all Warm Wash/Cold Rinse temperature selections tested pursuant to this section.

3.5.1 Maximum test load and water fill. Measure the values for hot water consumption (HwX), cold water consumption (CwX), and electrical energy consumption (EwX) for the Warm Wash/Cold Rinse cycle, with the controls set for the maximum water fill level. Use the maximum test load size as specified in Table 5.1 of this appendix.

3.5.2 Minimum test load and water fill. Measure the values for hot water consumption (Hwn), cold water consumption (Cwn), and electrical energy consumption (Ewn) for the Warm Wash/Cold Rinse cycle, with the controls set for the minimum water fill level. Use the minimum test load size as specified in Table 5.1 of this appendix.

3.5.3 Average test load and water fill. For a clothes washer with an automatic water fill control system, measure the values for hot water consumption (Hwa), cold water consumption (Cwa), and electrical energy consumption (Ewa) for a Warm Wash/Cold Rinse cycle. Use the average test load size as specified in Table 5.1 of this appendix.

3.6 Warm Wash/Warm Rinse. Measure the water and electrical energy consumption for each water fill level and/or test load size as specified in sections 3.6.1 through 3.6.3 of this appendix for the applicable Warm Wash/Warm Rinse temperature selection(s), as defined within the energy test cycle. For a clothes washer with fewer than four discrete Warm Wash/Warm Rinse temperature selections, test all Warm Wash/Warm Rinse selections. For a clothes washer that offers four or more Warm Wash/Warm Rinse selections, test at all discrete selections, or test at 25 percent, 50 percent, and 75 percent positions of the temperature selection device between the hottest hot (≤ 135 °F (57.2 °C)) wash and the coldest cold wash. If a selection is not available at the 25, 50 or 75 percent position, in place of each such unavailable selection use the next warmer setting. For each reportable value to be used for the Warm Wash/Warm Rinse temperature selection, calculate the average of all Warm Wash/Warm Rinse temperature selections tested pursuant to this section.

3.6.1 Maximum test load and water fill. Measure the values for hot water consumption (HwwX), cold water consumption (CwwX), and electrical energy consumption (EwwX) for the Warm Wash/Warm Rinse cycle, with the controls set for the maximum water fill level. Use the maximum test load size as specified in Table 5.1 of this appendix.

3.6.2 Minimum test load and water fill. Measure the values for hot water consumption (Hwwn), cold water consumption (Cwwn), and electrical energy consumption (Ewwn) for the Warm Wash/Warm Rinse cycle, with the controls set for the minimum water fill level. Use the minimum test load size as specified in Table 5.1 of this appendix.

3.6.3 Average test load and water fill. For a clothes washer with an automatic water fill control system, measure the values for hot water consumption (Hwwa), cold water consumption (Cwwa), and electrical energy consumption (Ewwa) for the Warm Wash/Warm Rinse cycle. Use the average test load size as specified in Table 5.1 of this appendix.

3.7 Cold Wash/Cold Rinse. Measure the water and electrical energy consumption for each water fill level and test load size as specified in sections 3.7.1 through 3.7.3 of this appendix for the applicable Cold Wash/Cold Rinse temperature selection, as defined within the energy test cycle.

3.7.1 Maximum test load and water fill. Measure the values for hot water consumption (HcX), cold water consumption (CcX), and electrical energy consumption (EcX) for a Cold Wash/Cold Rinse cycle, with the controls set for the maximum water fill level. Use the maximum test load size as specified in Table 5.1 of this appendix.

3.7.2 Minimum test load and water fill. Measure the values for hot water consumption (Hcn), cold water consumption (Ccn), and electrical energy consumption (Ecn) for a Cold Wash/Cold Rinse cycle, with the controls set for the minimum water fill level. Use the minimum test load size as specified in Table 5.1 of this appendix.

3.7.3 Average test load and water fill. For a clothes washer with an automatic water fill control system, measure the values for hot water consumption (Hca), cold water consumption (Cca), and electrical energy consumption (Eca) for a Cold Wash/Cold Rinse cycle. Use the average test load size as specified in Table 5.1 of this appendix.

3.8 Remaining moisture content (RMC).

3.8.1 The wash temperature must be the same as the rinse temperature for all testing. Use the maximum test load as defined in Table 5.1 of this appendix for testing.

3.8.2 Clothes washers with cold rinse only.

3.8.2.1 Record the actual “bone dry” weight of the test load (WIX), then place the test load in the clothes washer.

3.8.2.2 Set the water level controls to maximum fill.

3.8.2.3 Run the Cold Wash/Cold Rinse cycle.

3.8.2.4 Record the weight of the test load immediately after completion of the wash cycle (WCX).

3.8.2.5 Calculate the remaining moisture content of the maximum test load, RMCX, defined as:

RMCX = (WCX − WIX)/WIX

3.8.2.6 Apply the RMC correction curve described in section 9 of appendix J3 to this subpart to calculate the corrected remaining moisture content, RMCcorr, expressed as a percentage as follows:

RMCcorr = (A × RMCX + B) × 100% where: A and B are the coefficients of the RMC correction curve as defined in section 8.7 of appendix J3 to this subpart. RMCX = As defined in section 3.8.2.5 of this appendix.

3.8.2.7 Use RMCcorr as the final corrected RMC in section 4.3 of this appendix.

3.8.3 Clothes washers with both cold and warm rinse options.

3.8.3.1 Complete sections 3.8.2.1 through 3.8.2.4 of this appendix for a Cold Wash/Cold Rinse cycle. Calculate the remaining moisture content of the maximum test load for Cold Wash/Cold Rinse, RMCCOLD, defined as:

RMCCOLD = (WCX − WIX)/WIX

3.8.3.2 Apply the RMC correction curve described in section 9 of appendix J3 to this subpart to calculate the corrected remaining moisture content for Cold Wash/Cold Rinse, RMCCOLD,corr, expressed as a percentage, as follows:

RMCCOLD,corr = (A × RMCCOLD + B) × 100% where: A and B are the coefficients of the RMC correction curve as defined in section 8.7 of appendix J3 to this subpart. RMCCOLD = As defined in section 3.8.3.1 of this appendix.

3.8.3.3 Complete sections 3.8.2.1 through 3.8.2.4 of this appendix using a Warm Wash/Warm Rinse cycle instead. Calculate the remaining moisture content of the maximum test load for Warm Wash/Warm Rinse, RMCWARM, defined as:

RMCWARM = (WCX−WIX)/WIX

3.8.3.4 Apply the RMC correction curve described in section 9 of appendix J3 to this subpart to calculate the corrected remaining moisture content for Warm Wash/Warm Rinse, RMCWARM,corr, expressed as a percentage, as follows:

RMCWARM,corr = (A × RMCWARM + B) × 100% where: A and B are the coefficients of the RMC correction curve as defined in section 8.7 of appendix J3 to this subpart. RMCWARM = As defined in section 3.8.3.3 of this appendix.

3.8.3.5 Calculate the corrected remaining moisture content of the maximum test load, RMCcorr, expressed as a percentage as follows:

RMCcorr = RMCCOLD,corr × (1 − TUFww) + RMCWARM,corr × (TUFww) where: RMCCOLD,corr = As defined in section 3.8.3.2 of this Appendix. RMCWARM,corr = As defined in section 3.8.3.4 of this Appendix. TUFww is the temperature use factor for Warm Wash/Warm Rinse as defined in Table 4.1.1 of this appendix.

3.8.3.6 Use RMCcorr as calculated in section 3.8.3.5 as the final corrected RMC used in section 4.3 of this appendix.

3.8.4 Clothes washers that have options such as multiple selections of spin speeds or spin times that result in different RMC values, and that are available within the energy test cycle.

3.8.4.1 Complete sections 3.8.2 or 3.8.3 of this appendix, as applicable, using the maximum and minimum extremes of the available spin options, excluding any “no spin” (zero spin speed) settings. Combine the calculated values RMCcorr,max extraction and RMCcorr,min extraction at the maximum and minimum settings, respectively, as follows:

RMCcorr = 0.75 × RMCcorr,max extraction + 0.25 × RMCcorr,min extraction where: RMCcorr, max extraction is the corrected remaining moisture content using the maximum spin setting, calculated according to section 3.8.2 or 3.8.3 of this appendix, as applicable. RMCcorr, min extraction is the corrected remaining moisture content using the minimum spin setting, calculated according to section 3.8.2 or 3.8.3 of this appendix, as applicable.

3.8.4.2 Use RMCcorr as calculated in section 3.8.4.1 as the final corrected RMC used in section 4.3 of this appendix.

3.8.5 The procedure for calculating the corrected RMC as described in section 3.8.2, 3.8.3, or 3.8.4 of this appendix may be replicated twice in its entirety, for a total of three independent corrected RMC measurements. If three replications of the RMC measurement are performed, use the average of the three corrected RMC measurements as the final corrected RMC in section 4.3 of this appendix.

3.9 Combined low-power mode power. Connect the clothes washer to a watt meter as specified in section 2.5.3 of this appendix. Establish the testing conditions set forth in sections 2.1, 2.4, and 2.10 of this appendix.

3.9.1 Perform combined low-power mode testing after completion of an active mode wash cycle included as part of the energy test cycle; after removing the test load; without changing the control panel settings used for the active mode wash cycle; with the door closed; and without disconnecting the electrical energy supply to the clothes washer between completion of the active mode wash cycle and the start of combined low-power mode testing.

3.9.2 For a clothes washer that takes some time to automatically enter a stable inactive mode or off mode state from a higher power state as discussed in Section 5, Paragraph 5.1, note 1 of IEC 62301 (incorporated by reference; see § 430.3), allow sufficient time for the clothes washer to automatically reach the default inactive/off mode state before proceeding with the test measurement.

3.9.3 Once the stable inactive/off mode state has been reached, measure and record the default inactive/off mode power, Pdefault, in watts, following the test procedure for the sampling method specified in Section 5, Paragraph 5.3.2 of IEC 62301.

3.9.4 For a clothes washer with a switch, dial, or button that can be optionally selected by the end user to achieve a lower-power inactive/off mode state than the default inactive/off mode state measured in section 3.9.3 of this appendix, after performing the measurement in section 3.9.3, activate the switch, dial, or button to the position resulting in the lowest power consumption and repeat the measurement procedure described in section 3.9.3. Measure and record the lowest-power inactive/off mode power, Plowest, in Watts.

3.10 Energy consumption for the purpose of determining the cycle selection(s) to be included in the energy test cycle. This section is implemented only in cases where the energy test cycle flowcharts in section 2.12 require the determination of the wash/rinse temperature selection with the highest energy consumption.

3.10.1 For the wash/rinse temperature selection being considered under this section, establish the testing conditions set forth in section 2 of this appendix. Select the applicable cycle selection and wash/rinse temperature selection. For all wash/rinse temperature selections, the manufacturer default settings shall be used as described in section 3.2.7 of this appendix.

3.10.2 Use the clothes washer's maximum test load size, determined from Table 5.1 of this appendix, for testing under this section.

3.10.3 For clothes washers with a manual fill control system, user-adjustable automatic water fill control system, or automatic water fill control system with alternate manual water fill control system, use the water fill selector setting resulting in the maximum water level available for each cycle selection for testing under this section.

3.10.4 Each wash cycle tested under this section shall include the entire active washing mode and exclude any delay start or cycle finished modes.

3.10.5 Measure each wash cycle's electrical energy consumption (EX) and hot water consumption (HX). Calculate the total energy consumption for each cycle selection (ETX), as follows:

ETX = EX + (HX × T × K) where: EX is the electrical energy consumption, expressed in kilowatt-hours per cycle. HX is the hot water consumption, expressed in gallons per cycle. T = nominal temperature rise = 75 °F (41.7 °C). K = Water specific heat in kilowatt-hours per gallon per degree F = 0.00240 kWh/gal - °F (0.00114 kWh/L- °C). 4. Calculation of Derived Results From Test Measurements

4.1 Hot water and machine electrical energy consumption of clothes washers.

4.1.1 Per-cycle temperature-weighted hot water consumption for all maximum, average, and minimum water fill levels tested. Calculate the per-cycle temperature-weighted hot water consumption for the maximum water fill level, VhX, the average water fill level, Vha, and the minimum water fill level, Vhn, expressed in gallons per cycle (or liters per cycle) and defined as:

(a) VhX = [HmX × TUFm] + [HhX × TUFh] + [HwX × TUFw] + [HwwX × TUFww] + [HcX × TUFc] (b) Vha = [Hma × TUFm] + [Hha × TUFh] + [Hwa × TUFw] + [Hwwa × TUFww] + [Hca × TUFc] (c) Vhn = [Hmn × TUFm] + [Hhn × TUFh] + [Hwn × TUFw] + [Hwwn × TUFww] + [Hcn × TUFc] where:

HmX, Hma, and Hmn, are reported hot water consumption values, in gallons per-cycle (or liters per cycle), at maximum, average, and minimum water fill levels, respectively, for the Extra-Hot Wash/Cold Rinse cycle, as measured in sections 3.3.1 through 3.3.3 of this appendix.

HhX, Hha, and Hhn, are reported hot water consumption values, in gallons per-cycle (or liters per cycle), at maximum, average, and minimum water fill levels, respectively, for the Hot Wash/Cold Rinse cycle, as measured in sections 3.4.1 through 3.4.3 of this appendix.

HwX, Hwa, and Hwn, are reported hot water consumption values, in gallons per-cycle (or liters per cycle), at maximum, average, and minimum water fill levels, respectively, for the Warm Wash/Cold Rinse cycle, as measured in sections 3.5.1 through 3.5.3 of this appendix.

HwwX, Hwwa, and Hwwn, are reported hot water consumption values, in gallons per-cycle (or liters per cycle), at maximum, average, and minimum water fill levels, respectively, for the Warm Wash/Warm Rinse cycle, as measured in sections 3.6.1 through 3.6.3 of this appendix.

HcX, Hca, and Hcn, are reported hot water consumption values, in gallons per-cycle (or liters per cycle), at maximum, average, and minimum water fill levels, respectively, for the Cold Wash/Cold Rinse cycle, as measured in sections 3.7.1 through 3.7.3 of this appendix.

TUFm, TUFh, TUFw, TUFww, and TUFc are temperature use factors for Extra-Hot Wash/Cold Rinse, Hot Wash/Cold Rinse, Warm Wash/Cold Rinse, Warm Wash/Warm Rinse, and Cold Wash/Cold Rinse temperature selections, respectively, as defined in Table 4.1.1 of this appendix.

Table 4.1.1—Temperature Use Factors

Wash/Rinse Temperature Selections Available in the Energy Test Cycle Clothes washers with cold rinse only Clothes washers with both cold and warm rinse C/C H/C
C/C
H/C
W/C
C/C
XH/C
H/C
C/C
XH/C
H/C
W/C
C/C
H/C
W/C
W/W
C/C
XH/C
H/C
W/W
C/C
XH/C
H/C
W/C
W/W
C/C
TUFm (Extra-Hot/Cold)0.140.050.140.05 TUFh (Hot/Cold)0.630.14* 0.490.090.14* 0.220.09 TUFw (Warm/Cold)0.490.490.220.22 TUFww (Warm/Warm)0.270.270.27 TUFc (Cold/Cold)1.000.370.370.370.370.370.370.37

* On clothes washers with only two wash temperature selections ≤135 °F, the higher of the two wash temperatures is classified as a Hot Wash/Cold Rinse, in accordance with the wash/rinse temperature definitions within the energy test cycle.

4.1.2 Total per-cycle hot water energy consumption for all maximum, average, and minimum water fill levels tested. Calculate the total per-cycle hot water energy consumption for the maximum water fill level, HEmax, the average water fill level, HEavg, and the minimum water fill level, HEmin, expressed in kilowatt-hours per cycle and defined as:

(a) HEmax = [VhX × T × K] = Total energy when a maximum load is tested. (b) HEavg = [Vha × T × K] = Total energy when an average load is tested. (c) HEmin = [Vhn × T × K] = Total energy when a minimum load is tested. where: VhX, Vha, and Vhn are defined in section 4.1.1 of this appendix. T = Temperature rise = 75 °F (41.7 °C). K = Water specific heat in kilowatt-hours per gallon per degree F = 0.00240 kWh/gal- °F (0.00114 kWh/L- °C).

4.1.3 Total weighted per-cycle hot water energy consumption. Calculate the total weighted per-cycle hot water energy consumption, HET, expressed in kilowatt-hours per cycle and defined as:

HET = [HEmax × Fmax] + [HEavg × Favg] + HEmin × Fmin] where:

HEmax, HEavg, and HEmin are defined in section 4.1.2 of this appendix.

Fmax, Favg, and Fmin are the load usage factors for the maximum, average, and minimum test loads based on the size and type of the control system on the washer being tested, as defined in Table 4.1.3 of this appendix.

Table 4.1.3—Load Usage Factors

Load usage factor Water fill control system Manual Automatic Fmax =0.720.12 Favg =0.74 Fmin =0.280.14

4.1.4 Total per-cycle hot water energy consumption using gas-heated or oil-heated water, for product labeling requirements. Calculate for the energy test cycle the per-cycle hot water consumption, HETG, using gas-heated or oil-heated water, expressed in Btu per cycle (or megajoules per cycle) and defined as:

HETG = HET × 1/e × 3412 Btu/kWh or HETG = HET × 1/e × 3.6 MJ/kWh where: e = Nominal gas or oil water heater efficiency = 0.75. HET = As defined in section 4.1.3 of this Appendix.

4.1.5 Per-cycle machine electrical energy consumption for all maximum, average, and minimum test load sizes. Calculate the total per-cycle machine electrical energy consumption for the maximum water fill level, MEmax, the average water fill level, MEavg, and the minimum water fill level, MEmin, expressed in kilowatt-hours per cycle and defined as:

(a) MEmax = [EmX × TUFm] + [EhX × TUFh] + [EwX × TUFw] + [EwwX × TUFww] + [EcX × TUFc] (b) MEavg = [Ema × TUFm] + [Eha × TUFh] + [Ewa × TUFw] + [Ewwa × TUFww] + [Eca × TUFc] (c) MEmin = [Emn × TUFm] + [Ehn × TUFh] + [Ewn × TUFw] + [Ewwn × TUFww] + [Ecn × TUFc] where:

EmX, Ema, and Emn, are reported electrical energy consumption values, in kilowatt-hours per cycle, at maximum, average, and minimum test loads, respectively, for the Extra-Hot Wash/Cold Rinse cycle, as measured in sections 3.3.1 through 3.3.3 of this appendix.

EhX, Eha, and Ehn, are reported electrical energy consumption values, in kilowatt-hours per cycle, at maximum, average, and minimum test loads, respectively, for the Hot Wash/Cold Rinse cycle, as measured in sections 3.4.1 through 3.4.3 of this appendix.

EwX, Ewa, and Ewn, are reported electrical energy consumption values, in kilowatt-hours per cycle, at maximum, average, and minimum test loads, respectively, for the Warm Wash/Cold Rinse cycle, as measured in sections 3.5.1 through 3.5.3 of this appendix.

EwwX, Ewwa, and Ewwn, are reported electrical energy consumption values, in kilowatt-hours per cycle, at maximum, average, and minimum test loads, respectively, for the Warm Wash/Warm Rinse cycle, as measured in sections 3.6.1 through 3.6.3 of this appendix.

EcX, Eca, and Ecn, are reported electrical energy consumption values, in kilowatt-hours per cycle, at maximum, average, and minimum test loads, respectively, for the Cold Wash/Cold Rinse cycle, as measured in sections 3.7.1 through 3.7.3 of this appendix.

TUFm, TUFh, TUFw, TUFww, and TUFc are defined in Table 4.1.1 of this appendix.

4.1.6 Total weighted per-cycle machine electrical energy consumption. Calculate the total weighted per-cycle machine electrical energy consumption, MET, expressed in kilowatt-hours per cycle and defined as:

MET = [MEmax × Fmax] + [MEavg × Favg] + [MEmin × Fmin] where:

MEmax, MEavg, and MEmin are defined in section 4.1.5 of this appendix.

Fmax, Favg, and Fmin are defined in Table 4.1.3 of this appendix.

4.1.7 Total per-cycle energy consumption when electrically heated water is used. Calculate the total per-cycle energy consumption, ETE, using electrically heated water, expressed in kilowatt-hours per cycle and defined as:

ETE = HET + MET where: MET = As defined in section 4.1.6 of this appendix. HET = As defined in section 4.1.3 of this appendix.

4.2 Water consumption of clothes washers.

4.2.1 Per-cycle water consumption for Extra-Hot Wash/Cold Rinse. Calculate the maximum, average, and minimum total water consumption, expressed in gallons per cycle (or liters per cycle), for the Extra-Hot Wash/Cold Rinse cycle and defined as:

Qmmax = [HmX + CmX] Qmavg = [Hma + Cma] Qmmin = [Hmn + Cmn] where:

HmX, CmX, Hma, Cma, Hmn, and Cmn are defined in section 3.3 of this appendix.

4.2.2 Per-cycle water consumption for Hot Wash/Cold Rinse. Calculate the maximum, average, and minimum total water consumption, expressed in gallons per cycle (or liters per cycle), for the Hot Wash/Cold Rinse cycle and defined as:

Qhmax = [HhX + ChX] Qhavg = [Hha + Cha] Qhmin = [Hhn + Chn] where:

HhX, ChX, Hha, Cha, Hhn, and Chn are defined in section 3.4 of this appendix.

4.2.3 Per-cycle water consumption for Warm Wash/Cold Rinse. Calculate the maximum, average, and minimum total water consumption, expressed in gallons per cycle (or liters per cycle), for the Warm Wash/Cold Rinse cycle and defined as:

Qwmax = [HwX + CwX] Qwavg = [Hwa + Cwa] Qwmin = [Hwn + Cwn] where:

HwX, CwX, Hwa, Cwa, Hwn, and Cwn are defined in section 3.5 of this appendix.

4.2.4 Per-cycle water consumption for Warm Wash/Warm Rinse. Calculate the maximum, average, and minimum total water consumption, expressed in gallons per cycle (or liters per cycle), for the Warm Wash/Warm Rinse cycle and defined as:

Qwwmax = [HwwX + CwwX] Qwwavg = [Hwwa + Cwwa] Qwwmin = [Hwwn + Cwwn] where: HwwX, CwwX, Hwwa, Cwwa, Hwwn, and Cwwn are defined in section 3.6 of this appendix.

4.2.5 Per-cycle water consumption for Cold Wash/Cold Rinse. Calculate the maximum, average, and minimum total water consumption, expressed in gallons per cycle (or liters per cycle), for the Cold Wash/Cold Rinse cycle and defined as:

Qcmax = [HcX + CcX] Qcavg = [Hca + Cca] Qcmin = [Hcn + Ccn] where: HcX, CcX, Hca, Cca, Hcn, and Ccn are defined in section 3.7 of this appendix.

4.2.6 Total weighted per-cycle water consumption for Extra-Hot Wash/Cold Rinse. Calculate the total weighted per-cycle water consumption for the Extra-Hot Wash/Cold Rinse cycle, QmT, expressed in gallons per cycle (or liters per cycle) and defined as:

QmT = [Qmmax × Fmax] + [Qmavg × Favg] + [Qmmin × Fmin] where:

Qmmax, Qmavg, Qmmin are defined in section 4.2.1 of this appendix.

Fmax, Favg, Fmin are defined in Table 4.1.3 of this appendix.

4.2.7 Total weighted per-cycle water consumption for Hot Wash/Cold Rinse. Calculate the total weighted per-cycle water consumption for the Hot Wash/Cold Rinse cycle, QhT, expressed in gallons per cycle (or liters per cycle) and defined as:

QhT = [Qhmax × Fmax] + [Qhavg × Favg] + [Qhmin × Fmin] where:

Qhmax, Qhavg, Qhmin are defined in section 4.2.2 of this appendix.

Fmax, Favg, Fmin are defined in Table 4.1.3 of this appendix.

4.2.8 Total weighted per-cycle water consumption for Warm Wash/Cold Rinse. Calculate the total weighted per-cycle water consumption for the Warm Wash/Cold Rinse cycle, QwT, expressed in gallons per cycle (or liters per cycle) and defined as:

QwT = [Qwmax × Fmax] + [Qwavg × Favg] + [Qwmin × Fmin] where:

Qwmax, Qwavg, Qwmin are defined in section 4.2.3 of this appendix.

Fmax, Favg, Fmin are defined in Table 4.1.3 of this appendix.

4.2.9 Total weighted per-cycle water consumption for Warm Wash/Warm Rinse. Calculate the total weighted per-cycle water consumption for the Warm Wash/Warm Rinse cycle, QwwT, expressed in gallons per cycle (or liters per cycle) and defined as:

QwwT = [Qwwmax × Fmax] + [Qwwavg × Favg] + [Qwwmin × Fmin] where:

Qwwmax, Qwwavg, Qwwmin are defined in section 4.2.4 of this appendix.

Fmax, Favg, Fmin are defined in Table 4.1.3 of this appendix.

4.2.10 Total weighted per-cycle water consumption for Cold Wash/Cold Rinse. Calculate the total weighted per-cycle water consumption for the Cold Wash/Cold Rinse cycle, QcT, expressed in gallons per cycle (or liters per cycle) and defined as:

QcT = [Qcmax × Fmax] + [Qcavg × Favg] + [Qcmin × Fmin] where:

Qcmax, Qcavg, Qcmin are defined in section 4.2.5 of this appendix.

Fmax, Favg, Fmin are defined in Table 4.1.3 of this appendix.

4.2.11 Total weighted per-cycle water consumption for all wash cycles. Calculate the total weighted per-cycle water consumption for all wash cycles, QT, expressed in gallons per cycle (or liters per cycle) and defined as:

QT = [QmT × TUFm] + [QhT × TUFh] + [QwT × TUFw] + [QwwT × TUFww] + [QcT × TUFc] where:

QmT, QhT, QwT, QwwT, and QcT are defined in sections 4.2.6 through 4.2.10 of this appendix.

TUFm, TUFh, TUFw, TUFww, and TUFc are defined in Table 4.1.1 of this appendix.

4.2.12 Integrated water factor. Calculate the integrated water factor, IWF, expressed in gallons per cycle per cubic foot (or liters per cycle per liter), as:

IWF = QT/C where: QT = As defined in section 4.2.11 of this appendix. C = As defined in section 3.1.7 of this appendix.

4.3 Per-cycle energy consumption for removal of moisture from test load. Calculate the per-cycle energy required to remove the remaining moisture of the test load, DE, expressed in kilowatt-hours per cycle and defined as:

DE = [(Fmax × Maximum test load weight) + (Favg × Average test load weight) + (Fmin × Minimum test load weight)] × (RMCcorr - 4%) × (DEF) × (DUF)

where:

Fmax, Favg, and Fmin are defined in Table 4.1.3 of this appendix.

Maximum, average, and minimum test load weights are defined in Table 5.1 of this appendix.

RMCcorr = As defined in section 3.8.2.6, 3.8.3.5, or 3.8.4.1 of this Appendix. DEF = Nominal energy required for a clothes dryer to remove moisture from clothes = 0.5 kWh/lb (1.1 kWh/kg). DUF = Dryer usage factor, percentage of washer loads dried in a clothes dryer = 0.91.

4.4 Per-cycle combined low-power mode energy consumption. Calculate the per-cycle combined low-power mode energy consumption, ETLP, expressed in kilowatt-hours per cycle and defined as:

ETLP = [(Pdefault × Sdefault) + (Plowest × Slowest)] × Kp/295 where:

Pdefault = Default inactive/off mode power, in watts, as measured in section 3.9.3 of this appendix.

Plowest = Lowest-power inactive/off mode power, in watts, as measured in section 3.9.4 of this appendix for clothes washers with a switch, dial, or button that can be optionally selected by the end user to achieve a lower-power inactive/off mode than the default inactive/off mode; otherwise, Plowest=0. Sdefault= Annual hours in default inactive/off mode, defined as 8,465 if no optional lowest-power inactive/off mode is available; otherwise 4,232.5. Slowest= Annual hours in lowest-power inactive/off mode, defined as 0 if no optional lowest-power inactive/off mode is available; otherwise 4,232.5. Kp = Conversion factor of watt-hours to kilowatt-hours = 0.001. 295 = Representative average number of clothes washer cycles in a year. 8,465 = Combined annual hours for inactive and off mode. 4,232.5 = One-half of the combined annual hours for inactive and off mode.

4.5 Modified energy factor. Calculate the modified energy factor, MEFJ2, expressed in cubic feet per kilowatt-hour per cycle (or liters per kilowatt-hour per cycle) and defined as:

MEFJ2 = C/(ETE + DE) where: C = As defined in section 3.1.7 of this appendix. ETE = As defined in section 4.1.7 of this appendix. DE = As defined in section 4.3 of this appendix.

4.6 Integrated modified energy factor. Calculate the integrated modified energy factor, IMEF, expressed in cubic feet per kilowatt-hour per cycle (or liters per kilowatt-hour per cycle) and defined as:

IMEF = C/(ETE + DE + ETLP) where: C = As defined in section 3.1.7 of this appendix. ETE = As defined in section 4.1.7 of this appendix. DE = As defined in section 4.3 of this appendix. ETLP = As defined in section 4.4 of this appendix. 5. Test Loads

Table 5.1—Test Load Sizes

Container volume Minimum load Maximum load Average load cu. ft. liter lb kg lb kg lb kg ≥ < ≥ < 0.00-0.800.00-22.73.001.363.001.363.001.36 0.80-0.9022.7-25.53.001.363.501.593.251.47 0.90-1.0025.5-28.33.001.363.901.773.451.56 1.00-1.1028.3-31.13.001.364.301.953.651.66 1.10-1.2031.1-34.03.001.364.702.133.851.75 1.20-1.3034.0-36.83.001.365.102.314.051.84 1.30-1.4036.8-39.63.001.365.502.494.251.93 1.40-1.5039.6-42.53.001.365.902.684.452.02 1.50-1.6042.5-45.33.001.366.402.904.702.13 1.60-1.7045.3-48.13.001.366.803.084.902.22 1.70-1.8048.1-51.03.001.367.203.275.102.31 1.80-1.9051.0-53.83.001.367.603.455.302.40 1.90-2.0053.8-56.63.001.368.003.635.502.49 2.00-2.1056.6-59.53.001.368.403.815.702.59 2.10-2.2059.5-62.33.001.368.803.995.902.68 2.20-2.3062.3-65.13.001.369.204.176.102.77 2.30-2.4065.1-68.03.001.369.604.356.302.86 2.40-2.5068.0-70.83.001.3610.004.546.502.95 2.50-2.6070.8-73.63.001.3610.504.766.753.06 2.60-2.7073.6-76.53.001.3610.904.946.953.15 2.70-2.8076.5-79.33.001.3611.305.137.153.24 2.80-2.9079.3-82.13.001.3611.705.317.353.33 2.90-3.0082.1-85.03.001.3612.105.497.553.42 3.00-3.1085.0-87.83.001.3612.505.677.753.52 3.10-3.2087.8-90.63.001.3612.905.857.953.61 3.20-3.3090.6-93.43.001.3613.306.038.153.70 3.30-3.4093.4-96.33.001.3613.706.218.353.79 3.40-3.5096.3-99.13.001.3614.106.408.553.88 3.50-3.6099.1-101.93.001.3614.606.628.803.99 3.60-3.70101.9-104.83.001.3615.006.809.004.08 3.70-3.80104.8-107.63.001.3615.406.999.204.17 3.80-3.90107.6-110.43.001.3615.807.169.404.26 3.90-4.00110.4-113.33.001.3616.207.349.604.35 4.00-4.10113.3-116.13.001.3616.607.539.804.45 4.10-4.20116.1-118.93.001.3617.007.7210.004.54 4.20-4.30118.9-121.83.001.3617.407.9010.204.63 4.30-4.40121.8-124.63.001.3617.808.0910.404.72 4.40-4.50124.6-127.43.001.3618.208.2710.604.82 4.50-4.60127.4-130.33.001.3618.708.4610.854.91 4.60-4.70130.3-133.13.001.3619.108.6511.055.00 4.70-4.80133.1-135.93.001.3619.508.8311.255.10 4.80-4.90135.9-138.83.001.3619.909.0211.455.19 4.90-5.00138.8-141.63.001.3620.309.2011.655.28 5.00-5.10141.6-144.43.001.3620.709.3911.855.38 5.10-5.20144.4-147.23.001.3621.109.5812.055.47 5.20-5.30147.2-150.13.001.3621.509.7612.255.56 5.30-5.40150.1-152.93.001.3621.909.9512.455.65 5.40-5.50152.9-155.73.001.3622.3010.1312.655.75 5.50-5.60155.7-158.63.001.3622.8010.3212.905.84 5.60-5.70158.6-161.43.001.3623.2010.5113.105.93 5.70-5.80161.4-164.23.001.3623.6010.6913.306.03 5.80-5.90164.2-167.13.001.3624.0010.8813.506.12 5.90-6.00167.1-169.93.001.3624.4011.0613.706.21 6.00-6.10169.9-172.73.001.3624.8011.2513.906.30 6.10-6.20172.7-175.63.001.3625.2011.4314.106.40 6.20-6.30175.6-178.43.001.3625.6011.6114.306.49 6.30-6.40178.4-181.23.001.3626.0011.7914.506.58 6.40-6.50181.2-184.13.001.3626.4011.9714.706.67 6.50-6.60184.1-186.93.001.3626.9012.2014.956.78 6.60-6.70186.9-189.73.001.3627.3012.3815.156.87 6.70-6.80189.7-192.63.001.3627.7012.5615.356.96 6.80-6.90192.6-195.43.001.3628.1012.7515.557.05 6.90-7.00195.4-198.23.001.3628.5012.9315.757.14 7.00-7.10198.2-201.03.001.3628.9013.1115.957.23 7.10-7.20201.0-203.93.001.3629.3013.2916.157.33 7.20-7.30203.9-206.73.001.3629.7013.4716.357.42 7.30-7.40206.7-209.53.001.3630.1013.6516.557.51 7.40-7.50209.5-212.43.001.3630.5013.8316.757.60 7.50-7.60212.4-215.23.001.3631.0014.0617.007.71 7.60-7.70215.2-218.03.001.3631.4014.2417.207.80 7.70-7.80218.0-220.93.001.3631.8014.4217.407.89 7.80-7.90220.9-223.73.001.3632.2014.6117.607.98 7.90-8.00223.7-226.53.001.3632.6014.7917.808.07

(1) All test load weights are bone-dry weights.

(2) Allowable tolerance on the test load weights is ±0.10 lbs (0.05 kg).

[80 FR 46767, Aug. 5, 2015; 80 FR 50757, Aug. 21, 2015, as amended at 80 FR 62443, Oct. 16, 2015; 87 FR 33395, June 1, 2022; 87 FR 78820, Dec. 23, 2022; 89 FR 84076, Oct. 21, 2024]

Appendix J3 - Appendix J3 to Subpart B of Part 430—Energy Test Cloth Specifications and Procedures for Determining Correction Coefficients of New Energy Test Cloth Lots

Note:

DOE maintains an historical record of the standard extractor test data and final correction curve coefficients for each approved lot of energy test cloth. These can be accessed through DOE's web page for standards and test procedures for residential clothes washers at DOE's Building Technologies Office Appliance and Equipment Standards website.

1. Objective

This appendix includes the following: (1) Specifications for the energy test cloth to be used for testing clothes washers; (2) procedures for verifying that new lots of energy test cloth meet the defined material specifications; and (3) procedures for developing a set of correction coefficients that correlate the measured remaining moisture content (RMC) values of each new test cloth lot with a set of standard RMC values established as an historical reference point. These correction coefficients are applied to the RMC measurements performed during testing according to appendix J or appendix J2 to this subpart, ensuring that the final corrected RMC measurement for a clothes washer remains independent of the test cloth lot used for testing.

2. Definitions

AHAM means the Association of Home Appliance Manufacturers.

Bone-dry means a condition of a load of test cloth that has been dried in a dryer at maximum temperature for a minimum of 10 minutes, removed and weighed before cool down, and then dried again for 10 minute periods until the final weight change of the load is 1 percent or less.

Lot means a quantity of cloth that has been manufactured with the same batches of cotton and polyester during one continuous process.

Roll means a subset of a lot.

3. Energy Test Cloth Specifications

The energy test cloths and energy stuffer cloths must meet the following specifications:

3.1 The test cloth material should come from a roll of material with a width of approximately 63 inches and approximately 500 yards per roll. However, other sizes may be used if the test cloth material meets the specifications listed in sections 3.2 through 3.6 of this appendix.

3.2 Nominal fabric type. Pure finished bleached cloth made with a momie or granite weave, which is nominally 50 percent cotton and 50 percent polyester.

3.3 Fabric weight. 5.60 ± 0.25 ounces per square yard (190.0 ± 8.4 g/m2).

3.4 Thread count. 65 x 57 per inch (warp × fill), ±2 percent.

3.5 Fiber content of warp and filling yarn. 50 percent ±4 percent cotton, with the balance being polyester, open end spun, 15/1 ±5 percent cotton count blended yarn.

3.6 Water repellent finishes, such as fluoropolymer stain resistant finishes, must not be applied to the test cloth.

3.7. Test cloth dimensions.

3.7.1 Energy test cloth. The energy test cloth must be made from energy test cloth material, as specified in section 3.1 of this appendix, that is 24 ± 1/2 inches by 36 ± 1/2 inches (61.0 ± 1.3 cm by 91.4 ± 1.3 cm) and has been hemmed to 22 ± 1/2 inches by 34 ± 1/2 inches (55.9 ± 1.3 cm by 86.4 ± 1.3 cm) before washing.

3.7.2 Energy stuffer cloth. The energy stuffer cloth must be made from energy test cloth material, as specified in section 3.1 of this appendix, that is 12 ± 1/4 inches by 12 ± 1/4 inches (30.5 ± 0.6 cm by 30.5 ± 0.6 cm) and has been hemmed to 10 ± 1/4 inches by 10 ± 1/4 inches (25.4 ± 0.6 cm by 25.4 ± 0.6 cm) before washing.

3.8 The test cloth must be clean and must not be used for more than 60 test runs (after pre-conditioning as specified in section 5 of this appendix). All test cloth must be permanently marked identifying the lot number of the material. Mixed lots of material must not be used for testing a clothes washer according to appendix J or appendix J2 to this subpart.

4. Equipment Specifications

4.1 Extractor. Use a North Star Engineered Products Inc. (formerly Bock) Model 215 extractor (having a basket diameter of 20 inches, height of 11.5 inches, and volume of 2.09 ft 3), with a variable speed drive (North Star Engineered Products, P.O. Box 5127, Toledo, OH 43611) or an equivalent extractor with same basket design (i.e., diameter, height, volume, and hole configuration) and variable speed drive. Table 4.1 of this appendix shows the extractor spin speed, in revolutions per minute (RPM), that must be used to attain each required g-force level.

Table 4.1—Extractor Spin Speeds for Each Test Condition

“g Force” RPM 100594 ± 1 200840 ± 1 3501,111 ± 1 5001,328 ± 1 6501,514 ± 1

4.2 Bone-dryer. The dryer used for drying the cloth to bone-dry must heat the test cloth and energy stuffer cloths above 210 °F (99 °C).

5. Test Cloth Pre-Conditioning Instructions

Use the following instructions for performing pre-conditioning of new energy test cloths and energy stuffer cloths as specified throughout section 7 and section 8 of this appendix, and before any clothes washer testing using appendix J or appendix J2 to this subpart: Perform five complete wash-rinse-spin cycles, the first two with current AHAM Standard detergent Formula 3 and the last three without detergent. Place the test cloth in a clothes washer set at the maximum water level. Wash the load for ten minutes in soft water (17 ppm hardness or less) using 27.0 grams + 4.0 grams per pound of cloth load of AHAM Standard detergent Formula 3. The wash temperature is to be controlled to 135 °F ± 5 °F (57.2 °C ± 2.8 °C) and the rinse temperature is to be controlled to 60 °F ± 5 °F (15.6 °C ± 2.8 °C). Dry the load to bone-dry between each of the five wash-rinse-spin cycles. The maximum shrinkage after preconditioning must not be more than 5 percent of the length and width. Measure per AATCC Test Method 135-2010 (incorporated by reference; see § 430.3).

6. Extractor Run Instructions

Use the following instructions for performing each of the extractor runs specified throughout section 7 and section 8 of this appendix:

6.1 Test load size. Use a test load size of 8.4 lbs.

6.2 Measure the average RMC for each sample loads as follows:

6.2.1 Dry the test cloth until it is bone-dry according to the definition in section 2 of this appendix. Record the bone-dry weight of the test load (WI).

6.2.2 Prepare the test load for soak by grouping four test cloths into loose bundles. Create the bundles by hanging four cloths vertically from one corner and loosely wrapping the test cloth onto itself to form the bundle. Bundles should be wrapped loosely to ensure consistency of water extraction. Then place the bundles into the water to soak. Eight to nine bundles will be formed depending on the test load. The ninth bundle may not equal four cloths but can incorporate energy stuffer cloths to help offset the size difference.

6.2.3 Soak the test load for 20 minutes in 10 gallons of soft (<17 ppm) water. The entire test load must be submerged. Maintain a water temperature of 100 °F ± 5 °F (37.8 °C ± 2.8 °C) at all times between the start and end of the soak.

6.2.4 Remove the test load and allow each of the test cloth bundles to drain over the water bath for a maximum of 5 seconds.

6.2.5 Manually place the test cloth bundles in the basket of the extractor, distributing them evenly by eye. The draining and loading process must take no longer than 1 minute. Spin the load at a fixed speed corresponding to the intended centripetal acceleration level (measured in units of the acceleration of gravity, g) ± 1g for the intended time period ± 5 seconds. Begin the timer when the extractor meets the required spin speed for each test.

6.2.6 Record the weight of the test load immediately after the completion of the extractor spin cycle (WC).

6.2.7 Calculate the remaining moisture content of the test load as (WC-WI)/WI.

6.2.8 Draining the soak tub is not necessary if the water bath is corrected for water level and temperature before the next extraction.

6.2.9 Drying the test load in between extraction runs is not necessary. However, the bone-dry weight must be checked after every 12 extraction runs to make sure the bone-dry weight is within tolerance (8.4 ± 0.1 lbs). Following this, the test load must be soaked and extracted once before continuing with the remaining extraction runs. Perform this extraction at the same spin speed used for the extraction run prior to checking the bone-dry weight, for a time period of 4 minutes. Either warm or cold soak temperature may be used.

7. Test Cloth Material Verification Procedure

7.1 Material Properties Verification. The test cloth manufacturer must supply a certificate of conformance to ensure that the energy test cloth and stuffer cloth samples used for prequalification testing meet the specifications in section 3 of this appendix. The material properties of one energy test cloth from each of the first, middle, and last rolls must be evaluated as follows, prior to pre-conditioning:

7.1.1 Dimensions. Each hemmed energy test cloth must meet the size specifications in section 3.7.1 of this appendix. Each hemmed stuffer cloth must meet the size specifications in section 3.7.2 of this appendix.

7.1.2 Oil repellency. Perform AATCC Test Method 118-2007, Oil Repellency: Hydrocarbon Resistance Test, (incorporated by reference, see § 430.3), to confirm the absence of ScotchguardTM or other water-repellent finish. An Oil Repellency Grade of 0 (Fails Kaydol) is required.

7.1.3 Absorbency. Perform AATCC Test Method 79-2010, Absorbency of Textiles, (incorporated by reference, see § 430.3), to confirm the absence of ScotchguardTM or other water-repellent finish. The time to absorb one drop must be on the order of 1 second.

7.2 Uniformity Verification. The uniformity of each test cloth lot must be evaluated as follows.

7.2.1 Pre-conditioning. Pre-condition the energy test cloths and energy stuffer cloths used for uniformity verification, as specified in section 5 of this appendix.

7.2.2 Distribution of samples. Test loads must be comprised of cloth from three different rolls from the sample lot. Each roll from a lot must be marked in the run order that it was made. The three rolls are selected based on the run order such that the first, middle, and last rolls are used. As the rolls are cut into cloth, fabric must be selected from the beginning, middle, and end of the roll to create separate loads from each location, for a total of nine sample loads according to Table 7.2.2.

Table 7.2.2—Distribution of Sample Loads for Prequalification Testing

Roll No. Roll location FirstBeginning.
Middle.
End.
MiddleBeginning.
Middle.
End.
LastBeginning.
Middle.
End.

7.2.3 Measure the remaining moisture content of each of the nine sample test loads, as specified in section 6 of this appendix, using a centripetal acceleration of 350g (corresponding to 1111 ± 1 RPM) and a spin duration of 15 minutes ± 5 seconds.

7.2.4 Repeat section 7.2.3 of this appendix an additional two times and calculate the arithmetic average of the three RMC values to determine the average RMC value for each sample load. It is not necessary to dry the load to bone-dry the load before the second and third replications.

7.2.5 Calculate the coefficient of variation (CV) of the nine average RMC values from each sample load. The CV must be less than or equal to 1 percent for the test cloth lot to be considered acceptable and to perform the standard extractor RMC testing.

8. RMC Correction Curve Procedure

8.1 Pre-conditioning. Pre-condition the energy test cloths and energy stuffer cloths used for RMC correction curve measurements, as specified in section 5 of this appendix.

8.2 Distribution of samples. Test loads must be comprised of randomly selected cloth at the beginning, middle and end of a lot. Two test loads may be used, with each load used for half of the total number of required tests. Separate test loads must be used from the loads used for uniformity verification.

8.3 Measure the remaining moisture content of the test load, as specified in section 6 of this appendix at five g-force levels: 100 g, 200 g, 350 g, 500 g, and 650 g, using two different spin times at each g level: 4 minutes and 15 minutes. Table 4.1 of this appendix provides the corresponding spin speeds for each g-force level.

8.4 Repeat section 8.3 of this appendix using soft (<17 ppm) water at 60 °F ± 5 °F (15.6 °C ± 2.8 °C).

8.5 Repeat sections 8.3.3 and 8.3.4 of this appendix an additional two times, so that three replications at each extractor condition are performed. When this procedure is performed in its entirety, a total of 60 extractor RMC test runs are required.

8.6 Average the values of the 3 replications performed for each extractor condition specified in section 8.3 of this appendix.

8.7 Perform a linear least-squares fit to determine coefficients A and B such that the standard RMC values shown in Table 8.7 of this appendix (RMCstandard) are linearly related to the average RMC values calculated in section 8.6 of this appendix (RMCcloth):

RMCstandard ∼ A × RMCcloth + B where A and B are coefficients of the linear least-squares fit.

Table 8.7—Standard RMC Values

“g Force” RMC percentage Warm soak Cold soak 15 min. spin
(percent)
4 min. spin
(percent)
15 min. spin
(percent)
4 min. spin
(percent)
10045.949.949.752.8 20035.740.437.943.1 35029.633.130.735.8 50024.228.725.530.0 65023.026.424.128.0

8.8 Perform an analysis of variance with replication test using two factors, spin speed and lot, to check the interaction of speed and lot. Use the values from section 8.6 of this appendix and Table 8.7 of this appendix in the calculation. The “P” value of the F-statistic for interaction between spin speed and lot in the variance analysis must be greater than or equal to 0.1. If the “P” value is less than 0.1, the test cloth is unacceptable. “P” is a theoretically based measure of interaction based on an analysis of variance.

9. Application of the RMC Correction Curve

9.1 Using the coefficients A and B calculated in section 8.7 of this appendix:

RMCcorr = A × RMC + B

9.2 Apply this RMC correction curve to measured RMC values in appendix J and appendix J2 to this subpart.

[87 span 33403, June 1, 2022, as amended at 87 span 78820, Dec. 23, 2022]

- Appendixes K-L to Subpart B of Part 430 [Reserved]

Appendix M - Appendix M to Subpart B of Part 430—Uniform Test Method for Measuring the Energy Consumption of Central Air Conditioners and Heat Pumps

Note:

Prior to January 1, 2023, if using the appendix M test procedure for representations, including compliance certifications, with respect to the energy use, power, or efficiency of central air conditioners and central air conditioning heat pumps, any such representations must be based on the results of testing pursuant to either this appendix or the procedures in appendix M as it appeared at 10 Cspan part 430, subpart B, in the 10 Cspan parts 200 to 499 edition revised as of January 1, 2022. Any representations made with respect to the energy use or efficiency of such central air conditioners and central air conditioning heat pumps must be in accordance with whichever version is selected. Any representations, including compliance certifications, made with respect to the energy use, power, or efficiency of central air conditioners and central air conditioning heat pumps made on or after January 1, 2023, must be based on the results of testing pursuant the procedures in appendix M1 to this subpart.

On or after July 5, 2017 and prior to January 1, 2023, any representations, including compliance certifications, made with respect to the energy use, power, or efficiency of central air conditioners and central air conditioning heat pumps must be based on the results of testing pursuant to this appendix.

On or after January 1, 2023, any representations, including compliance certifications, made with respect to the energy use, power, or efficiency of central air conditioners and central air conditioning heat pumps must be based on the results of testing pursuant to appendix M1 of this subpart.

1. Scope and Definitions 1.1 Scope

This test procedure provides a method of determining SEER, EER, HSPF and PW,OFF for central air conditioners and central air conditioning heat pumps including the following categories:

(a) Split-system air conditioners, including single-split, multi-head mini-split, multi-split (including VRF), and multi-circuit systems (b) Split-system heat pumps, including single-split, multi-head mini-split, multi-split (including VRF), and multi-circuit systems (c) Single-package air conditioners (d) Single-package heat pumps (e) Small-duct, high-velocity systems (including VRF) (f) Space-constrained products—air conditioners (g) Space-constrained products—heat pumps

For purposes of this appendix, the Department of Energy incorporates by reference specific sections of several industry standards, as listed in § 430.3. In cases where there is a conflict, the language of the test procedure in this appendix takes precedence over the incorporated standards.

All section references refer to sections within this appendix unless otherwise stated.

1.2 Definitions

Airflow-control settings are programmed or wired control system configurations that control a fan to achieve discrete, differing ranges of airflow—often designated for performing a specific function (e.g., cooling, heating, or constant circulation)—without manual adjustment other than interaction with a user-operable control (i.e., a thermostat) that meets the manufacturer specifications for installed-use. For the purposes of this appendix, manufacturer specifications for installed-use are those found in the product literature shipped with the unit.

Air sampling device is an assembly consisting of a manifold with several branch tubes with multiple sampling holes that draws an air sample from a critical location from the unit under test (e.g. indoor air inlet, indoor air outlet, outdoor air inlet, etc.).

Airflow prevention device denotes a device that prevents airflow via natural convection by mechanical means, such as an air damper box, or by means of changes in duct height, such as an upturned duct.

Aspirating psychrometer is a piece of equipment with a monitored airflow section that draws uniform airflow through the measurement section and has probes for measurement of air temperature and humidity.

Blower coil indoor unit means an indoor unit either with an indoor blower housed with the coil or with a separate designated air mover such as a furnace or a modular blower (as defined in appendix AA to the subpart).

Blower coil system refers to a split system that includes one or more blower coil indoor units.

Cased coil means a coil-only indoor unit with external cabinetry.

Coefficient of Performance (COP) means the ratio of the average rate of space heating delivered to the average rate of electrical energy consumed by the heat pump. These rate quantities must be determined from a single test or, if derived via interpolation, must be determined at a single set of operating conditions. COP is a dimensionless quantity. When determined for a ducted coil-only system, COP must include the sections 3.7 and 3.9.1 of this appendix: Default values for the heat output and power input of a fan motor.

Coil-only indoor unit means an indoor unit that is distributed in commerce without an indoor blower or separate designated air mover. A coil-only indoor unit installed in the field relies on a separately-installed furnace or a modular blower for indoor air movement. Coil-only system refers to a system that includes only (one or more) coil-only indoor units.

Condensing unit removes the heat absorbed by the refrigerant to transfer it to the outside environment and consists of an outdoor coil, compressor(s), and air moving device.

Constant-air-volume-rate indoor blower means a fan that varies its operating speed to provide a fixed air-volume-rate from a ducted system.

Continuously recorded, when referring to a dry bulb measurement, dry bulb temperature used for test room control, wet bulb temperature, dew point temperature, or relative humidity measurements, means that the specified value must be sampled at regular intervals that are equal to or less than 15 seconds.

Cooling load factor (CLF) means the ratio having as its numerator the total cooling delivered during a cyclic operating interval consisting of one ON period and one OFF period, and as its denominator the total cooling that would be delivered, given the same ambient conditions, had the unit operated continuously at its steady-state, space-cooling capacity for the same total time (ON + OFF) interval.

Crankcase heater means any electrically powered device or mechanism for intentionally generating heat within and/or around the compressor sump volume. Crankcase heater control may be achieved using a timer or may be based on a change in temperature or some other measurable parameter, such that the crankcase heater is not required to operate continuously. A crankcase heater without controls operates continuously when the compressor is not operating.

Cyclic Test means a test where the unit's compressor is cycled on and off for specific time intervals. A cyclic test provides half the information needed to calculate a degradation coefficient.

Damper box means a short section of duct having an air damper that meets the performance requirements of section 2.5.7 of this appendix.

Degradation coefficient (CD) means a parameter used in calculating the part load factor. The degradation coefficient for cooling is denoted by CD c. The degradation coefficient for heating is denoted by CD h.

Demand-defrost control system means a system that defrosts the heat pump outdoor coil-only when measuring a predetermined degradation of performance. The heat pump's controls either:

(1) Monitor one or more parameters that always vary with the amount of frost accumulated on the outdoor coil (e.g., coil to air differential temperature, coil differential air pressure, outdoor fan power or current, optical sensors) at least once for every ten minutes of compressor ON-time when space heating or

(2) operate as a feedback system that measures the length of the defrost period and adjusts defrost frequency accordingly. In all cases, when the frost parameter(s) reaches a predetermined value, the system initiates a defrost. In a demand-defrost control system, defrosts are terminated based on monitoring a parameter(s) that indicates that frost has been eliminated from the coil. (Note: Systems that vary defrost intervals according to outdoor dry-bulb temperature are not demand-defrost systems.) A demand-defrost control system, which otherwise meets the above requirements, may allow time-initiated defrosts if, and only if, such defrosts occur after 6 hours of compressor operating time.

Design heating requirement (DHR) predicts the space heating load of a residence when subjected to outdoor design conditions. Estimates for the minimum and maximum DHR are provided for six generalized U.S. climatic regions in section 4.2 of this appendix.

Dry-coil tests are cooling mode tests where the wet-bulb temperature of the air supplied to the indoor unit is maintained low enough that no condensate forms on the evaporator coil.

Ducted system means an air conditioner or heat pump that is designed to be permanently installed equipment and delivers conditioned air to the indoor space through a duct(s). The air conditioner or heat pump may be either a split-system or a single-package unit.

Energy efficiency ratio (EER) means the ratio of the average rate of space cooling delivered to the average rate of electrical energy consumed by the air conditioner or heat pump. Determine these rate quantities from a single test or, if derived via interpolation, determine at a single set of operating conditions. EER is expressed in units of

When determined for a ducted coil-only system, EER must include, from this appendix, the section 3.3 and 3.5.1 default values for the heat output and power input of a fan motor.

Evaporator coil means an assembly that absorbs heat from an enclosed space and transfers the heat to a refrigerant.

Heat pump means a kind of central air conditioner that utilizes an indoor conditioning coil, compressor, and refrigerant-to-outdoor air heat exchanger to provide air heating, and may also provide air cooling, air dehumidifying, air humidifying, air circulating, and air cleaning.

Heat pump having a heat comfort controller means a heat pump with controls that can regulate the operation of the electric resistance elements to assure that the air temperature leaving the indoor section does not fall below a specified temperature. Heat pumps that actively regulate the rate of electric resistance heating when operating below the balance point (as the result of a second stage call from the thermostat) but do not operate to maintain a minimum delivery temperature are not considered as having a heat comfort controller.

Heating load factor (HLF) means the ratio having as its numerator the total heating delivered during a cyclic operating interval consisting of one ON period and one OFF period, and its denominator the heating capacity measured at the same test conditions used for the cyclic test, multiplied by the total time interval (ON plus OFF) of the cyclic-test.

Heating season means the months of the year that require heating, e.g., typically, and roughly, October through April.

Heating seasonal performance factor (HSPF) means the total space heating required during the heating season, expressed in Btu, divided by the total electrical energy consumed by the heat pump system during the same season, expressed in watt-hours. The HSPF used to evaluate compliance with 10 Cspan 430.32(c) is based on Region IV and the sampling plan stated in 10 Cspan 429.16(a). HSPF is determined in accordance with appendix M.

Independent coil manufacturer (ICM) means a manufacturer that manufactures indoor units but does not manufacture single-package units or outdoor units.

Indoor unit means a separate assembly of a split system that includes—

(1) An arrangement of refrigerant-to-air heat transfer coil(s) for transfer of heat between the refrigerant and the indoor air,

(2) A condensate drain pan, and may or may not include

(3) Sheet metal or plastic parts not part of external cabinetry to direct/route airflow over the coil(s),

(4) A cooling mode expansion device,

(5) External cabinetry, and

(6) An integrated indoor blower (i.e. a device to move air including its associated motor). A separate designated air mover that may be a furnace or a modular blower (as defined in appendix AA to the subpart) may be considered to be part of the indoor unit. A service coil is not an indoor unit.

Multi-head mini-split system means a split system that has one outdoor unit and that has two or more indoor units connected with a single refrigeration circuit. The indoor units operate in unison in response to a single indoor thermostat.

Multiple-circuit (or multi-circuit) system means a split system that has one outdoor unit and that has two or more indoor units installed on two or more refrigeration circuits such that each refrigeration circuit serves a compressor and one and only one indoor unit, and refrigerant is not shared from circuit to circuit.

Multiple-split (or multi-split) system means a split system that has one outdoor unit and two or more coil-only indoor units and/or blower coil indoor units connected with a single refrigerant circuit. The indoor units operate independently and can condition multiple zones in response to at least two indoor thermostats or temperature sensors. The outdoor unit operates in response to independent operation of the indoor units based on control input of multiple indoor thermostats or temperature sensors, and/or based on refrigeration circuit sensor input (e.g., suction pressure).

Nominal capacity means the capacity that is claimed by the manufacturer on the product name plate. Nominal cooling capacity is approximate to the air conditioner cooling capacity tested at A or A2 condition. Nominal heating capacity is approximate to the heat pump heating capacity tested in H1N test.

Non-ducted indoor unit means an indoor unit that is designed to be permanently installed, mounted on room walls and/or ceilings, and that directly heats or cools air within the conditioned space.

Normalized Gross Indoor Fin Surface (NGIFS) means the gross fin surface area of the indoor unit coil divided by the cooling capacity measured for the A or A2 Test, whichever applies.

Off-mode power consumption means the power consumption when the unit is connected to its main power source but is neither providing cooling nor heating to the building it serves.

Off-mode season means, for central air conditioners other than heat pumps, the shoulder season and the entire heating season; and for heat pumps, the shoulder season only.

Outdoor unit means a separate assembly of a split system that transfers heat between the refrigerant and the outdoor air, and consists of an outdoor coil, compressor(s), an air moving device, and in addition for heat pumps, may include a heating mode expansion device, reversing valve, and/or defrost controls.

Outdoor unit manufacturer (OUM) means a manufacturer of single-package units, outdoor units, and/or both indoor units and outdoor units.

Part-load factor (PLF) means the ratio of the cyclic EER (or COP for heating) to the steady-state EER (or COP), where both EERs (or COPs) are determined based on operation at the same ambient conditions.

Seasonal energy efficiency ratio (SEER) means the total heat removed from the conditioned space during the annual cooling season, expressed in Btu's, divided by the total electrical energy consumed by the central air conditioner or heat pump during the same season, expressed in watt-hours. SEER is determined in accordance with appendix M.

Service coil means an arrangement of refrigerant-to-air heat transfer coil(s), condensate drain pan, sheet metal or plastic parts to direct/route airflow over the coil(s), which may or may not include external cabinetry and/or a cooling mode expansion device, distributed in commerce solely for replacing an uncased coil or cased coil that has already been placed into service, and that has been labeled “for indoor coil replacement only” on the nameplate and in manufacturer technical and product literature. The model number for any service coil must include some mechanism (e.g., an additional letter or number) for differentiating a service coil from a coil intended for an indoor unit.

Shoulder season means the months of the year in between those months that require cooling and those months that require heating, e.g., typically, and roughly, April through May, and September through October.

Single-package unit means any central air conditioner or heat pump that has all major assemblies enclosed in one cabinet.

Single-split system means a split system that has one outdoor unit and one indoor unit connected with a single refrigeration circuit. Small-duct, high-velocity system means a split system for which all indoor units are blower coil indoor units that produce at least 1.2 inches (of water column) of external static pressure when operated at the full-load air volume rate certified by the manufacturer of at least 220 scfm per rated ton of cooling.

Split system means any air conditioner or heat pump that has at least two separate assemblies that are connected with refrigerant piping when installed. One of these assemblies includes an indoor coil that exchanges heat with the indoor air to provide heating or cooling, while one of the others includes an outdoor coil that exchanges heat with the outdoor air. Split systems may be either blower coil systems or coil-only systems.

Standard Air means dry air having a mass density of 0.075 lb/ft 3.

Steady-state test means a test where the test conditions are regulated to remain as constant as possible while the unit operates continuously in the same mode.

Temperature bin means the 5 °F increments that are used to partition the outdoor dry-bulb temperature ranges of the cooling (≥65 °F) and heating (<65 °F) seasons.

Test condition tolerance means the maximum permissible difference between the average value of the measured test parameter and the specified test condition.

Test operating tolerance means the maximum permissible range that a measurement may vary over the specified test interval. The difference between the maximum and minimum sampled values must be less than or equal to the specified test operating tolerance.

Tested combination means a multi-head mini-split, multi-split, or multi-circuit system having the following features:

(1) The system consists of one outdoor unit with one or more compressors matched with between two and five indoor units;

(2) The indoor units must:

(i) Collectively, have a nominal cooling capacity greater than or equal to 95 percent and less than or equal to 105 percent of the nominal cooling capacity of the outdoor unit;

(ii) Each represent the highest sales volume model family, if this is possible while meeting all the requirements of this section. If this is not possible, one or more of the indoor units may represent another indoor model family in order that all the other requirements of this section are met.

(iii) Individually not have a nominal cooling capacity greater than 50 percent of the nominal cooling capacity of the outdoor unit, unless the nominal cooling capacity of the outdoor unit is 24,000 Btu/h or less;

(iv) Operate at fan speeds consistent with manufacturer's specifications; and

(v) All be subject to the same minimum external static pressure requirement while able to produce the same external static pressure at the exit of each outlet plenum when connected in a manifold configuration as required by the test procedure.

(3) Where referenced, “nominal cooling capacity” means, for indoor units, the highest cooling capacity listed in published product literature for 95 °F outdoor dry bulb temperature and 80 °F dry bulb, 67 °F wet bulb indoor conditions, and for outdoor units, the lowest cooling capacity listed in published product literature for these conditions. If incomplete or no operating conditions are published, the highest (for indoor units) or lowest (for outdoor units) such cooling capacity available for sale must be used.

Time-adaptive defrost control system is a demand-defrost control system that measures the length of the prior defrost period(s) and uses that information to automatically determine when to initiate the next defrost cycle.

Time-temperature defrost control systems initiate or evaluate initiating a defrost cycle only when a predetermined cumulative compressor ON-time is obtained. This predetermined ON-time is generally a fixed value (e.g., 30, 45, 90 minutes) although it may vary based on the measured outdoor dry-bulb temperature. The ON-time counter accumulates if controller measurements (e.g., outdoor temperature, evaporator temperature) indicate that frost formation conditions are present, and it is reset/remains at zero at all other times. In one application of the control scheme, a defrost is initiated whenever the counter time equals the predetermined ON-time. The counter is reset when the defrost cycle is completed.

In a second application of the control scheme, one or more parameters are measured (e.g., air and/or refrigerant temperatures) at the predetermined, cumulative, compressor ON-time. A defrost is initiated only if the measured parameter(s) falls within a predetermined range. The ON-time counter is reset regardless of whether or not a defrost is initiated. If systems of this second type use cumulative ON-time intervals of 10 minutes or less, then the heat pump may qualify as having a demand defrost control system (see definition).

Triple-capacity, northern heat pump means a heat pump that provides two stages of cooling and three stages of heating. The two common stages for both the cooling and heating modes are the low capacity stage and the high capacity stage. The additional heating mode stage is the booster capacity stage, which offers the highest heating capacity output for a given set of ambient operating conditions.

Triple-split system means a split system that is composed of three separate assemblies: An outdoor fan coil section, a blower coil indoor unit, and an indoor compressor section.

Two-capacity (or two-stage) compressor system means a central air conditioner or heat pump that has a compressor or a group of compressors operating with only two stages of capacity. For such systems, low capacity means the compressor(s) operating at low stage, or at low load test conditions. The low compressor stage that operates for heating mode tests may be the same or different from the low compressor stage that operates for cooling mode tests. For such systems, high capacity means the compressor(s) operating at high stage, or at full load test conditions.

Two-capacity, northern heat pump means a heat pump that has a factory or field-selectable lock-out feature to prevent space cooling at high-capacity. Two-capacity heat pumps having this feature will typically have two sets of ratings, one with the feature disabled and one with the feature enabled. The heat pump is a two-capacity northern heat pump only when this feature is enabled at all times. The certified indoor coil model number must reflect whether the ratings pertain to the lockout enabled option via the inclusion of an extra identifier, such as “+LO”. When testing as a two-capacity, northern heat pump, the lockout feature must remain enabled for all tests.

Uncased coil means a coil-only indoor unit without external cabinetry.

Variable refrigerant flow (VRF) system means a multi-split system with at least three compressor capacity stages, distributing refrigerant through a piping network to multiple indoor blower coil units each capable of individual zone temperature control, through proprietary zone temperature control devices and a common communications network. Note: Single-phase VRF systems less than 65,000 Btu/h are central air conditioners and central air conditioning heat pumps.

Variable-speed compressor system means a central air conditioner or heat pump that has a compressor that uses a variable-speed drive to vary the compressor speed to achieve variable capacities.

Wet-coil test means a test conducted at test conditions that typically cause water vapor to condense on the test unit evaporator coil.

2. Testing Overview and Conditions

(A) Test VRF systems using AHRI 1230-2010 (incorporated by reference, see § 430.3) and appendix M. Where AHRI 1230-2010 refers to the appendix C therein substitute the provisions of this appendix. In cases where there is a conflict, the language of the test procedure in this appendix takes precedence over AHRI 1230-2010.

For definitions use section 1 of appendix M and section 3 of AHRI 1230-2010 (incorporated by reference, see § 430.3). For rounding requirements, refer to § 430.23(m). For determination of certified ratings, refer to § 429.16 of this chapter.

For test room requirements, refer to section 2.1 of this appendix. For test unit installation requirements refer to sections 2.2.a, 2.2.b, 2.2.c, 2.2.1, 2.2.2, 2.2.3(a), 2.2.3(c), 2.2.4, 2.2.5, and 2.4 to 2.12 of this appendix, and sections 5.1.3 and 5.1.4 of AHRI 1230-2010. The “manufacturer's published instructions,” as stated in section 8.2 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3) and “manufacturer's installation instructions” discussed in this appendix mean the manufacturer's installation instructions that come packaged with or appear in the labels applied to the unit. This does not include online manuals. Installation instructions that appear in the labels applied to the unit take precedence over installation instructions that are shipped with the unit.

For general requirements for the test procedure, refer to section 3.1 of this appendix, except for sections 3.1.3 and 3.1.4, which are requirements for indoor air volume and outdoor air volume. For indoor air volume and outdoor air volume requirements, refer instead to section 6.1.5 (except where section 6.1.5 refers to Table 8, refer instead to Table 4 of this appendix) and 6.1.6 of AHRI 1230-2010.

For the test method, refer to sections 3.3 to 3.5 and 3.7 to 3.13 of this appendix. For cooling mode and heating mode test conditions, refer to section 6.2 of AHRI 1230-2010. For calculations of seasonal performance descriptors, refer to section 4 of this appendix.

(B) For systems other than VRF, only a subset of the sections listed in this test procedure apply when testing and determining represented values for a particular unit. Table 1 shows the sections of the test procedure that apply to each system. This table is meant to assist manufacturers in finding the appropriate sections of the test procedure; the appendix sections rather than the table provide the specific requirements for testing, and given the varied nature of available units, manufacturers are responsible for determining which sections apply to each unit tested based on the unit's characteristics. To use this table, first refer to the sections listed under “all units”. Then refer to additional requirements based on:

(1) System configuration(s),

(2) The compressor staging or modulation capability, and

(3) Any special features.

Testing requirements for space-constrained products do not differ from similar equipment that is not space-constrained and thus are not listed separately in this table. Air conditioners and heat pumps are not listed separately in this table, but heating procedures and calculations apply only to heat pumps.

2.1 Test Room Requirements

a. Test using two side-by-side rooms: An indoor test room and an outdoor test room. For multiple-split, single-zone-multi-coil or multi-circuit air conditioners and heat pumps, however, use as many indoor test rooms as needed to accommodate the total number of indoor units. These rooms must comply with the requirements specified in sections 8.1.2 and 8.1.3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3).

b. Inside these test rooms, use artificial loads during cyclic tests and frost accumulation tests, if needed, to produce stabilized room air temperatures. For one room, select an electric resistance heater(s) having a heating capacity that is approximately equal to the heating capacity of the test unit's condenser. For the second room, select a heater(s) having a capacity that is close to the sensible cooling capacity of the test unit's evaporator. Cycle the heater located in the same room as the test unit evaporator coil ON and OFF when the test unit cycles ON and OFF. Cycle the heater located in the same room as the test unit condensing coil ON and OFF when the test unit cycles OFF and ON.

2.2 Test Unit Installation Requirements

a. Install the unit according to section 8.2 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3), subject to the following additional requirements:

(1) When testing split systems, follow the requirements given in section 6.1.3.5 of AHRI 210/240-2008 (incorporated by reference, see § 430.3). For the vapor refrigerant line(s), use the insulation included with the unit; if no insulation is provided, use insulation meeting the specifications for the insulation in the installation instructions included with the unit by the manufacturer; if no insulation is included with the unit and the installation instructions do not contain provisions for insulating the line(s), fully insulate the vapor refrigerant line(s) with vapor proof insulation having an inside diameter that matches the refrigerant tubing and a nominal thickness of at least 0.5 inches. For the liquid refrigerant line(s), use the insulation included with the unit; if no insulation is provided, use insulation meeting the specifications for the insulation in the installation instructions included with the unit by the manufacturer; if no insulation is included with the unit and the installation instructions do not contain provisions for insulating the line(s), leave the liquid refrigerant line(s) exposed to the air for air conditioners and heat pumps that heat and cool; or, for heating-only heat pumps, insulate the liquid refrigerant line(s) with insulation having an inside diameter that matches the refrigerant tubing and a nominal thickness of at least 0.5 inches. However, these requirements do not take priority over instructions for application of insulation for the purpose of improving refrigerant temperature measurement accuracy as required by sections 2.10.2 and 2.10.3 of this appendix. Insulation must be the same for the cooling and heating tests.

(2) When testing split systems, if the indoor unit does not ship with a cooling mode expansion device, test the system using the device as specified in the installation instructions provided with the indoor unit. If none is specified, test the system using a fixed orifice or piston type expansion device that is sized appropriately for the system.

(3) When testing triple-split systems (see section 1.2 of this appendix, Definitions), use the tubing length specified in section 6.1.3.5 of AHRI 210/240-2008 (incorporated by reference, see § 430.3) to connect the outdoor coil, indoor compressor section, and indoor coil while still meeting the requirement of exposing 10 feet of the tubing to outside conditions;

(4) When testing split systems having multiple indoor coils, connect each indoor blower coil unit to the outdoor unit using:

(a) 25 feet of tubing, or

(b) tubing furnished by the manufacturer, whichever is longer.

At least 10 feet of the system interconnection tubing shall be exposed to the outside conditions. If they are needed to make a secondary measurement of capacity or for verification of refrigerant charge, install refrigerant pressure measuring instruments as described in section 8.2.5 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3). Section 2.10 of this appendix specifies which secondary methods require refrigerant pressure measurements and section 2.2.5.5 of this appendix discusses use of pressure measurements to verify charge. At a minimum, insulate the low-pressure line(s) of a split system with insulation having an inside diameter that matches the refrigerant tubing and a nominal thickness of 0.5 inch.

b. For units designed for both horizontal and vertical installation or for both up-flow and down-flow vertical installations, use the orientation for testing specified by the manufacturer in the certification report. Conduct testing with the following installed:

(1) The most restrictive filter(s);

(2) Supplementary heating coils; and

(3) Other equipment specified as part of the unit, including all hardware used by a heat comfort controller if so equipped (see section 1 of this appendix, Definitions). For small-duct, high-velocity systems, configure all balance dampers or restrictor devices on or inside the unit to fully open or lowest restriction.

c. Testing a ducted unit without having an indoor air filter installed is permissible as long as the minimum external static pressure requirement is adjusted as stated in Table 4, note 3 (see section 3.1.4 of this appendix). Except as noted in section 3.1.10 of this appendix, prevent the indoor air supplementary heating coils from operating during all tests. For uncased coils, create an enclosure using 1 inch fiberglass foil-faced ductboard having a nominal density of 6 pounds per cubic foot. Or alternatively, construct an enclosure using sheet metal or a similar material and insulating material having a thermal resistance (“R” value) between 4 and 6 hr·ft 2· °F/Btu. Size the enclosure and seal between the coil and/or drainage pan and the interior of the enclosure as specified in installation instructions shipped with the unit. Also seal between the plenum and inlet and outlet ducts.

d. When testing a coil-only system, install a toroidal-type transformer to power the system's low-voltage components, complying with any additional requirements for the transformer mentioned in the installation manuals included with the unit by the system manufacturer. If the installation manuals do not provide specifications for the transformer, use a transformer having the following features:

(1) A nominal volt-amp rating such that the transformer is loaded between 25 and 90 percent of this rating for the highest level of power measured during the off mode test (section 3.13 of this appendix);

(2) Designed to operate with a primary input of 230 V, single phase, 60 Hz; and

(3) That provides an output voltage that is within the specified range for each low-voltage component. Include the power consumption of the components connected to the transformer as part of the total system power consumption during the off mode tests; do not include the power consumed by the transformer when no load is connected to it.

e. Test an outdoor unit with no match (i.e., that is not distributed in commerce with any indoor units) using a coil-only indoor unit with a single cooling air volume rate whose coil has:

(1) Round tubes of outer diameter no less than 0.375 inches, and

(2) a normalized gross indoor fin surface (NGIFS) no greater than 1.0 square inches per British thermal unit per hour (sq. in./Btu/hr). NGIFS is calculated as follows:

NGIFS = 2 × Lf × Wf × Nf ÷ Q c(95)

where: Lf = Indoor coil fin length in inches, also height of the coil transverse to the tubes. Wf = Indoor coil fin width in inches, also depth of the coil. Nf = Number of fins. Q c(95) = the measured space cooling capacity of the tested outdoor unit/indoor unit combination as determined from the A2 or A Test whichever applies, Btu/h.

ƒ. If the outdoor unit or the outdoor portion of a single-package unit has a drain pan heater to prevent freezing of defrost water, the heater shall be energized, subject to control to de-energize it when not needed by the heater's thermostat or the unit's control system, for all tests.

g. If pressure measurement devices are connected to a cooling/heating heat pump refrigerant circuit, the refrigerant charge Mt that could potentially transfer out of the connected pressure measurement systems (transducers, gauges, connections, and lines) between operating modes must be less than 2 percent of the factory refrigerant charge listed on the nameplate of the outdoor unit. If the outdoor unit nameplate has no listed refrigerant charge, or the heat pump is shipped without a refrigerant charge, use a factory refrigerant charge equal to 30 ounces per ton of certified cooling capacity. Use Equation 2.2-1 to calculate Mt for heat pumps that have a single expansion device located in the outdoor unit to serve each indoor unit, and use Equation 2.2-2 to calculate Mt for heat pumps that have two expansion devices per indoor unit.

where: Vi (i=2,3,4. . .) = the internal volume of the pressure measurement system (pressure lines, fittings, and gauge and/or transducer) at the location i (as indicated in Table 2), (cubic inches) fi (i=5,6) = 0 if the pressure measurement system is pitched upwards from the pressure tap location to the gauge or transducer, 1 if it is not. r = the density associated with liquid refrigerant at 100 °F bubble point conditions (ounces per cubic inch)

Table 2—Pressure Measurement Locations

Location Compressor Discharge1 Between Outdoor Coil and Outdoor Expansion Valve(s)2 Liquid Service Valve3 Indoor Coil Inlet4 Indoor Coil Outlet5 Common Suction Port (i.e. vapor service valve)6 Compressor Suction7

Calculate the internal volume of each pressure measurement system using internal volume reported for pressure transducers and gauges in product literature, if available. If such information is not available, use the value of 0.1 cubic inches internal volume for each pressure transducer, and 0.2 cubic inches for each pressure gauge.

In addition, for heat pumps that have a single expansion device located in the outdoor unit to serve each indoor unit, the internal volume of the pressure system at location 2 (as indicated in Table 2) must be no more than 1 cubic inch. Once the pressure measurement lines are set up, no change should be made until all tests are finished.

2.2.1 Defrost Control Settings

Set heat pump defrost controls at the normal settings which most typify those encountered in generalized climatic region IV. (Refer to Figure 1 and Table 20 of section 4.2 of this appendix for information on region IV.) For heat pumps that use a time-adaptive defrost control system (see section 1.2 of this appendix, Definitions), the manufacturer must specify in the certification report the frosting interval to be used during frost accumulation tests and provide the procedure for manually initiating the defrost at the specified time.

2.2.2 Special Requirements for Units Having a Multiple-Speed Outdoor Fan

Configure the multiple-speed outdoor fan according to the installation manual included with the unit by the manufacturer, and thereafter, leave it unchanged for all tests. The controls of the unit must regulate the operation of the outdoor fan during all lab tests except dry coil cooling mode tests. For dry coil cooling mode tests, the outdoor fan must operate at the same speed used during the required wet coil test conducted at the same outdoor test conditions.

2.2.3 Special Requirements for Multi-Split Air Conditioners and Heat Pumps and Ducted Systems Using a Single Indoor Section Containing Multiple Indoor Blowers That Would Normally Operate Using Two or More Indoor Thermostats

Because these systems will have more than one indoor blower and possibly multiple outdoor fans and compressor systems, references in this test procedure to a singular indoor blower, outdoor fan, and/or compressor means all indoor blowers, all outdoor fans, and all compressor systems that are energized during the test.

a. Additional requirements for multi-split air conditioners and heat pumps. For any test where the system is operated at part load (i.e., one or more compressors “off”, operating at the intermediate or minimum compressor speed, or at low compressor capacity), record the indoor coil(s) that are not providing heating or cooling during the test. For variable-speed systems, the manufacturer must designate in the certification report at least one indoor unit that is not providing heating or cooling for all tests conducted at minimum compressor speed.

b. Additional requirements for ducted split systems with a single indoor unit containing multiple indoor blowers (or for single-package units with an indoor section containing multiple indoor blowers) where the indoor blowers are designed to cycle on and off independently of one another and are not controlled such that all indoor blowers are modulated to always operate at the same air volume rate or speed. For any test where the system is operated at its lowest capacity—i.e., the lowest total air volume rate allowed when operating the single-speed compressor or when operating at low compressor capacity—indoor blowers accounting for at least one-third of the full-load air volume rate must be turned off unless prevented by the controls of the unit. In such cases, turn off as many indoor blowers as permitted by the unit's controls. Where more than one option exists for meeting this “off” requirement, the manufacturer shall indicate in its certification report which indoor blower(s) are turned off. The chosen configuration shall remain unchanged for all tests conducted at the same lowest capacity configuration. For any indoor coil turned off during a test, cease forced airflow through any outlet duct connected to a switched-off indoor blower.

c. For test setups where the laboratory's physical limitations requires use of more than the required line length of 25 feet as listed in section 2.2.a(4) of this appendix, then the actual refrigerant line length used by the laboratory may exceed the required length and the refrigerant line length correction factors in Table 4 of AHRI 1230-2010 are applied to the cooling capacity measured for each cooling mode test.

2.2.4 Wet-Bulb Temperature Requirements for the Air Entering the Indoor and Outdoor Coils 2.2.4.1 Cooling Mode Tests

For wet-coil cooling mode tests, regulate the water vapor content of the air entering the indoor unit so that the wet-bulb temperature is as listed in Tables 5 to 8. As noted in these same tables, achieve a wet-bulb temperature during dry-coil cooling mode tests that results in no condensate forming on the indoor coil. Controlling the water vapor content of the air entering the outdoor side of the unit is not required for cooling mode tests except when testing:

(1) Units that reject condensate to the outdoor coil during wet coil tests. Tables 5-8 list the applicable wet-bulb temperatures.

(2) Single-package units where all or part of the indoor section is located in the outdoor test room. The average dew point temperature of the air entering the outdoor coil during wet coil tests must be within ±3.0 °F of the average dew point temperature of the air entering the indoor coil over the 30-minute data collection interval described in section 3.3 of this appendix. For dry coil tests on such units, it may be necessary to limit the moisture content of the air entering the outdoor coil of the unit to meet the requirements of section 3.4 of this appendix.

2.2.4.2 Heating Mode Tests

For heating mode tests, regulate the water vapor content of the air entering the outdoor unit to the applicable wet-bulb temperature listed in Tables 12 to 15. The wet-bulb temperature entering the indoor side of the heat pump must not exceed 60 °F. Additionally, if the Outdoor Air Enthalpy test method (section 2.10.1 of this appendix) is used while testing a single-package heat pump where all or part of the outdoor section is located in the indoor test room, adjust the wet-bulb temperature for the air entering the indoor side to yield an indoor-side dew point temperature that is as close as reasonably possible to the dew point temperature of the outdoor-side entering air.

2.2.5 Additional Refrigerant Charging Requirements 2.2.5.1 Instructions To Use for Charging

a. Where the manufacturer's installation instructions contain two sets of refrigerant charging criteria, one for field installations and one for lab testing, use the field installation criteria.

b. For systems consisting of an outdoor unit manufacturer's outdoor section and indoor section with differing charging procedures, adjust the refrigerant charge per the outdoor installation instructions.

c. For systems consisting of an outdoor unit manufacturer's outdoor unit and an independent coil manufacturer's indoor unit with differing charging procedures, adjust the refrigerant charge per the indoor unit's installation instructions. If instructions are provided only with the outdoor unit or are provided only with an independent coil manufacturer's indoor unit, then use the provided instructions.

2.2.5.2 Test(s) To Use for Charging

a. Use the tests or operating conditions specified in the manufacturer's installation instructions for charging. The manufacturer's installation instructions may specify use of tests other than the A or A2 test for charging, but, unless the unit is a heating-only heat pump, the air volume rate must be determined by the A or A2 test as specified in section 3.1 of this appendix.

b. If the manufacturer's installation instructions do not specify a test or operating conditions for charging or there are no manufacturer's instructions, use the following test(s):

(1) For air conditioners or cooling and heating heat pumps, use the A or A2 test.

(2) For cooling and heating heat pumps that do not operate in the H1 or H12 test (e.g. due to shut down by the unit limiting devices) when tested using the charge determined at the A or A2 test, and for heating-only heat pumps, use the H1 or H12 test.

2.2.5.3 Parameters To Set and Their Target Values

a. Consult the manufacturer's installation instructions regarding which parameters (e.g., superheat) to set and their target values. If the instructions provide ranges of values, select target values equal to the midpoints of the provided ranges.

b. In the event of conflicting information between charging instructions (i.e., multiple conditions given for charge adjustment where all conditions specified cannot be met), follow the following hierarchy.

(1) For fixed orifice systems:

(i) Superheat

(ii) High side pressure or corresponding saturation or dew-point temperature

(iii) Low side pressure or corresponding saturation or dew-point temperature

(iv) Low side temperature

(v) High side temperature

(vi) Charge weight

(2) For expansion valve systems:

(i) Subcooling

(ii) High side pressure or corresponding saturation or dew-point temperature

(iii) Low side pressure or corresponding saturation or dew-point temperature

(iv) Approach temperature (difference between temperature of liquid leaving condenser and condenser average inlet air temperature)

(v) Charge weight

c. If there are no installation instructions and/or they do not provide parameters and target values, set superheat to a target value of 12 °F for fixed orifice systems or set subcooling to a target value of 10 °F for expansion valve systems.

2.2.5.4 Charging Tolerances

a. If the manufacturer's installation instructions specify tolerances on target values for the charging parameters, set the values within these tolerances.

b. Otherwise, set parameter values within the following test condition tolerances for the different charging parameters:

1. Superheat: ± 2.0 °F 2. Subcooling: ± 2.0 °F 3. High side pressure or corresponding saturation or dew point temperature: ± 4.0 psi or ± 1.0 °F 4. Low side pressure or corresponding saturation or dew point temperature: ± 2.0 psi or ± 0.8 °F 5. High side temperature: ±2.0 °F 6. Low side temperature: ±2.0 °F 7. Approach temperature: ± 1.0 °F 8. Charge weight: ± 2.0 ounce 2.2.5.5 Special Charging Instructions a. Cooling and Heating Heat Pumps

If, using the initial charge set in the A or A2 test, the conditions are not within the range specified in manufacturer's installation instructions for the H1 or H12 test, make as small as possible an adjustment to obtain conditions for this test in the specified range. After this adjustment, recheck conditions in the A or A2 test to confirm that they are still within the specified range for the A or A2 test.

b. Single-Package Systems

Unless otherwise directed by the manufacturer's installation instructions, install one or more refrigerant line pressure gauges during the setup of the unit, located depending on the parameters used to verify or set charge, as described:

(1) Install a pressure gauge at the location of the service valve on the liquid line if charging is on the basis of subcooling, or high side pressure or corresponding saturation or dew point temperature;

(2) Install a pressure gauge at the location of the service valve on the suction line if charging is on the basis of superheat, or low side pressure or corresponding saturation or dew point temperature.

Use methods for installing pressure gauge(s) at the required location(s) as indicated in manufacturer's instructions if specified.

2.2.5.6 Near-Azeotropic and Zeotropic Refrigerants.

Perform charging of near-azeotropic and zeotropic refrigerants only with refrigerant in the liquid state.

2.2.5.7 Adjustment of Charge Between Tests.

After charging the system as described in this test procedure, use the set refrigerant charge for all tests used to determine performance. Do not adjust the refrigerant charge at any point during testing. If measurements indicate that refrigerant charge has leaked during the test, repair the refrigerant leak, repeat any necessary set-up steps, and repeat all tests.

2.3 Indoor Air Volume Rates.

If a unit's controls allow for overspeeding the indoor blower (usually on a temporary basis), take the necessary steps to prevent overspeeding during all tests.

2.3.1 Cooling Tests

a. Set indoor blower airflow-control settings (e.g., fan motor pin settings, fan motor speed) according to the requirements that are specified in section 3.1.4 of this appendix.

b. Express the Cooling full-load air volume rate, the Cooling Minimum Air Volume Rate, and the Cooling Intermediate Air Volume Rate in terms of standard air.

2.3.2 Heating Tests

a. Set indoor blower airflow-control settings (e.g., fan motor pin settings, fan motor speed) according to the requirements that are specified in section 3.1.4 of this appendix.

b. Express the heating full-load air volume rate, the heating minimum air volume rate, the heating intermediate air volume rate, and the heating nominal air volume rate in terms of standard air.

2.4 Indoor Coil Inlet and Outlet Duct Connections

Insulate and/or construct the outlet plenum as described in section 2.4.1 of this appendix and, if installed, the inlet plenum described in section 2.4.2 of this appendix with thermal insulation having a nominal overall resistance (R-value) of at least 19 hr·ft 2· °F/Btu.

2.4.1 Outlet Plenum for the Indoor Unit

a. Attach a plenum to the outlet of the indoor coil. (Note: For some packaged systems, the indoor coil may be located in the outdoor test room.)

b. For systems having multiple indoor coils, or multiple indoor blowers within a single indoor section, attach a plenum to each indoor coil or indoor blower outlet. In order to reduce the number of required airflow measurement apparati (section 2.6 of this appendix), each such apparatus may serve multiple outlet plenums connected to a single common duct leading to the apparatus. More than one indoor test room may be used, which may use one or more common ducts leading to one or more airflow measurement apparati within each test room that contains multiple indoor coils. At the plane where each plenum enters a common duct, install an adjustable airflow damper and use it to equalize the static pressure in each plenum. Each outlet air temperature grid (section 2.5.4 of this appendix) and airflow measuring apparatus are located downstream of the inlet(s) to the common duct. For multiple-circuit (or multi-circuit) systems for which each indoor coil outlet is measured separately and its outlet plenum is not connected to a common duct connecting multiple outlet plenums, the outlet air temperature grid and airflow measuring apparatus must be installed at each outlet plenum.

c. For small-duct, high-velocity systems, install an outlet plenum that has a diameter that is equal to or less than the value listed in Table 3. The limit depends only on the Cooling full-load air volume rate (see section 3.1.4.1.1 of this appendix) and is effective regardless of the flange dimensions on the outlet of the unit (or an air supply plenum adapter accessory, if installed in accordance with the manufacturer's installation instructions).

d. Add a static pressure tap to each face of the (each) outlet plenum, if rectangular, or at four evenly distributed locations along the circumference of an oval or round plenum. Create a manifold that connects the four static pressure taps. Figure 9 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3) shows allowed options for the manifold configuration. The cross-sectional dimensions of plenum shall be equal to the dimensions of the indoor unit outlet. See Figures 7a, 7b, and 7c of ANSI/ASHRAE 37-2009 for the minimum length of the (each) outlet plenum and the locations for adding the static pressure taps for ducted blower coil indoor units and single-package systems. See Figure 8 of ANSI/ASHRAE 37-2009 for coil-only indoor units.

Table 3—Size of Outlet Plenum for Small-Duct High-Velocity Indoor Units

Cooling full-load
air volume rate
(scfm)
Maximum
diameter *
of outlet
plenum
(inches)
≤5006 501 to 7007 701 to 9008 901 to 11009 1101 to 140010 1401 to 175011

* If the outlet plenum is rectangular, calculate its equivalent diameter using (4A/P,) where A is the cross-sectional area and P is the perimeter of the rectangular plenum, and compare it to the listed maximum diameter.

2.4.2 Inlet Plenum for the Indoor Unit

Install an inlet plenum when testing a coil-only indoor unit, a ducted blower coil indoor unit, or a single-package system. See Figures 7b and 7c of ANSI/ASHRAE 37-2009 for cross-sectional dimensions, the minimum length of the inlet plenum, and the locations of the static-pressure taps for ducted blower coil indoor units and single-package systems. See Figure 8 of ANSI/ASHRAE 37-2009 for coil-only indoor units. The inlet plenum duct size shall equal the size of the inlet opening of the air-handling (blower coil) unit or furnace. For a ducted blower coil indoor unit the set up may omit the inlet plenum if an inlet airflow prevention device is installed with a straight internally unobstructed duct on its outlet end with a minimum length equal to 1.5 times the square root of the cross-sectional area of the indoor unit inlet. See section 2.5.1.2 of this appendix for requirements for the locations of static pressure taps built into the inlet airflow prevention device. For all of these arrangements, make a manifold that connects the four static-pressure taps using one of the three configurations specified in section 2.4.1.d of this appendix. Never use an inlet plenum when testing non-ducted indoor units.

2.5 Indoor Coil Air Property Measurements and Airflow Prevention Devices

Follow instructions for indoor coil air property measurements as described in section 2.14 of this appendix, unless otherwise instructed in this section.

a. Measure the dry-bulb temperature and water vapor content of the air entering and leaving the indoor coil. If needed, use an air sampling device to divert air to a sensor(s) that measures the water vapor content of the air. See section 5.3 of ANSI/ASHRAE 41.1-2013 (incorporated by reference, see § 430.3) for guidance on constructing an air sampling device. No part of the air sampling device or the tubing transferring the sampled air to the sensor shall be within two inches of the test chamber floor, and the transfer tubing shall be insulated. The sampling device may also be used for measurement of dry bulb temperature by transferring the sampled air to a remotely located sensor(s). The air sampling device and the remotely located temperature sensor(s) may be used to determine the entering air dry bulb temperature during any test. The air sampling device and the remotely located sensor(s) may be used to determine the leaving air dry bulb temperature for all tests except:

(1) Cyclic tests; and

(2) Frost accumulation tests.

b. Install grids of temperature sensors to measure dry bulb temperatures of both the entering and leaving airstreams of the indoor unit. These grids of dry bulb temperature sensors may be used to measure average dry bulb temperature entering and leaving the indoor unit in all cases (as an alternative to the dry bulb sensor measuring the sampled air). The leaving airstream grid is required for measurement of average dry bulb temperature leaving the indoor unit for the two special cases noted above. The grids are also required to measure the air temperature distribution of the entering and leaving airstreams as described in sections 3.1.8 and 3.1.9 of this appendix. Two such grids may applied as a thermopile, to directly obtain the average temperature difference rather than directly measuring both entering and leaving average temperatures.

c. Use of airflow prevention devices. Use an inlet and outlet air damper box, or use an inlet upturned duct and an outlet air damper box when conducting one or both of the cyclic tests listed in sections 3.2 and 3.6 of this appendix on ducted systems. If not conducting any cyclic tests, an outlet air damper box is required when testing ducted and non-ducted heat pumps that cycle off the indoor blower during defrost cycles and there is no other means for preventing natural or forced convection through the indoor unit when the indoor blower is off. Never use an inlet damper box or an inlet upturned duct when testing non-ducted indoor units. An inlet upturned duct is a length of ductwork installed upstream from the inlet such that the indoor duct inlet opening, facing upwards, is sufficiently high to prevent natural convection transfer out of the duct. If an inlet upturned duct is used, install a dry bulb temperature sensor near the inlet opening of the indoor duct at a centerline location not higher than the lowest elevation of the duct edges at the inlet, and ensure that any pair of 5-minute averages of the dry bulb temperature at this location, measured at least every minute during the compressor OFF period of the cyclic test, do not differ by more than 1.0 °F.

2.5.1 Test Set-Up on the Inlet Side of the Indoor Coil: For Cases Where the Inlet Airflow Prevention Device Is Installed

a. Install an airflow prevention device as specified in section 2.5.1.1 or 2.5.1.2 of this appendix, whichever applies.

b. For an inlet damper box, locate the grid of entering air dry-bulb temperature sensors, if used, and the air sampling device, or the sensor used to measure the water vapor content of the inlet air, at a location immediately upstream of the damper box inlet. For an inlet upturned duct, locate the grid of entering air dry-bulb temperature sensors, if used, and the air sampling device, or the sensor used to measure the water vapor content of the inlet air, at a location at least one foot downstream from the beginning of the insulated portion of the duct but before the static pressure measurement.

2.5.1.1 If the Section 2.4.2 Inlet Plenum Is Installed

Construct the airflow prevention device having a cross-sectional flow area equal to or greater than the flow area of the inlet plenum. Install the airflow prevention device upstream of the inlet plenum and construct ductwork connecting it to the inlet plenum. If needed, use an adaptor plate or a transition duct section to connect the airflow prevention device with the inlet plenum. Insulate the ductwork and inlet plenum with thermal insulation that has a nominal overall resistance (R-value) of at least 19 hr · ft 2 · °F/Btu.

2.5.1.2 If the Section 2.4.2 Inlet Plenum Is Not Installed

Construct the airflow prevention device having a cross-sectional flow area equal to or greater than the flow area of the air inlet of the indoor unit. Install the airflow prevention device immediately upstream of the inlet of the indoor unit. If needed, use an adaptor plate or a short transition duct section to connect the airflow prevention device with the unit's air inlet. Add static pressure taps at the center of each face of a rectangular airflow prevention device, or at four evenly distributed locations along the circumference of an oval or round airflow prevention device. Locate the pressure taps at a distance from the indoor unit inlet equal to 0.5 times the square root of the cross sectional area of the indoor unit inlet. This location must be between the damper and the inlet of the indoor unit, if a damper is used. Make a manifold that connects the four static pressure taps using one of the configurations shown in Figure 9 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3). Insulate the ductwork with thermal insulation that has a nominal overall resistance (R-value) of at least 19 hr · ft 2 · °F/Btu.

2.5.2 Test Set-Up on the Inlet Side of the Indoor Unit: for Cases Where No Airflow Prevention Device is Installed

If using the section 2.4.2 inlet plenum and a grid of dry bulb temperature sensors, mount the grid at a location upstream of the static pressure taps described in section 2.4.2 of this appendix, preferably at the entrance plane of the inlet plenum. If the section 2.4.2 inlet plenum is not used (i.e. for non-ducted units) locate a grid approximately 6 inches upstream of the indoor unit inlet. In the case of a system having multiple non-ducted indoor units, do this for each indoor unit. Position an air sampling device, or the sensor used to measure the water vapor content of the inlet air, immediately upstream of the (each) entering air dry-bulb temperature sensor grid. If a grid of sensors is not used, position the entering air sampling device (or the sensor used to measure the water vapor content of the inlet air) as if the grid were present.

2.5.3 Indoor Coil Static Pressure Difference Measurement

Fabricate pressure taps meeting all requirements described in section 6.5.2 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3) and illustrated in Figure 2A of AMCA 210-2007 (incorporated by reference, see § 430.3), however, if adhering strictly to the description in section 6.5.2 of ANSI/ASHRAE 37-2009, the minimum pressure tap length of 2.5 times the inner diameter of Figure 2A of AMCA 210-2007 is waived. Use a differential pressure measuring instrument that is accurate to within ±0.01 inches of water and has a resolution of at least 0.01 inches of water to measure the static pressure difference between the indoor coil air inlet and outlet. Connect one side of the differential pressure instrument to the manifolded pressure taps installed in the outlet plenum. Connect the other side of the instrument to the manifolded pressure taps located in either the inlet plenum or incorporated within the airflow prevention device. For non-ducted indoor units that are tested with multiple outlet plenums, measure the static pressure within each outlet plenum relative to the surrounding atmosphere.

2.5.4 Test Set-Up on the Outlet Side of the Indoor Coil

a. Install an interconnecting duct between the outlet plenum described in section 2.4.1 of this appendix and the airflow measuring apparatus described below in section 2.6 of this appendix. The cross-sectional flow area of the interconnecting duct must be equal to or greater than the flow area of the outlet plenum or the common duct used when testing non-ducted units having multiple indoor coils. If needed, use adaptor plates or transition duct sections to allow the connections. To minimize leakage, tape joints within the interconnecting duct (and the outlet plenum). Construct or insulate the entire flow section with thermal insulation having a nominal overall resistance (R-value) of at least 19 hr·ft 2· °F/Btu.

b. Install a grid(s) of dry-bulb temperature sensors inside the interconnecting duct. Also, install an air sampling device, or the sensor(s) used to measure the water vapor content of the outlet air, inside the interconnecting duct. Locate the dry-bulb temperature grid(s) upstream of the air sampling device (or the in-duct sensor(s) used to measure the water vapor content of the outlet air). Turn off the sampler fan motor during the cyclic tests. Air leaving an indoor unit that is sampled by an air sampling device for remote water-vapor-content measurement must be returned to the interconnecting duct at a location:

(1) Downstream of the air sampling device;

(2) On the same side of the outlet air damper as the air sampling device; and

(3) Upstream of the section 2.6 airflow measuring apparatus.

2.5.4.1 Outlet Air Damper Box Placement and Requirements

If using an outlet air damper box (see section 2.5 of this appendix), the leakage rate from the combination of the outlet plenum, the closed damper, and the duct section that connects these two components must not exceed 20 cubic feet per minute when a negative pressure of 1 inch of water column is maintained at the plenum's inlet.

2.5.4.2 Procedures To Minimize Temperature Maldistribution

Use these procedures if necessary to correct temperature maldistributions. Install a mixing device(s) upstream of the outlet air, dry-bulb temperature grid (but downstream of the outlet plenum static pressure taps). Use a perforated screen located between the mixing device and the dry-bulb temperature grid, with a maximum open area of 40 percent. One or both items should help to meet the maximum outlet air temperature distribution specified in section 3.1.8 of this appendix. Mixing devices are described in sections 5.3.2 and 5.3.3 of ANSI/ASHRAE 41.1-2013 and section 5.2.2 of ASHRAE 41.2-1987 (RA 1992) (incorporated by reference, see § 430.3).

2.5.4.3 Minimizing Air Leakage

For small-duct, high-velocity systems, install an air damper near the end of the interconnecting duct, just prior to the transition to the airflow measuring apparatus of section 2.6 of this appendix. To minimize air leakage, adjust this damper such that the pressure in the receiving chamber of the airflow measuring apparatus is no more than 0.5 inch of water higher than the surrounding test room ambient. If applicable, in lieu of installing a separate damper, use the outlet air damper box of sections 2.5 and 2.5.4.1 of this appendix if it allows variable positioning. Also apply these steps to any conventional indoor blower unit that creates a static pressure within the receiving chamber of the airflow measuring apparatus that exceeds the test room ambient pressure by more than 0.5 inches of water column.

2.5.5 Dry Bulb Temperature Measurement

a. Measure dry bulb temperatures as specified in sections 4, 5.3, 6, and 7 of ANSI/ASHRAE 41.1-2013 (incorporated by reference, see § 430.3).

b. Distribute the sensors of a dry-bulb temperature grid over the entire flow area. The required minimum is 9 sensors per grid.

2.5.6 Water Vapor Content Measurement

Determine water vapor content by measuring dry-bulb temperature combined with the air wet-bulb temperature, dew point temperature, or relative humidity. If used, construct and apply wet-bulb temperature sensors as specified in sections 4, 5, 6, 7.2, 7.3, and 7.4 of ASHRAE 41.6-2014 (incorporated by reference, see § 430.3). The temperature sensor (wick removed) must be accurate to within ±0.2 °F. If used, apply dew point hygrometers as specified in sections 4, 5, 6, 7.1, and 7.4 of ASHRAE 41.6-2014 (incorporated by reference, see § 430.3). The dew point hygrometers must be accurate to within ±0.4 °F when operated at conditions that result in the evaluation of dew points above 35 °F. If used, a relative humidity (RH) meter must be accurate to within ±0.7% RH. Other means to determine the psychrometric state of air may be used as long as the measurement accuracy is equivalent to or better than the accuracy achieved from using a wet-bulb temperature sensor that meets the above specifications.

2.5.7 Air Damper Box Performance Requirements

If used (see section 2.5 of this appendix), the air damper box(es) must be capable of being completely opened or completely closed within 10 seconds for each action.

2.6 Airflow Measuring Apparatus

a. Fabricate and operate an airflow measuring apparatus as specified in section 6.2 and 6.3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3). Place the static pressure taps and position the diffusion baffle (settling means) relative to the chamber inlet as indicated in Figure 12 of AMCA 210-2007 and/or Figure 14 of ASHRAE 41.2-1987 (RA 1992) (incorporated by reference, see § 430.3). When measuring the static pressure difference across nozzles and/or velocity pressure at nozzle throats using electronic pressure transducers and a data acquisition system, if high frequency fluctuations cause measurement variations to exceed the test tolerance limits specified in section 9.2 and Table 2 of ANSI/ASHRAE 37-2009, dampen the measurement system such that the time constant associated with response to a step change in measurement (time for the response to change 63% of the way from the initial output to the final output) is no longer than five seconds.

b. Connect the airflow measuring apparatus to the interconnecting duct section described in section 2.5.4 of this appendix. See sections 6.1.1, 6.1.2, and 6.1.4, and Figures 1, 2, and 4 of ANSI/ASHRAE 37-2009; and Figures D1, D2, and D4 of AHRI 210/240-2008 (incorporated by reference, see § 430.3) for illustrative examples of how the test apparatus may be applied within a complete laboratory set-up. Instead of following one of these examples, an alternative set-up may be used to handle the air leaving the airflow measuring apparatus and to supply properly conditioned air to the test unit's inlet. The alternative set-up, however, must not interfere with the prescribed means for measuring airflow rate, inlet and outlet air temperatures, inlet and outlet water vapor contents, and external static pressures, nor create abnormal conditions surrounding the test unit. (Note: Do not use an enclosure as described in section 6.1.3 of ANSI/ASHRAE 37-2009 when testing triple-split units.)

2.7 Electrical Voltage Supply

Perform all tests at the voltage specified in section 6.1.3.2 of AHRI 210/240-2008 (incorporated by reference, see § 430.3) for “Standard Rating Tests.” If either the indoor or the outdoor unit has a 208V or 200V nameplate voltage and the other unit has a 230V nameplate rating, select the voltage supply on the outdoor unit for testing. Otherwise, supply each unit with its own nameplate voltage. Measure the supply voltage at the terminals on the test unit using a volt meter that provides a reading that is accurate to within ±1.0 percent of the measured quantity.

2.8 Electrical Power and Energy Measurements

a. Use an integrating power (watt-hour) measuring system to determine the electrical energy or average electrical power supplied to all components of the air conditioner or heat pump (including auxiliary components such as controls, transformers, crankcase heater, integral condensate pump on non-ducted indoor units, etc.). The watt-hour measuring system must give readings that are accurate to within ±0.5 percent. For cyclic tests, this accuracy is required during both the ON and OFF cycles. Use either two different scales on the same watt-hour meter or two separate watt-hour meters. Activate the scale or meter having the lower power rating within 15 seconds after beginning an OFF cycle. Activate the scale or meter having the higher power rating within 15 seconds prior to beginning an ON cycle. For ducted blower coil systems, the ON cycle lasts from compressor ON to indoor blower OFF. For ducted coil-only systems, the ON cycle lasts from compressor ON to compressor OFF. For non-ducted units, the ON cycle lasts from indoor blower ON to indoor blower OFF. When testing air conditioners and heat pumps having a variable-speed compressor, avoid using an induction watt/watt-hour meter.

b. When performing section 3.5 and/or 3.8 cyclic tests on non-ducted units, provide instrumentation to determine the average electrical power consumption of the indoor blower motor to within ±1.0 percent. If required according to sections 3.3, 3.4, 3.7, 3.9.1 of this appendix, and/or 3.10 of this appendix, this same instrumentation requirement (to determine the average electrical power consumption of the indoor blower motor to within ±1.0 percent) applies when testing air conditioners and heat pumps having a variable-speed constant-air-volume-rate indoor blower or a variable-speed, variable-air-volume-rate indoor blower.

2.9 Time Measurements

Make elapsed time measurements using an instrument that yields readings accurate to within ±0.2 percent.

2.10 Test Apparatus for the Secondary Space Conditioning Capacity Measurement

For all tests, use the indoor air enthalpy method to measure the unit's capacity. This method uses the test set-up specified in sections 2.4 to 2.6 of this appendix. In addition, for all steady-state tests, conduct a second, independent measurement of capacity as described in section 3.1.1 of this appendix. For split systems, use one of the following secondary measurement methods: Outdoor air enthalpy method, compressor calibration method, or refrigerant enthalpy method. For single-package units, use either the outdoor air enthalpy method or the compressor calibration method as the secondary measurement.

2.10.1 Outdoor Air Enthalpy Method

a. To make a secondary measurement of indoor space conditioning capacity using the outdoor air enthalpy method, do the following:

(1) Measure the electrical power consumption of the test unit;

(2) Measure the air-side capacity at the outdoor coil; and

(3) Apply a heat balance on the refrigerant cycle.

b. The test apparatus required for the outdoor air enthalpy method is a subset of the apparatus used for the indoor air enthalpy method. Required apparatus includes the following:

(1) On the outlet side, an outlet plenum containing static pressure taps (sections 2.4, 2.4.1, and 2.5.3 of this appendix),

(2) An airflow measuring apparatus (section 2.6 of this appendix),

(3) A duct section that connects these two components and itself contains the instrumentation for measuring the dry-bulb temperature and water vapor content of the air leaving the outdoor coil (sections 2.5.4, 2.5.5, and 2.5.6 of this appendix), and

(4) On the inlet side, a sampling device and temperature grid (section 2.11.b of this appendix).

c. During the free outdoor air tests described in sections 3.11.1 and 3.11.1.1 of this appendix, measure the evaporator and condenser temperatures or pressures. On both the outdoor coil and the indoor coil, solder a thermocouple onto a return bend located at or near the midpoint of each coil or at points not affected by vapor superheat or liquid subcooling. Alternatively, if the test unit is not sensitive to the refrigerant charge, install pressure gages to the access valves or to ports created from tapping into the suction and discharge lines according to sections 7.4.2 and 8.2.5 of ANSI/ASHRAE 37-2009. Use this alternative approach when testing a unit charged with a zeotropic refrigerant having a temperature glide in excess of 1 °F at the specified test conditions.

2.10.2 Compressor Calibration Method

Measure refrigerant pressures and temperatures to determine the evaporator superheat and the enthalpy of the refrigerant that enters and exits the indoor coil. Determine refrigerant flow rate or, when the superheat of the refrigerant leaving the evaporator is less than 5 °F, total capacity from separate calibration tests conducted under identical operating conditions. When using this method, install instrumentation and measure refrigerant properties according to section 7.4.2 and 8.2.5 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3). If removing the refrigerant before applying refrigerant lines and subsequently recharging, use the steps in 7.4.2 of ANSI/ASHRAE 37-2009 in addition to the methods of section 2.2.5 of this appendix to confirm the refrigerant charge. Use refrigerant temperature and pressure measuring instruments that meet the specifications given in sections 5.1.1 and 5.2 of ANSI/ASHRAE 37-2009.

2.10.3 Refrigerant Enthalpy Method

For this method, calculate space conditioning capacity by determining the refrigerant enthalpy change for the indoor coil and directly measuring the refrigerant flow rate. Use section 7.5.2 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3) for the requirements for this method, including the additional instrumentation requirements, and information on placing the flow meter and a sight glass. Use refrigerant temperature, pressure, and flow measuring instruments that meet the specifications given in sections 5.1.1, 5.2, and 5.5.1 of ANSI/ASHRAE 37-2009. Refrigerant flow measurement device(s), if used, must be either elevated at least two feet from the test chamber floor or placed upon insulating material having a total thermal resistance of at least R-12 and extending at least one foot laterally beyond each side of the device(s)' exposed surfaces.

2.11 Measurement of Test Room Ambient Conditions

Follow instructions for setting up air sampling device and aspirating psychrometer as described in section 2.14 of this appendix, unless otherwise instructed in this section.

a. If using a test set-up where air is ducted directly from the conditioning apparatus to the indoor coil inlet (see Figure 2, Loop Air-Enthalpy Test Method Arrangement, of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3)), add instrumentation to permit measurement of the indoor test room dry-bulb temperature.

b. On the outdoor side, use one of the following two approaches, except that approach (1) is required for all evaporatively-cooled units and units that transfer condensate to the outdoor unit for evaporation using condenser heat.

(1) Use sampling tree air collection on all air-inlet surfaces of the outdoor unit.

(2) Use sampling tree air collection on one or more faces of the outdoor unit and demonstrate air temperature uniformity as follows. Install a grid of evenly-distributed thermocouples on each air-permitting face on the inlet of the outdoor unit. Install the thermocouples on the air sampling device, locate them individually or attach them to a wire structure. If not installed on the air sampling device, install the thermocouple grid 6 to 24 inches from the unit. The thermocouples shall be evenly spaced across the coil inlet surface and be installed to avoid sampling of discharge air or blockage of air recirculation. The grid of thermocouples must provide at least 16 measuring points per face or one measurement per square foot of inlet face area, whichever is less. This grid must be constructed and used as per section 5.3 of ANSI/ASHRAE 41.1-2013 (incorporated by reference, see § 430.3). The maximum difference between the average temperatures measured during the test period of any two pairs of these individual thermocouples located at any of the faces of the inlet of the outdoor unit, must not exceed 2.0 °F, otherwise approach (1) must be used.

The air sampling devices shall be located at the geometric center of each side; the branches may be oriented either parallel or perpendicular to the longer edges of the air inlet area. The air sampling devices in the outdoor air inlet location shall be sized such that they cover at least 75% of the face area of the side of the coil that they are measuring.

Air distribution at the test facility point of supply to the unit shall be reviewed and may require remediation prior to the beginning of testing. Mixing fans can be used to ensure adequate air distribution in the test room. If used, mixing fans shall be oriented such that they are pointed away from the air intake so that the mixing fan exhaust does not affect the outdoor coil air volume rate. Particular attention should be given to prevent the mixing fans from affecting (enhancing or limiting) recirculation of condenser fan exhaust air back through the unit. Any fan used to enhance test room air mixing shall not cause air velocities in the vicinity of the test unit to exceed 500 feet per minute.

The air sampling device may be larger than the face area of the side being measured, however care shall be taken to prevent discharge air from being sampled. If an air sampling device dimension extends beyond the inlet area of the unit, holes shall be blocked in the air sampling device to prevent sampling of discharge air. Holes can be blocked to reduce the region of coverage of the intake holes both in the direction of the trunk axis or perpendicular to the trunk axis. For intake hole region reduction in the direction of the trunk axis, block holes of one or more adjacent pairs of branches (the branches of a pair connect opposite each other at the same trunk location) at either the outlet end or the closed end of the trunk. For intake hole region reduction perpendicular to the trunk axis, block off the same number of holes on each branch on both sides of the trunk.

A maximum of four (4) air sampling devices shall be connected to each aspirating psychrometer. In order to proportionately divide the flow stream for multiple air sampling devices for a given aspirating psychrometer, the tubing or conduit conveying sampled air to the psychrometer shall be of equivalent lengths for each air sampling device. Preferentially, the air sampling device should be hard connected to the aspirating psychrometer, but if space constraints do not allow this, the assembly shall have a means of allowing a flexible tube to connect the air sampling device to the aspirating psychrometer. The tubing or conduit shall be insulated and routed to prevent heat transfer to the air stream. Any surface of the air conveying tubing in contact with surrounding air at a different temperature than the sampled air shall be insulated with thermal insulation with a nominal thermal resistance (R-value) of at least 19 hr · ft 2 · °F/Btu. Alternatively the conduit may have lower thermal resistance if additional sensor(s) are used to measure dry bulb temperature at the outlet of each air sampling device. No part of the air sampling device or the tubing conducting the sampled air to the sensors shall be within two inches of the test chamber floor.

Pairs of measurements (e.g., dry bulb temperature and wet bulb temperature) used to determine water vapor content of sampled air shall be measured in the same location.

2.12 Measurement of Indoor Blower Speed

When required, measure fan speed using a revolution counter, tachometer, or stroboscope that gives readings accurate to within ±1.0 percent.

2.13 Measurement of Barometric Pressure

Determine the average barometric pressure during each test. Use an instrument that meets the requirements specified in section 5.2 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3).

2.14 Air Sampling Device and Aspirating Psychrometer Requirements

Air temperature measurements shall be made in accordance with ANSI/ASHRAE 41.1-2013, unless otherwise instructed in this section.

2.14.1 Air Sampling Device Requirements

The air sampling device is intended to draw in a sample of the air at the critical locations of a unit under test. It shall be constructed of stainless steel, plastic or other suitable, durable materials. It shall have a main flow trunk tube with a series of branch tubes connected to the trunk tube. Holes shall be on the side of the sampler facing the upstream direction of the air source. Other sizes and rectangular shapes can be used, and shall be scaled accordingly with the following guidelines:

(1) Minimum hole density of 6 holes per square foot of area to be sampled

(2) Sampler branch tube pitch (spacing) of 6 ± 3 in

(3) Manifold trunk to branch diameter ratio having a minimum of 3:1 ratio

(4) Hole pitch (spacing) shall be equally distributed over the branch ( 1/2 pitch from the closed end to the nearest hole)

(5) Maximum individual hole to branch diameter ratio of 1:2 (1:3 preferred)

The minimum average velocity through the air sampling device holes shall be 2.5 ft/s as determined by evaluating the sum of the open area of the holes as compared to the flow area in the aspirating psychrometer.

2.14.2 Aspirating Psychrometer

The psychrometer consists of a flow section and a fan to draw air through the flow section and measures an average value of the sampled air stream. At a minimum, the flow section shall have a means for measuring the dry bulb temperature (typically, a resistance temperature device (RTD) and a means for measuring the humidity (RTD with wetted sock, chilled mirror hygrometer, or relative humidity sensor). The aspirating psychrometer shall include a fan that either can be adjusted manually or automatically to maintain required velocity across the sensors.

The psychrometer shall be made from suitable material which may be plastic (such as polycarbonate), aluminum or other metallic materials. All psychrometers for a given system being tested, shall be constructed of the same material. Psychrometers shall be designed such that radiant heat from the motor (for driving the fan that draws sampled air through the psychrometer) does not affect sensor measurements. For aspirating psychrometers, velocity across the wet bulb sensor shall be 1000 ± 200 ft/min. For all other psychrometers, velocity shall be as specified by the sensor manufacturer.

3. Testing Procedures 3.1 General Requirements

If, during the testing process, an equipment set-up adjustment is made that would have altered the performance of the unit during any already completed test, then repeat all tests affected by the adjustment. For cyclic tests, instead of maintaining an air volume rate, for each airflow nozzle, maintain the static pressure difference or velocity pressure during an ON period at the same pressure difference or velocity pressure as measured during the steady-state test conducted at the same test conditions.

Use the testing procedures in this section to collect the data used for calculating

(1) Performance metrics for central air conditioners and heat pumps during the cooling season;

(2) Performance metrics for heat pumps during the heating season; and

(3) Power consumption metric(s) for central air conditioners and heat pumps during the off mode season(s).

3.1.1 Primary and Secondary Test Methods

For all tests, use the indoor air enthalpy method test apparatus to determine the unit's space conditioning capacity. The procedure and data collected, however, differ slightly depending upon whether the test is a steady-state test, a cyclic test, or a frost accumulation test. The following sections described these differences. For the full-capacity cooling-mode test and (for a heat pump) the full-capacity heating-mode test, use one of the acceptable secondary methods specified in section 2.10 of this appendix to determine indoor space conditioning capacity. Calculate this secondary check of capacity according to section 3.11 of this appendix. The two capacity measurements must agree to within 6 percent to constitute a valid test. For this capacity comparison, use the Indoor Air Enthalpy Method capacity that is calculated in section 7.3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3) (and, if testing a coil-only system, compare capacities before making the after-test fan heat adjustments described in section 3.3, 3.4, 3.7, and 3.10 of this appendix). However, include the appropriate section 3.3 to 3.5 and 3.7 to 3.10 fan heat adjustments within the indoor air enthalpy method capacities used for the section 4 seasonal calculations of this appendix.

3.1.2 Manufacturer-Provided Equipment Overrides

Where needed, the manufacturer must provide a means for overriding the controls of the test unit so that the compressor(s) operates at the specified speed or capacity and the indoor blower operates at the specified speed or delivers the specified air volume rate.

3.1.3 Airflow Through the Outdoor Coil

For all tests, meet the requirements given in section 6.1.3.4 of AHRI 210/240-2008 (incorporated by reference, see § 430.3) when obtaining the airflow through the outdoor coil.

3.1.3.1 Double-Ducted

For products intended to be installed with the outdoor airflow ducted, the unit shall be installed with outdoor coil ductwork installed per manufacturer installation instructions and shall operate between 0.10 and 0.15 in H2O external static pressure. External static pressure measurements shall be made in accordance with ANSI/ASHRAE 37-2009 section 6.4 and 6.5.

3.1.4 Airflow Through the Indoor Coil

Airflow setting(s) shall be determined before testing begins. Unless otherwise specified within this or its subsections, no changes shall be made to the airflow setting(s) after initiation of testing.

3.1.4.1 Cooling Full-Load Air Volume Rate 3.1.4.1.1. Cooling Full-Load Air Volume Rate for Ducted Units

Identify the certified cooling full-load air volume rate and certified instructions for setting fan speed or controls. If there is no certified Cooling full-load air volume rate, use a value equal to the certified cooling capacity of the unit times 400 scfm per 12,000 Btu/h. If there are no instructions for setting fan speed or controls, use the as-shipped settings. Use the following procedure to confirm and, if necessary, adjust the Cooling full-load air volume rate and the fan speed or control settings to meet each test procedure requirement:

a. For all ducted blower coil systems, except those having a constant-air-volume-rate indoor blower:

Step (1) Operate the unit under conditions specified for the A (for single-stage units) or A2 test using the certified fan speed or controls settings, and adjust the exhaust fan of the airflow measuring apparatus to achieve the certified Cooling full-load air volume rate;

Step (2) Measure the external static pressure;

Step (3) If this external static pressure is equal to or greater than the applicable minimum external static pressure cited in Table 4, the pressure requirement is satisfied; proceed to step 7 of this section. If this external static pressure is not equal to or greater than the applicable minimum external static pressure cited in Table 4, proceed to step 4 of this section;

Step (4) Increase the external static pressure by adjusting the exhaust fan of the airflow measuring apparatus until either

(i) The applicable Table 4 minimum is equaled or

(ii) The measured air volume rate equals 90 percent or less of the Cooling full-load air volume rate, whichever occurs first;

Step (5) If the conditions of step 4 (i) of this section occur first, the pressure requirement is satisfied; proceed to step 7 of this section. If the conditions of step 4 (ii) of this section occur first, proceed to step 6 of this section;

Step (6) Make an incremental change to the setup of the indoor blower (e.g., next highest fan motor pin setting, next highest fan motor speed) and repeat the evaluation process beginning above, at step 1 of this section. If the indoor blower setup cannot be further changed, increase the external static pressure by adjusting the exhaust fan of the airflow measuring apparatus until the applicable Table 4 minimum is equaled; proceed to step 7 of this section;

Step (7) The airflow constraints have been satisfied. Use the measured air volume rate as the Cooling full-load air volume rate. Use the final fan speed or control settings for all tests that use the Cooling full-load air volume rate.

b. For ducted blower coil systems with a constant-air-volume-rate indoor blower. For all tests that specify the Cooling full-load air volume rate, obtain an external static pressure as close to (but not less than) the applicable Table 4 value that does not cause automatic shutdown of the indoor blower or air volume rate variation QVar, defined as follows, greater than 10 percent.

where: Qmax = maximum measured airflow value Qmin = minimum measured airflow value QVar = airflow variance, percent

Additional test steps as described in section 3.3.(e) of this appendix are required if the measured external static pressure exceeds the target value by more than 0.03 inches of water.

c. For coil-only indoor units. For the A or A2 Test, (exclusively), the pressure drop across the indoor coil assembly must not exceed 0.30 inches of water. If this pressure drop is exceeded, reduce the air volume rate until the measured pressure drop equals the specified maximum. Use this reduced air volume rate for all tests that require the Cooling full-load air volume rate.

Table 4—Minimum External Static Pressure for Ducted Blower Coil Systems

Rated Cooling 1 or Heating 2 Capacity
(Btu/h)
Minimum external resistance 3 (Inches of water) Small-duct,
high-velocity
systems 4 5
All other
systems
Up Thru 28,8001.100.10 29,000 to 42,5001.150.15 43,000 and Above1.200.20

1 For air conditioners and air-conditioning heat pumps, the value certified by the manufacturer for the unit's cooling capacity when operated at the A or A2 Test conditions.

2 For heating-only heat pumps, the value certified by the manufacturer for the unit's heating capacity when operated at the H1 or H12 Test conditions.

3 For ducted units tested without an air filter installed, increase the applicable tabular value by 0.08 inches of water.

4 See section 1.2 of this appendix, Definitions, to determine if the equipment qualifies as a small-duct, high-velocity system.

5 If a closed-loop, air-enthalpy test apparatus is used on the indoor side, limit the resistance to airflow on the inlet side of the blower coil indoor unit to a maximum value of 0.1 inch of water. Impose the balance of the airflow resistance on the outlet side of the indoor blower.

d. For ducted systems having multiple indoor blowers within a single indoor section, obtain the full-load air volume rate with all indoor blowers operating unless prevented by the controls of the unit. In such cases, turn on the maximum number of indoor blowers permitted by the unit's controls. Where more than one option exists for meeting this “on” indoor blower requirement, which indoor blower(s) are turned on must match that specified in the certification report. Conduct section 3.1.4.1.1 setup steps for each indoor blower separately. If two or more indoor blowers are connected to a common duct as per section 2.4.1 of this appendix, temporarily divert their air volume to the test room when confirming or adjusting the setup configuration of individual indoor blowers. The allocation of the system's full-load air volume rate assigned to each “on” indoor blower must match that specified by the manufacturer in the certification report.

3.1.4.1.2. Cooling Full-Load Air Volume Rate for Non-Ducted Units

For non-ducted units, the Cooling full-load air volume rate is the air volume rate that results during each test when the unit is operated at an external static pressure of zero inches of water.

3.1.4.2 Cooling Minimum Air Volume Rate

Identify the certified cooling minimum air volume rate and certified instructions for setting fan speed or controls. If there is no certified cooling minimum air volume rate, use the final indoor blower control settings as determined when setting the cooling full-load air volume rate, and readjust the exhaust fan of the airflow measuring apparatus if necessary to reset to the cooling full load air volume obtained in section 3.1.4.1 of this appendix. Otherwise, calculate the target external static pressure and follow instructions a, b, c, d, or e below. The target external static pressure, ΔPst__i, for any test “i” with a specified air volume rate not equal to the Cooling full-load air volume rate is determined as follows:

where: ΔPst__i = target minimum external static pressure for test i; ΔPst__full = minimum external static pressure for test A or A2 (Table 4); Qi = air volume rate for test i; and Qfull = Cooling full-load air volume rate as measured after setting and/or adjustment as described in section 3.1.4.1.1 of this appendix.

a. For a ducted blower coil system without a constant-air-volume indoor blower, adjust for external static pressure as follows:

Step (1) Operate the unit under conditions specified for the B1 test using the certified fan speed or controls settings, and adjust the exhaust fan of the airflow measuring apparatus to achieve the certified cooling minimum air volume rate;

Step (2) Measure the external static pressure;

Step (3) If this pressure is equal to or greater than the minimum external static pressure computed above, the pressure requirement is satisfied; proceed to step 7 of this section. If this pressure is not equal to or greater than the minimum external static pressure computed above, proceed to step 4 of this section;

Step (4) Increase the external static pressure by adjusting the exhaust fan of the airflow measuring apparatus until either

(i) The pressure is equal to the minimum external static pressure computed above or

(ii) The measured air volume rate equals 90 percent or less of the cooling minimum air volume rate, whichever occurs first;

Step (5) If the conditions of step 4 (i) of this section occur first, the pressure requirement is satisfied; proceed to step 7 of this section. If the conditions of step 4 (ii) of this section occur first, proceed to step 6 of this section;

Step (6) Make an incremental change to the setup of the indoor blower (e.g., next highest fan motor pin setting, next highest fan motor speed) and repeat the evaluation process beginning above, at step 1 of this section. If the indoor blower setup cannot be further changed, increase the external static pressure by adjusting the exhaust fan of the airflow measuring apparatus until it equals the minimum external static pressure computed above; proceed to step 7 of this section;

Step (7) The airflow constraints have been satisfied. Use the measured air volume rate as the cooling minimum air volume rate. Use the final fan speed or control settings for all tests that use the cooling minimum air volume rate.

b. For ducted units with constant-air-volume indoor blowers, conduct all tests that specify the cooling minimum air volume rate—(i.e., the A1, B1, C1, F1, and G1 Tests)—at an external static pressure that does not cause an automatic shutdown of the indoor blower or air volume rate variation QVar, defined in section 3.1.4.1.1.b of this appendix, greater than 10 percent, while being as close to, but not less than the target minimum external static pressure. Additional test steps as described in section 3.3(e) of this appendix are required if the measured external static pressure exceeds the target value by more than 0.03 inches of water.

c. For ducted two-capacity coil-only systems, the cooling minimum air volume rate is the higher of (1) the rate specified by the installation instructions included with the unit by the manufacturer or (2) 75 percent of the cooling full-load air volume rate. During the laboratory tests on a coil-only (fanless) system, obtain this cooling minimum air volume rate regardless of the pressure drop across the indoor coil assembly.

d. For non-ducted units, the cooling minimum air volume rate is the air volume rate that results during each test when the unit operates at an external static pressure of zero inches of water and at the indoor blower setting used at low compressor capacity (two-capacity system) or minimum compressor speed (variable-speed system). For units having a single-speed compressor and a variable-speed variable-air-volume-rate indoor blower, use the lowest fan setting allowed for cooling.

e. For ducted systems having multiple indoor blowers within a single indoor section, operate the indoor blowers such that the lowest air volume rate allowed by the unit's controls is obtained when operating the lone single-speed compressor or when operating at low compressor capacity while meeting the requirements of section 2.2.3.b of this appendix for the minimum number of blowers that must be turned off. Using the target external static pressure and the certified air volume rates, follow the procedures described in section 3.1.4.2.a of this appendix if the indoor blowers are not constant-air-volume indoor blowers or as described in section 3.1.4.2.b of this appendix if the indoor blowers are constant-air-volume indoor blowers. The sum of the individual “on” indoor blowers' air volume rates is the cooling minimum air volume rate for the system.

3.1.4.3 Cooling Intermediate Air Volume Rate

Identify the certified cooling intermediate air volume rate and certified instructions for setting fan speed or controls. If there is no certified cooling intermediate air volume rate, use the final indoor blower control settings as determined when setting the cooling full load air volume rate, and readjust the exhaust fan of the airflow measuring apparatus if necessary to reset to the cooling full load air volume obtained in section 3.1.4.1 of this appendix. Otherwise, calculate target minimum external static pressure as described in section 3.1.4.2 of this appendix, and set the air volume rate as follows.

a. For a ducted blower coil system without a constant-air-volume indoor blower, adjust for external static pressure as described in section 3.1.4.2.a of this appendix for cooling minimum air volume rate.

b. For a ducted blower coil system with a constant-air-volume indoor blower, conduct the EV Test at an external static pressure that does not cause an automatic shutdown of the indoor blower or air volume rate variation QVar, defined in section 3.1.4.1.1.b of this appendix, greater than 10 percent, while being as close to, but not less than the target minimum external static pressure. Additional test steps as described in section 3.3(e) of this appendix are required if the measured external static pressure exceeds the target value by more than 0.03 inches of water.

c. For non-ducted units, the cooling intermediate air volume rate is the air volume rate that results when the unit operates at an external static pressure of zero inches of water and at the fan speed selected by the controls of the unit for the EV Test conditions.

3.1.4.4 Heating Full-Load Air Volume Rate 3.1.4.4.1. Ducted Heat Pumps Where the Heating and Cooling Full-Load Air Volume Rates Are the Same

a. Use the Cooling full-load air volume rate as the heating full-load air volume rate for:

(1) Ducted blower coil system heat pumps that do not have a constant-air-volume indoor blower, and that operate at the same airflow-control setting during both the A (or A2) and the H1 (or H12) Tests;

(2) Ducted blower coil system heat pumps with constant-air-flow indoor blowers that provide the same air flow for the A (or A2) and the H1 (or H12) Tests; and

(3) Ducted heat pumps that are tested with a coil-only indoor unit (except two-capacity northern heat pumps that are tested only at low capacity cooling—see section 3.1.4.4.2 of this appendix).

b. For heat pumps that meet the above criteria “1” and “3,” no minimum requirements apply to the measured external or internal, respectively, static pressure. Use the final indoor blower control settings as determined when setting the Cooling full-load air volume rate, and readjust the exhaust fan of the airflow measuring apparatus if necessary to reset to the cooling full-load air volume obtained in section 3.1.4.1 of this appendix. For heat pumps that meet the above criterion “2,” test at an external static pressure that does not cause an automatic shutdown of the indoor blower or air volume rate variation QVar, defined in section 3.1.4.1.1.b of this appendix, greater than 10 percent, while being as close to, but not less than, the same Table 4 minimum external static pressure as was specified for the A (or A2) cooling mode test. Additional test steps as described in section 3.9.1(c) of this appendix are required if the measured external static pressure exceeds the target value by more than 0.03 inches of water.

3.1.4.4.2. Ducted Heat Pumps Where the Heating and Cooling Full-Load Air Volume Rates Are Different Due to Changes in Indoor Blower Operation, i.e. Speed Adjustment by the System Controls

Identify the certified heating full-load air volume rate and certified instructions for setting fan speed or controls. If there is no certified heating full-load air volume rate, use the final indoor blower control settings as determined when setting the cooling full-load air volume rate, and readjust the exhaust fan of the airflow measuring apparatus if necessary to reset to the cooling full load air volume obtained in section 3.1.4.1 of this appendix. Otherwise, calculate target minimum external static pressure as described in section 3.1.4.2 of this appendix and set the air volume rate as follows.

a. For ducted blower coil system heat pumps that do not have a constant-air-volume indoor blower, adjust for external static pressure as described in section 3.1.4.2.a of this appendix for cooling minimum air volume rate.

b. For ducted heat pumps tested with constant-air-volume indoor blowers installed, conduct all tests that specify the heating full-load air volume rate at an external static pressure that does not cause an automatic shutdown of the indoor blower or air volume rate variation QVar, defined in section 3.1.4.1.1.b of this appendix, greater than 10 percent, while being as close to, but not less than the target minimum external static pressure. Additional test steps as described in section 3.9.1(c) of this appendix are required if the measured external static pressure exceeds the target value by more than 0.03 inches of water.

c. When testing ducted, two-capacity blower coil system northern heat pumps (see section 1.2 of this appendix, Definitions), use the appropriate approach of the above two cases. For coil-only system northern heat pumps, the heating full-load air volume rate is the lesser of the rate specified by the manufacturer in the installation instructions included with the unit or 133 percent of the cooling full-load air volume rate. For this latter case, obtain the heating full-load air volume rate regardless of the pressure drop across the indoor coil assembly.

d. For ducted systems having multiple indoor blowers within a single indoor section, obtain the heating full-load air volume rate using the same “on” indoor blowers as used for the Cooling full-load air volume rate. Using the target external static pressure and the certified air volume rates, follow the procedures as described in section 3.1.4.4.2.a of this appendix if the indoor blowers are not constant-air-volume indoor blowers or as described in section 3.1.4.4.2.b of this appendix if the indoor blowers are constant-air-volume indoor blowers. The sum of the individual “on” indoor blowers' air volume rates is the heating full load air volume rate for the system.

3.1.4.4.3. Ducted Heating-Only Heat Pumps

Identify the certified heating full-load air volume rate and certified instructions for setting fan speed or controls. If there is no certified heating full-load air volume rate, use a value equal to the certified heating capacity of the unit times 400 scfm per 12,000 Btu/h. If there are no instructions for setting fan speed or controls, use the as-shipped settings.

a. For all ducted heating-only blower coil system heat pumps, except those having a constant-air-volume-rate indoor blower. Conduct the following steps only during the first test, the H1 or H12 Test:

Step (1) Adjust the exhaust fan of the airflow measuring apparatus to achieve the certified heating full-load air volume rate.

Step (2) Measure the external static pressure.

Step (3) If this pressure is equal to or greater than the Table 4 minimum external static pressure that applies given the heating-only heat pump's rated heating capacity, the pressure requirement is satisfied; proceed to step 7 of this section. If this pressure is not equal to or greater than the applicable Table 4 minimum external static pressure, proceed to step 4 of this section;

Step (4) Increase the external static pressure by adjusting the exhaust fan of the airflow measuring apparatus until either (i) the pressure is equal to the applicable Table 4 minimum external static pressure or (ii) the measured air volume rate equals 90 percent or less of the heating full-load air volume rate, whichever occurs first;

Step (5) If the conditions of step 4(i) of this section occur first, the pressure requirement is satisfied; proceed to step 7 of this section. If the conditions of step 4(ii) of this section occur first, proceed to step 6 of this section;

Step (6) Make an incremental change to the setup of the indoor blower (e.g., next highest fan motor pin setting, next highest fan motor speed) and repeat the evaluation process beginning above, at step 1 of this section. If the indoor blower setup cannot be further changed, increase the external static pressure by adjusting the exhaust fan of the airflow measuring apparatus until it equals the applicable Table 4 minimum external static pressure; proceed to step 7 of this section;

Step (7) The airflow constraints have been satisfied. Use the measured air volume rate as the heating full-load air volume rate. Use the final fan speed or control settings for all tests that use the heating full-load air volume rate.

b. For ducted heating-only blower coil system heat pumps having a constant-air-volume-rate indoor blower. For all tests that specify the heating full-load air volume rate, obtain an external static pressure that does not cause an automatic shutdown of the indoor blower or air volume rate variation QVar, defined in section 3.1.4.1.1.b of this appendix, greater than 10 percent, while being as close to, but not less than, the applicable Table 4 minimum. Additional test steps as described in section 3.9.1(c) of this appendix are required if the measured external static pressure exceeds the target value by more than 0.03 inches of water.

c. For ducted heating-only coil-only system heat pumps in the H1 or H12 Test, (exclusively), the pressure drop across the indoor coil assembly must not exceed 0.30 inches of water. If this pressure drop is exceeded, reduce the air volume rate until the measured pressure drop equals the specified maximum. Use this reduced air volume rate for all tests that require the heating full-load air volume rate.

3.1.4.4.4. Non-Ducted Heat Pumps, Including Non-Ducted Heating-Only Heat Pumps

For non-ducted heat pumps, the heating full-load air volume rate is the air volume rate that results during each test when the unit operates at an external static pressure of zero inches of water.

3.1.4.5 Heating Minimum Air Volume Rate 3.1.4.5.1. Ducted Heat Pumps Where the Heating and Cooling Minimum Air Volume Rates Are the Same

a. Use the cooling minimum air volume rate as the heating minimum air volume rate for:

(1) Ducted blower coil system heat pumps that do not have a constant-air-volume indoor blower, and that operate at the same airflow-control setting during both the A1 and the H11 tests;

(2) Ducted blower coil system heat pumps with constant-air-flow indoor blowers installed that provide the same air flow for the A1 and the H11 Tests; and

(3) Ducted coil-only system heat pumps.

b. For heat pumps that meet the above criteria “1” and “3,” no minimum requirements apply to the measured external or internal, respectively, static pressure. Use the final indoor blower control settings as determined when setting the cooling minimum air volume rate, and readjust the exhaust fan of the airflow measuring apparatus if necessary to reset to the cooling minimum air volume rate obtained in section 3.1.4.2 of this appendix. For heat pumps that meet the above criterion “2,” test at an external static pressure that does not cause an automatic shutdown of the indoor blower or air volume rate variation QVar, defined in section 3.1.4.1.1.b of this appendix, greater than 10 percent, while being as close to, but not less than, the same target minimum external static pressure as was specified for the A1 cooling mode test. Additional test steps as described in section 3.9.1(c) of this appendix are required if the measured external static pressure exceeds the target value by more than 0.03 inches of water.

3.1.4.5.2. Ducted Heat Pumps Where the Heating and Cooling Minimum Air Volume Rates Are Different Due to Changes in Indoor Blower Operation, i.e. Speed Adjustment by the System Controls

Identify the certified heating minimum air volume rate and certified instructions for setting fan speed or controls. If there is no certified heating minimum air volume rate, use the final indoor blower control settings as determined when setting the cooling minimum air volume rate, and readjust the exhaust fan of the airflow measuring apparatus if necessary to reset to the cooling minimum air volume obtained in section 3.1.4.2 of this appendix. Otherwise, calculate the target minimum external static pressure as described in section 3.1.4.2 of this appendix.

a. For ducted blower coil system heat pumps that do not have a constant-air-volume indoor blower, adjust for external static pressure as described in section 3.1.4.2.a of this appendix for cooling minimum air volume rate.

b. For ducted heat pumps tested with constant-air-volume indoor blowers installed, conduct all tests that specify the heating minimum air volume rate—(i.e., the H01, H11, H21, and H31 Tests)—at an external static pressure that does not cause an automatic shutdown of the indoor blower while being as close to, but not less than the air volume rate variation QVar, defined in section 3.1.4.1.1.b of this appendix, greater than 10 percent, while being as close to, but not less than the target minimum external static pressure. Additional test steps as described in section 3.9.1.c of this appendix are required if the measured external static pressure exceeds the target value by more than 0.03 inches of water.

c. For ducted two-capacity blower coil system northern heat pumps, use the appropriate approach of the above two cases.

d. For ducted two-capacity coil-only system heat pumps, use the cooling minimum air volume rate as the heating minimum air volume rate. For ducted two-capacity coil-only system northern heat pumps, use the cooling full-load air volume rate as the heating minimum air volume rate. For ducted two-capacity heating-only coil-only system heat pumps, the heating minimum air volume rate is the higher of the rate specified by the manufacturer in the test setup instructions included with the unit or 75 percent of the heating full-load air volume rate. During the laboratory tests on a coil-only system, obtain the heating minimum air volume rate without regard to the pressure drop across the indoor coil assembly.

e. For non-ducted heat pumps, the heating minimum air volume rate is the air volume rate that results during each test when the unit operates at an external static pressure of zero inches of water and at the indoor blower setting used at low compressor capacity (two-capacity system) or minimum compressor speed (variable-speed system). For units having a single-speed compressor and a variable-speed, variable-air-volume-rate indoor blower, use the lowest fan setting allowed for heating.

f. For ducted systems with multiple indoor blowers within a single indoor section, obtain the heating minimum air volume rate using the same “on” indoor blowers as used for the cooling minimum air volume rate. Using the target external static pressure and the certified air volume rates, follow the procedures as described in section 3.1.4.5.2.a of this appendix if the indoor blowers are not constant-air-volume indoor blowers or as described in section 3.1.4.5.2.b of this appendix if the indoor blowers are constant-air-volume indoor blowers. The sum of the individual “on” indoor blowers' air volume rates is the heating full-load air volume rate for the system.

3.1.4.6 Heating Intermediate Air Volume Rate

Identify the certified heating intermediate air volume rate and certified instructions for setting fan speed or controls. If there is no certified heating intermediate air volume rate, use the final indoor blower control settings as determined when setting the heating full-load air volume rate, and readjust the exhaust fan of the airflow measuring apparatus if necessary to reset to the cooling full load air volume obtained in section 3.1.4.2 of this appendix. Calculate the target minimum external static pressure as described in section 3.1.4.2 of this appendix.

a. For ducted blower coil system heat pumps that do not have a constant-air-volume indoor blower, adjust for external static pressure as described in section 3.1.4.2.a of this appendix for cooling minimum air volume rate.

b. For ducted heat pumps tested with constant-air-volume indoor blowers installed, conduct the H2V Test at an external static pressure that does not cause an automatic shutdown of the indoor blower or air volume rate variation QVar, defined in section 3.1.4.1.1.b of this appendix, greater than 10 percent, while being as close to, but not less than the target minimum external static pressure. Additional test steps as described in section 3.9.1(c) of this appendix are required if the measured external static pressure exceeds the target value by more than 0.03 inches of water.

c. For non-ducted heat pumps, the heating intermediate air volume rate is the air volume rate that results when the heat pump operates at an external static pressure of zero inches of water and at the fan speed selected by the controls of the unit for the H2V Test conditions.

3.1.4.7 Heating Nominal Air Volume Rate

The manufacturer must specify the heating nominal air volume rate and the instructions for setting fan speed or controls. Calculate target minimum external static pressure as described in section 3.1.4.2 of this appendix. Make adjustments as described in section 3.1.4.6 of this appendix for heating intermediate air volume rate so that the target minimum external static pressure is met or exceeded.

3.1.5 Indoor Test Room Requirement When the Air Surrounding the Indoor Unit Is Not Supplied From the Same Source as the Air Entering the Indoor Unit

If using a test set-up where air is ducted directly from the air reconditioning apparatus to the indoor coil inlet (see Figure 2, Loop Air-Enthalpy Test Method Arrangement, of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3)), maintain the dry bulb temperature within the test room within ±5.0 °F of the applicable sections 3.2 and 3.6 dry bulb temperature test condition for the air entering the indoor unit. Dew point shall be within 2 °F of the required inlet conditions.

3.1.6 Air Volume Rate Calculations

For all steady-state tests and for frost accumulation (H2, H21, H22, H2V) tests, calculate the air volume rate through the indoor coil as specified in sections 7.7.2.1 and 7.7.2.2 of ANSI/ASHRAE 37-2009. When using the outdoor air enthalpy method, follow sections 7.7.2.1 and 7.7.2.2 of ANSI/ASHRAE 37-2009 to calculate the air volume rate through the outdoor coil. To express air volume rates in terms of standard air, use:

Where: V s = air volume rate of standard (dry) air, (ft 3/min)da V mx = air volume rate of the air-water vapor mixture, (ft 3/min)mx vn′ = specific volume of air-water vapor mixture at the nozzle, ft 3 per lbm of the air-water vapor mixture Wn = humidity ratio at the nozzle, lbm of water vapor per lbm of dry air 0.075 = the density associated with standard (dry) air, (lbm/ft 3) vn = specific volume of the dry air portion of the mixture evaluated at the dry-bulb temperature, vapor content, and barometric pressure existing at the nozzle, ft 3 per lbm of dry air. Note:

In the first printing of ANSI/ASHRAE 37-2009, the second IP equation for Qmi should read

3.1.7 Test Sequence

Before making test measurements used to calculate performance, operate the equipment for the “break-in” period specified in the certification report, which may not exceed 20 hours. Each compressor of the unit must undergo this “break-in” period. When testing a ducted unit (except if a heating-only heat pump), conduct the A or A2 Test first to establish the cooling full-load air volume rate. For ducted heat pumps where the heating and cooling full-load air volume rates are different, make the first heating mode test one that requires the heating full-load air volume rate. For ducted heating-only heat pumps, conduct the H1 or H12 Test first to establish the heating full-load air volume rate. When conducting a cyclic test, always conduct it immediately after the steady-state test that requires the same test conditions. For variable-speed systems, the first test using the cooling minimum air volume rate should precede the EV Test, and the first test using the heating minimum air volume rate must precede the H2V Test. The test laboratory makes all other decisions on the test sequence.

3.1.8 Requirement for the Air Temperature Distribution Leaving the Indoor Coil

For at least the first cooling mode test and the first heating mode test, monitor the temperature distribution of the air leaving the indoor coil using the grid of individual sensors described in sections 2.5 and 2.5.4 of this appendix. For the 30-minute data collection interval used to determine capacity, the maximum spread among the outlet dry bulb temperatures from any data sampling must not exceed 1.5 °F. Install the mixing devices described in section 2.5.4.2 of this appendix to minimize the temperature spread.

3.1.9 Requirement for the Air Temperature Distribution Entering the Outdoor Coil

Monitor the temperatures of the air entering the outdoor coil using air sampling devices and/or temperature sensor grids, maintaining the required tolerances, if applicable, as described in section 2.11 of this appendix.

3.1.10 Control of Auxiliary Resistive Heating Elements

Except as noted, disable heat pump resistance elements used for heating indoor air at all times, including during defrost cycles and if they are normally regulated by a heat comfort controller. For heat pumps equipped with a heat comfort controller, enable the heat pump resistance elements only during the below-described, short test. For single-speed heat pumps covered under section 3.6.1 of this appendix, the short test follows the H1 or, if conducted, the H1C Test. For two-capacity heat pumps and heat pumps covered under section 3.6.2 of this appendix, the short test follows the H12 Test. Set the heat comfort controller to provide the maximum supply air temperature. With the heat pump operating and while maintaining the heating full-load air volume rate, measure the temperature of the air leaving the indoor-side beginning 5 minutes after activating the heat comfort controller. Sample the outlet dry-bulb temperature at regular intervals that span 5 minutes or less. Collect data for 10 minutes, obtaining at least 3 samples. Calculate the average outlet temperature over the 10-minute interval, TCC.

3.2 Cooling Mode Tests for Different Types of Air Conditioners and Heat Pumps 3.2.1 Tests for a System Having a Single-Speed Compressor and Fixed Cooling Air Volume Rate

This set of tests is for single-speed-compressor units that do not have a cooling minimum air volume rate or a cooling intermediate air volume rate that is different than the cooling full load air volume rate. Conduct two steady-state wet coil tests, the A and B Tests. Use the two optional dry-coil tests, the steady-state C Test and the cyclic D Test, to determine the cooling mode cyclic degradation coefficient, CD c. If the two optional tests are conducted but yield a tested CD c that exceeds the default CD c or if the two optional tests are not conducted, assign CD c the default value of 0.25 (for outdoor units with no match) or 0.20 (for all other systems). Table 5 specifies test conditions for these four tests.

Table 5—Cooling Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed Cooling Air Volume Rate

Test description Air entering indoor unit
temperature ( °F)
Air entering outdoor unit
temperature ( °F)
Cooling air volume rate Dry bulb Wet bulb Dry bulb Wet bulb A Test—required (steady, wet coil)8067951 75Cooling full-load. 2B Test—required (steady, wet coil)8067821 65Cooling full-load. 2C Test—optional (steady, dry coil)80( 3)82Cooling full-load. 2D Test—optional (cyclic, dry coil)80( 3)82( 4).

1 The specified test condition only applies if the unit rejects condensate to the outdoor coil.

2 Defined in section 3.1.4.1 of this appendix.

3 The entering air must have a low enough moisture content so no condensate forms on the indoor coil. (It is recommended that an indoor wet-bulb temperature of 57 °F or less be used.)

4 Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity pressure as measured during the C Test.

3.2.2 Tests for a Unit Having a Single-Speed Compressor Where the Indoor Section Uses a Single Variable-Speed Variable-Air-Volume Rate Indoor Blower or Multiple Indoor Blowers 3.2.2.1 Indoor Blower Capacity Modulation That Correlates With the Outdoor Dry Bulb Temperature or Systems With a Single Indoor Coil but Multiple Indoor Blowers

Conduct four steady-state wet coil tests: The A2, A1, B2, and B1 tests. Use the two optional dry-coil tests, the steady-state C1 test and the cyclic D1 test, to determine the cooling mode cyclic degradation coefficient, CD c. If the two optional tests are conducted but yield a tested CDc that exceeds the default CDc or if the two optional tests are not conducted, assign CDc the default value of 0.20.

3.2.2.2 Indoor Blower Capacity Modulation Based on Adjusting the Sensible to Total (S/T) Cooling Capacity Ratio

The testing requirements are the same as specified in section 3.2.1 of this appendix and Table 5. Use a cooling full-load air volume rate that represents a normal installation. If performed, conduct the steady-state C Test and the cyclic D Test with the unit operating in the same S/T capacity control mode as used for the B Test.

Table 6—Cooling Mode Test Conditions for Units With a Single-Speed Compressor That Meet the Section 3.2.2.1 Indoor Unit Requirements

Test description Air entering indoor unit
temperature ( °F)
Air entering outdoor unit
temperature ( °F)
Cooling air volume rate Dry bulb Wet bulb Dry bulb Wet bulb A2 Test—required (steady, wet coil)8067951 75Cooling full-load. 2A1 Test—required (steady, wet coil)8067951 75Cooling minimum. 3B2 Test—required (steady, wet coil)8067821 65Cooling full-load. 2B1 Test—required (steady, wet coil)8067821 65Cooling minimum. 3C1 Test 4—optional (steady, dry coil)80( 4)82Cooling minimum. 3D1 Test 4—optional (cyclic, dry coil)80( 4)82( 5).

1 The specified test condition only applies if the unit rejects condensate to the outdoor coil.

2 Defined in section 3.1.4.1 of this appendix.

3 Defined in section 3.1.4.2 of this appendix.

4 The entering air must have a low enough moisture content so no condensate forms on the indoor coil. (It is recommended that an indoor wet-bulb temperature of 5 °F or less be used.)

5 Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity pressure as measured during the C1 Test.

3.2.3 Tests for a Unit Having a Two-Capacity Compressor (See Section 1.2 of This Appendix, Definitions)

a. Conduct four steady-state wet coil tests: the A2, B2, B1, and F1 Tests. Use the two optional dry-coil tests, the steady-state C1 Test and the cyclic D1 Test, to determine the cooling-mode cyclic-degradation coefficient, CD c. If the two optional tests are conducted but yield a tested CDc that exceeds the default CDc or if the two optional tests are not conducted, assign CDc the default value of 0.20. Table 6 specifies test conditions for these six tests.

b. For units having a variable speed indoor blower that is modulated to adjust the sensible to total (S/T) cooling capacity ratio, use cooling full-load and cooling minimum air volume rates that represent a normal installation. Additionally, if conducting the dry-coil tests, operate the unit in the same S/T capacity control mode as used for the B1 Test.

c. Test two-capacity, northern heat pumps (see section 1.2 of this appendix, Definitions) in the same way as a single speed heat pump with the unit operating exclusively at low compressor capacity (see section 3.2.1 of this appendix and Table 5).

d. If a two-capacity air conditioner or heat pump locks out low-capacity operation at higher outdoor temperatures, then use the two dry-coil tests, the steady-state C2 Test and the cyclic D2 Test, to determine the cooling-mode cyclic-degradation coefficient that only applies to on/off cycling from high capacity, CD c(k=2). If the two optional tests are conducted but yield a tested CD c (k = 2) that exceeds the default CD c (k = 2) or if the two optional tests are not conducted, assign CD c (k = 2) the default value. The default CD c(k=2) is the same value as determined or assigned for the low-capacity cyclic-degradation coefficient, CD c [or equivalently, CD c(k=1)].

Table 7—Cooling Mode Test Conditions for Units Having a Two-Capacity Compressor

Test description Air entering indoor unit temperature ( °F) Air entering outdoor unit temperature ( °F) Compressor
capacity
Cooling air volume rate Dry bulb Wet bulb Dry bulb Wet bulb A2 Test—required (steady, wet coil)8067951 75HighCooling Full-Load. 2B2 Test—required (steady, wet coil)8067821 65HighCooling Full-Load. 2B1 Test—required (steady, wet coil)8067821 65LowCooling Minimum. 3C2 Test—optional (steady, dry-coil)80( 4)82HighCooling Full-Load. 2D2 Test—optional (cyclic, dry-coil)80( 4)82High( 5). C1 Test—optional (steady, dry-coil)80( 4)82LowCooling Minimum. 3D1 Test—optional (cyclic, dry-coil)80( 4)82Low( 6). F1 Test—required (steady, wet coil)8067671 53.5LowCooling Minimum. 3

1 The specified test condition only applies if the unit rejects condensate to the outdoor coil.

2 Defined in section 3.1.4.1 of this appendix.

3 Defined in section 3.1.4.2 of this appendix.

4 The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air wet-bulb temperature of 57 °F or less.

5 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the C2 Test.

6 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the C1 Test.

3.2.4 Tests for a Unit Having a Variable-Speed Compressor

a. Conduct five steady-state wet coil tests: The A2, EV, B2, B1, and F1 Tests. Use the two optional dry-coil tests, the steady-state G1 Test and the cyclic I1 Test, to determine the cooling mode cyclic degradation coefficient, CD c. If the two optional tests are conducted but yield a tested CDc that exceeds the default CDc or if the two optional tests are not conducted, assign CDc the default value of 0.25. Table 8 specifies test conditions for these seven tests. The compressor shall operate at the same cooling full speed, measured by RPM or power input frequency (Hz), for both the A2 and B2 tests. The compressor shall operate at the same cooling minimum speed, measured by RPM or power input frequency (Hz), for the B1, F1, G1, and I1 tests. Determine the cooling intermediate compressor speed cited in Table 8 using:

where a tolerance of plus 5 percent or the next higher inverter frequency step from that calculated is allowed.

b. For units that modulate the indoor blower speed to adjust the sensible to total (S/T) cooling capacity ratio, use cooling full-load, cooling intermediate, and cooling minimum air volume rates that represent a normal installation. Additionally, if conducting the dry-coil tests, operate the unit in the same S/T capacity control mode as used for the F1 Test.

c. For multiple-split air conditioners and heat pumps (except where noted), the following procedures supersede the above requirements: For all Table 8 tests specified for a minimum compressor speed, at least one indoor unit must be turned off. The manufacturer shall designate the particular indoor unit(s) that is turned off. The manufacturer must also specify the compressor speed used for the Table 8 EV Test, a cooling-mode intermediate compressor speed that falls within 1/4 and 3/4 of the difference between the full and minimum cooling-mode speeds. The manufacturer should prescribe an intermediate speed that is expected to yield the highest EER for the given EV Test conditions and bracketed compressor speed range. The manufacturer can designate that one or more indoor units are turned off for the EV Test.

Table 8—Cooling Mode Test Condition for Units Having a Variable-Speed Compressor

Test description Air entering indoor unit
temperature ( °F)
Air entering outdoor unit
temperature ( °F)
Compressor speed Cooling air
volume rate
Dry bulb Wet bulb Dry bulb Wet bulb A2 Test—required (steady, wet coil)8067951 75Cooling FullCooling Full-Load. 2B2 Test—required (steady, wet coil)8067821 65Cooling FullCooling Full-Load. 2EV Test—required (steady, wet coil)8067871 69Cooling IntermediateCooling Intermediate. 3B1 Test—required (steady, wet coil)8067821 65Cooling MinimumCooling Minimum. 4F1 Test—required (steady, wet coil)8067671 53.5Cooling MinimumCooling Minimum. 4G1 Test 5—optional (steady, dry-coil)80( 6)67Cooling MinimumCooling Minimum. 4I1 Test 5—optional (cyclic, dry-coil)80( 6)67Cooling Minimum( 6).

1 The specified test condition only applies if the unit rejects condensate to the outdoor coil.

2 Defined in section 3.1.4.1 of this appendix.

3 Defined in section 3.1.4.3 of this appendix.

4 Defined in section 3.1.4.2 of this appendix.

5 The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air wet bulb temperature of 57 °F or less.

6 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity pressure as measured during the G1 Test.

3.2.5 Cooling Mode Tests for Northern Heat Pumps With Triple-Capacity Compressors

Test triple-capacity, northern heat pumps for the cooling mode in the same way as specified in section 3.2.3 of this appendix for units having a two-capacity compressor.

3.2.6 Tests for an Air Conditioner or Heat Pump Having a Single Indoor Unit Having Multiple Indoor Blowers and Offering Two Stages of Compressor Modulation

Conduct the cooling mode tests specified in section 3.2.3 of this appendix.

3.3 Test Procedures for Steady-State Wet Coil Cooling Mode Tests (the A, A2, A1, B, B2, B1, EV, and F1 Tests)

a. For the pretest interval, operate the test room reconditioning apparatus and the unit to be tested until maintaining equilibrium conditions for at least 30 minutes at the specified section 3.2 test conditions. Use the exhaust fan of the airflow measuring apparatus and, if installed, the indoor blower of the test unit to obtain and then maintain the indoor air volume rate and/or external static pressure specified for the particular test. Continuously record (see section 1.2 of this appendix, Definitions):

(1) The dry-bulb temperature of the air entering the indoor coil,

(2) The water vapor content of the air entering the indoor coil,

(3) The dry-bulb temperature of the air entering the outdoor coil, and

(4) For the section 2.2.4 of this appendix cases where its control is required, the water vapor content of the air entering the outdoor coil.

Refer to section 3.11 of this appendix for additional requirements that depend on the selected secondary test method.

b. After satisfying the pretest equilibrium requirements, make the measurements specified in Table 3 of ANSI/ASHRAE 37-2009 for the indoor air enthalpy method and the user-selected secondary method. Make said Table 3 measurements at equal intervals that span 5 minutes or less. Continue data sampling until reaching a 30-minute period (e.g., seven consecutive 5-minute samples) where the test tolerances specified in Table 9 are satisfied. For those continuously recorded parameters, use the entire data set from the 30-minute interval to evaluate Table 9 compliance. Determine the average electrical power consumption of the air conditioner or heat pump over the same 30-minute interval.

c. Calculate indoor-side total cooling capacity and sensible cooling capacity as specified in sections 7.3.3.1 and 7.3.3.3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3). To calculate capacity, use the averages of the measurements (e.g. inlet and outlet dry bulb and wet bulb temperatures measured at the psychrometers) that are continuously recorded for the same 30-minute interval used as described above to evaluate compliance with test tolerances. Do not adjust the parameters used in calculating capacity for the permitted variations in test conditions. Evaluate air enthalpies based on the measured barometric pressure. Use the values of the specific heat of air given in section 7.3.3.1 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3) for calculation of the sensible cooling capacities. Assign the average total space cooling capacity, average sensible cooling capacity, and electrical power consumption over the 30-minute data collection interval to the variables Q c k(T), Q sc k(T) and E c k(T), respectively. For these three variables, replace the “T” with the nominal outdoor temperature at which the test was conducted. The superscript k is used only when testing multi-capacity units.

Use the superscript k=2 to denote a test with the unit operating at high capacity or full speed, k=1 to denote low capacity or minimum speed, and k=v to denote the intermediate speed.

d. For coil-only system tests, decrease Q c k(T) by

and increase E c k(T) by,

where V s is the average measured indoor air volume rate expressed in units of cubic feet per minute of standard air (scfm).

Table 9—Test Operating and Test Condition Tolerances for Section 3.3 Steady-State Wet Coil Cooling Mode Tests and Section 3.4 Dry Coil Cooling Mode Tests

Test operating
tolerance 1
Test condition
tolerance 1
Indoor dry-bulb, °F Entering temperature2.00.5 Leaving temperature2.0 Indoor wet-bulb, °F Entering temperature1.02 0.3 Leaving temperature2 1.0 Outdoor dry-bulb, °F Entering temperature2.00.5 Leaving temperature3 2.0 Outdoor wet-bulb, °F Entering temperature1.04 0.3 Leaving temperature3 1.0 External resistance to airflow, inches of water0.055 0.02 Electrical voltage, % of rdg.2.01.5 Nozzle pressure drop, % of rdg.2.0

1 See section 1.2 of this appendix, Definitions.

2 Only applies during wet coil tests; does not apply during steady-state, dry coil cooling mode tests.

3 Only applies when using the outdoor air enthalpy method.

4 Only applies during wet coil cooling mode tests where the unit rejects condensate to the outdoor coil.

5 Only applies when testing non-ducted units.

e. For air conditioners and heat pumps having a constant-air-volume-rate indoor blower, the five additional steps listed below are required if the average of the measured external static pressures exceeds the applicable sections 3.1.4 minimum (or target) external static pressure (ΔPmin) by 0.03 inches of water or more.

(1) Measure the average power consumption of the indoor blower motor (E fan,1) and record the corresponding external static pressure (ΔP1) during or immediately following the 30-minute interval used for determining capacity.

(2) After completing the 30-minute interval and while maintaining the same test conditions, adjust the exhaust fan of the airflow measuring apparatus until the external static pressure increases to approximately ΔP1 + (ΔP1−ΔPmin).

(3) After re-establishing steady readings of the fan motor power and external static pressure, determine average values for the indoor blower power (E fan,2) and the external static pressure (ΔP2) by making measurements over a 5-minute interval.

(4) Approximate the average power consumption of the indoor blower motor at ΔPmin using linear extrapolation:

(5) Increase the total space cooling capacity, Q c k(T), by the quantity (E fan,1−E fan,min), when expressed on a Btu/h basis. Decrease the total electrical power, E c k(T), by the same fan power difference, now expressed in watts.

3.4 Test Procedures for the Steady-State Dry-Coil Cooling-Mode Tests (the C, C1, C2, and G1 Tests)

a. Except for the modifications noted in this section, conduct the steady-state dry coil cooling mode tests as specified in section 3.3 of this appendix for wet coil tests. Prior to recording data during the steady-state dry coil test, operate the unit at least one hour after achieving dry coil conditions. Drain the drain pan and plug the drain opening. Thereafter, the drain pan should remain completely dry.

b. Denote the resulting total space cooling capacity and electrical power derived from the test as Q ss,dry and E ss,dry. With regard to a section 3.3 deviation, do not adjust Q ss,dry for duct losses (i.e., do not apply section 7.3.3.3 of ANSI/ASHRAE 37-2009). In preparing for the section 3.5 cyclic tests of this appendix, record the average indoor-side air volume rate, V , specific heat of the air, Cp,a (expressed on dry air basis), specific volume of the air at the nozzles, v′n, humidity ratio at the nozzles, Wn, and either pressure difference or velocity pressure for the flow nozzles. For units having a variable-speed indoor blower (that provides either a constant or variable air volume rate) that will or may be tested during the cyclic dry coil cooling mode test with the indoor blower turned off (see section 3.5 of this appendix), include the electrical power used by the indoor blower motor among the recorded parameters from the 30-minute test.

c. If the temperature sensors used to provide the primary measurement of the indoor-side dry bulb temperature difference during the steady-state dry-coil test and the subsequent cyclic dry-coil test are different, include measurements of the latter sensors among the regularly sampled data. Beginning at the start of the 30-minute data collection period, measure and compute the indoor-side air dry-bulb temperature difference using both sets of instrumentation, ΔT (Set SS) and ΔT (Set CYC), for each equally spaced data sample. If using a consistent data sampling rate that is less than 1 minute, calculate and record minutely averages for the two temperature differences. If using a consistent sampling rate of one minute or more, calculate and record the two temperature differences from each data sample. After having recorded the seventh (i=7) set of temperature differences, calculate the following ratio using the first seven sets of values:

Each time a subsequent set of temperature differences is recorded (if sampling more frequently than every 5 minutes), calculate FCD using the most recent seven sets of values. Continue these calculations until the 30-minute period is completed or until a value for FCD is calculated that falls outside the allowable range of 0.94-1.06. If the latter occurs, immediately suspend the test and identify the cause for the disparity in the two temperature difference measurements. Recalibration of one or both sets of instrumentation may be required. If all the values for FCD are within the allowable range, save the final value of the ratio from the 30-minute test as FCD*. If the temperature sensors used to provide the primary measurement of the indoor-side dry bulb temperature difference during the steady-state dry-coil test and the subsequent cyclic dry-coil test are the same, set FCD*= 1.

3.5 Test Procedures for the Cyclic Dry-Coil Cooling-Mode Tests (the D, D1, D2, and I1 Tests)

After completing the steady-state dry-coil test, remove the outdoor air enthalpy method test apparatus, if connected, and begin manual OFF/ON cycling of the unit's compressor. The test set-up should otherwise be identical to the set-up used during the steady-state dry coil test. When testing heat pumps, leave the reversing valve during the compressor OFF cycles in the same position as used for the compressor ON cycles, unless automatically changed by the controls of the unit. For units having a variable-speed indoor blower, the manufacturer has the option of electing at the outset whether to conduct the cyclic test with the indoor blower enabled or disabled. Always revert to testing with the indoor blower disabled if cyclic testing with the fan enabled is unsuccessful.

a. For all cyclic tests, the measured capacity must be adjusted for the thermal mass stored in devices and connections located between measured points. Follow the procedure outlined in section 7.4.3.4.5 of ASHRAE 116-2010 (incorporated by reference, see § 430.3) to ensure any required measurements are taken.

b. For units having a single-speed or two-capacity compressor, cycle the compressor OFF for 24 minutes and then ON for 6 minutes (Δτcyc,dry = 0.5 hours). For units having a variable-speed compressor, cycle the compressor OFF for 48 minutes and then ON for 12 minutes (Δτcyc,dry = 1.0 hours). Repeat the OFF/ON compressor cycling pattern until the test is completed. Allow the controls of the unit to regulate cycling of the outdoor fan. If an upturned duct is used, measure the dry-bulb temperature at the inlet of the device at least once every minute and ensure that its test operating tolerance is within 1.0 °F for each compressor OFF period.

c. Sections 3.5.1 and 3.5.2 of this appendix specify airflow requirements through the indoor coil of ducted and non-ducted indoor units, respectively. In all cases, use the exhaust fan of the airflow measuring apparatus (covered under section 2.6 of this appendix) along with the indoor blower of the unit, if installed and operating, to approximate a step response in the indoor coil airflow. Regulate the exhaust fan to quickly obtain and then maintain the flow nozzle static pressure difference or velocity pressure at the same value as was measured during the steady-state dry coil test. The pressure difference or velocity pressure should be within 2 percent of the value from the steady-state dry coil test within 15 seconds after airflow initiation. For units having a variable-speed indoor blower that ramps when cycling on and/or off, use the exhaust fan of the airflow measuring apparatus to impose a step response that begins at the initiation of ramp up and ends at the termination of ramp down.

d. For units having a variable-speed indoor blower, conduct the cyclic dry coil test using the pull-thru approach described below if any of the following occur when testing with the fan operating:

(1) The test unit automatically cycles off;

(2) Its blower motor reverses; or

(3) The unit operates for more than 30 seconds at an external static pressure that is 0.1 inches of water or more higher than the value measured during the prior steady-state test.

For the pull-thru approach, disable the indoor blower and use the exhaust fan of the airflow measuring apparatus to generate the specified flow nozzles static pressure difference or velocity pressure. If the exhaust fan cannot deliver the required pressure difference because of resistance created by the unpowered indoor blower, temporarily remove the indoor blower.

e. Conduct three complete compressor OFF/ON cycles with the test tolerances given in Table 10 satisfied. Calculate the degradation coefficient CD for each complete cycle. If all three CD values are within 0.02 of the average CD then stability has been achieved, and the highest CD value of these three shall be used. If stability has not been achieved, conduct additional cycles, up to a maximum of eight cycles total, until stability has been achieved between three consecutive cycles. Once stability has been achieved, use the highest CD value of the three consecutive cycles that establish stability. If stability has not been achieved after eight cycles, use the highest CD from cycle one through cycle eight, or the default CD, whichever is lower.

f. With regard to the Table 10 parameters, continuously record the dry-bulb temperature of the air entering the indoor and outdoor coils during periods when air flows through the respective coils. Sample the water vapor content of the indoor coil inlet air at least every 2 minutes during periods when air flows through the coil. Record external static pressure and the air volume rate indicator (either nozzle pressure difference or velocity pressure) at least every minute during the interval that air flows through the indoor coil. (These regular measurements of the airflow rate indicator are in addition to the required measurement at 15 seconds after flow initiation.) Sample the electrical voltage at least every 2 minutes beginning 30 seconds after compressor start-up. Continue until the compressor, the outdoor fan, and the indoor blower (if it is installed and operating) cycle off.

g. For ducted units, continuously record the dry-bulb temperature of the air entering (as noted above) and leaving the indoor coil. Or if using a thermopile, continuously record the difference between these two temperatures during the interval that air flows through the indoor coil. For non-ducted units, make the same dry-bulb temperature measurements beginning when the compressor cycles on and ending when indoor coil airflow ceases.

h. Integrate the electrical power over complete cycles of length Δτcyc,dry. For ducted blower coil systems tested with the unit's indoor blower operating for the cycling test, integrate electrical power from indoor blower OFF to indoor blower OFF. For all other ducted units and for non-ducted units, integrate electrical power from compressor OFF to compressor OFF. (Some cyclic tests will use the same data collection intervals to determine the electrical energy and the total space cooling. For other units, terminate data collection used to determine the electrical energy before terminating data collection used to determine total space cooling.)

Table 10—Test Operating and Test Condition Tolerances for Cyclic Dry Coil Cooling Mode Tests

Test operating tolerance 1Test condition tolerance 1Indoor entering dry-bulb temperature, 2 °F2.00.5 Indoor entering wet-bulb temperature, °F( 3) Outdoor entering dry-bulb temperature, 2 °F2.00.5 External resistance to airflow, 2 inches of water0.05 Airflow nozzle pressure difference or velocity pressure, 2 % of reading2.04 2.0 Electrical voltage, 5 % of rdg2.01.5

1 See section 1.2 of this appendix, Definitions.

2 Applies during the interval that air flows through the indoor (outdoor) coil except for the first 30 seconds after flow initiation. For units having a variable-speed indoor blower that ramps, the tolerances listed for the external resistance to airflow apply from 30 seconds after achieving full speed until ramp down begins.

3 Shall at no time exceed a wet-bulb temperature that results in condensate forming on the indoor coil.

4 The test condition shall be the average nozzle pressure difference or velocity pressure measured during the steady-state dry coil test.

5 Applies during the interval when at least one of the following—the compressor, the outdoor fan, or, if applicable, the indoor blower—are operating except for the first 30 seconds after compressor start-up.

If the Table 10 tolerances are satisfied over the complete cycle, record the measured electrical energy consumption as ecyc,dry and express it in units of watt-hours. Calculate the total space cooling delivered, qcyc,dry, in units of Btu using,

Where, V , Cp,a, vn′ (or vn), Wn, and FCD* are the values recorded during the section 3.4 dry coil steady-state test and Tal(τ) = dry bulb temperature of the air entering the indoor coil at time τ, °F. Ta2(τ) = dry bulb temperature of the air leaving the indoor coil at time τ, °F. τ1 = for ducted units, the elapsed time when airflow is initiated through the indoor coil; for non-ducted units, the elapsed time when the compressor is cycled on, hr. τ2 = the elapsed time when indoor coil airflow ceases, hr.

Adjust the total space cooling delivered, qcyc,dry, according to calculation method outlined in section 7.4.3.4.5 of ASHRAE 116-2010 (incorporated by reference, see § 430.3).

3.5.1 Procedures When Testing Ducted Systems

The automatic controls that are installed in the test unit must govern the OFF/ON cycling of the air moving equipment on the indoor side (exhaust fan of the airflow measuring apparatus and the indoor blower of the test unit). For ducted coil-only systems rated based on using a fan time-delay relay, control the indoor coil airflow according to the OFF delay listed by the manufacturer in the certification report. For ducted units having a variable-speed indoor blower that has been disabled (and possibly removed), start and stop the indoor airflow at the same instances as if the fan were enabled. For all other ducted coil-only systems, cycle the indoor coil airflow in unison with the cycling of the compressor. If air damper boxes are used, close them on the inlet and outlet side during the OFF period. Airflow through the indoor coil should stop within 3 seconds after the automatic controls of the test unit (act to) de-energize the indoor blower. For ducted coil-only systems (excluding the special case where a variable-speed fan is temporarily removed), increase ecyc,dry by the quantity,

and decrease qcyc,dry by,

where V s is the average indoor air volume rate from the section 3.4 dry coil steady-state test and is expressed in units of cubic feet per minute of standard air (scfm). For units having a variable-speed indoor blower that is disabled during the cyclic test, increase ecyc,dry and decrease qcyc,dry based on: a. The product of [τ2 - τ1] and the indoor blower power measured during or following the dry coil steady-state test; or, b. The following algorithm if the indoor blower ramps its speed when cycling.

(1) Measure the electrical power consumed by the variable-speed indoor blower at a minimum of three operating conditions: At the speed/air volume rate/external static pressure that was measured during the steady-state test, at operating conditions associated with the midpoint of the ramp-up interval, and at conditions associated with the midpoint of the ramp-down interval. For these measurements, the tolerances on the airflow volume or the external static pressure are the same as required for the section 3.4 steady-state test.

(2) For each case, determine the fan power from measurements made over a minimum of 5 minutes.

(3) Approximate the electrical energy consumption of the indoor blower if it had operated during the cyclic test using all three power measurements. Assume a linear profile during the ramp intervals. The manufacturer must provide the durations of the ramp-up and ramp-down intervals. If the test setup instructions included with the unit by the manufacturer specifies a ramp interval that exceeds 45 seconds, use a 45-second ramp interval nonetheless when estimating the fan energy.

3.5.2 Procedures When Testing Non-Ducted Indoor Units

Do not use airflow prevention devices when conducting cyclic tests on non-ducted indoor units. Until the last OFF/ON compressor cycle, airflow through the indoor coil must cycle off and on in unison with the compressor. For the last OFF/ON compressor cycle—the one used to determine ecyc,dry and qcyc,dry—use the exhaust fan of the airflow measuring apparatus and the indoor blower of the test unit to have indoor airflow start 3 minutes prior to compressor cut-on and end three minutes after compressor cutoff. Subtract the electrical energy used by the indoor blower during the 3 minutes prior to compressor cut-on from the integrated electrical energy, ecyc,dry. Add the electrical energy used by the indoor blower during the 3 minutes after compressor cutoff to the integrated cooling capacity, qcyc,dry. For the case where the non-ducted indoor unit uses a variable-speed indoor blower which is disabled during the cyclic test, correct ecyc,dry and qcyc,dry using the same approach as prescribed in section 3.5.1 of this appendix for ducted units having a disabled variable-speed indoor blower.

3.5.3 Cooling-Mode Cyclic-Degradation Coefficient Calculation

Use the two dry-coil tests to determine the cooling-mode cyclic-degradation coefficient, CD c. Append “(k=2)” to the coefficient if it corresponds to a two-capacity unit cycling at high capacity. If the two optional tests are conducted but yield a tested CD c that exceeds the default CD c or if the two optional tests are not conducted, assign CD c the default value of 0.25 for variable-speed compressor systems and outdoor units with no match, and 0.20 for all other systems. The default value for two-capacity units cycling at high capacity, however, is the low-capacity coefficient, i.e., CD c(k=2) = CD c. Evaluate CD c using the above results and those from the section 3.4 dry-coil steady-state test.

where: the average energy efficiency ratio during the cyclic dry coil cooling mode test, Btu/W·h the average energy efficiency ratio during the steady-state dry coil cooling mode test, Btu/W·h the cooling load factor dimensionless Round the calculated value for CD c to the nearest 0.01. If CD c is negative, then set it equal to zero. 3.6 Heating Mode Tests for Different Types of Heat Pumps, Including Heating-Only Heat Pumps 3.6.1 Tests for a Heat Pump Having a Single-Speed Compressor and Fixed Heating Air Volume Rate

This set of tests is for single-speed-compressor heat pumps that do not have a heating minimum air volume rate or a heating intermediate air volume rate that is different than the heating full load air volume rate. Conduct the optional high temperature cyclic (H1C) test to determine the heating mode cyclic-degradation coefficient, CD h. If this optional test is conducted but yields a tested CD h that exceeds the default CD h or if the optional test is not conducted, assign CD h the default value of 0.25. Test conditions for the four tests are specified in Table 10.

Table 11—Heating Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed-Speed Indoor Blower, a Constant Air Volume Rate Indoor Blower, or No Indoor Blower

Test description Air entering indoor unit
temperature
( °F)
Air entering outdoor unit
temperature
( °F)
Heating air volume rate Dry bulb Wet bulb Dry bulb Wet bulb H1 Test (required, steady)7060 (max)4743Heating Full-load. 1H1C Test (optional, cyclic)7060 (max)4743( 2) H2 Test (required)7060 (max)3533Heating Full-load. 1H3 Test (required, steady)7060 (max)1715Heating Full-load. 1

1 Defined in section 3.1.4.4 of this appendix. f 2 Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity pressure as measured during the H1 Test.

3.6.2 Tests for a Heat Pump Having a Single-Speed Compressor and a Single Indoor Unit Having Either (1) a Variable Speed, Variable-Air-Rate Indoor Blower Whose Capacity Modulation Correlates With Outdoor Dry Bulb Temperature or (2) Multiple Indoor Blowers

Conduct five tests: Two high temperature tests (H12 and H11), one frost accumulation test (H22), and two low temperature tests (H32 and H31). Conducting an additional frost accumulation test (H21) is optional. Conduct the optional high temperature cyclic (H1C1) test to determine the heating mode cyclic-degradation coefficient, CD h. If this optional test is conducted but yields a tested CD h that exceeds the default CD h or if the optional test is not conducted, assign CD h the default value of 0.25. Test conditions for the seven tests are specified in Table 12. If the optional H21 test is not performed, use the following equations to approximate the capacity and electrical power of the heat pump at the H21 test conditions:

The quantities Q hk=2(47), E hk=2(47), Q hk=1(47), and E hk=1(47) are determined from the H12 and H11 tests and evaluated as specified in section 3.7 of this appendix; the quantities Q hk=2(35) and E hk=2(35) are determined from the H22 test and evaluated as specified in section 3.9 of this appendix; and the quantities Q hk=2(17), E hk=2(17), Q hk=1(17), and E hk=1(17), are determined from the H32 and H31 tests and evaluated as specified in section 3.10 of this appendix.

Table 12—Table Heating Mode Test Conditions for Units With a Single-Speed Compressor That Meet the Section 3.6.2 Indoor Unit Requirements

Test description Air entering indoor unit
temperature
( °F)
Air entering outdoor unit
temperature
( °F)
Heating air volume rate Dry bulb Wet bulb Dry bulb Wet bulb H12 Test (required, steady)7060 (max)4743Heating Full-load. 1H11 Test (required, steady)7060 (max)4743Heating Minimum. 2H1C1 Test (optional, cyclic)7060 (max)4743( 3) H22 Test (required)7060 (max)3533Heating Full-load. 1H21 Test (optional)7060 (max)3533Heating Minimum. 2H32 Test (required, steady)7060 (max)1715Heating Full-load. 1H31 Test (required, steady)7060 (max)1715Heating Minimum. 2

1 Defined in section 3.1.4.4 of this appendix.

2 Defined in section 3.1.4.5 of this appendix.

3 Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity pressure as measured during the H11 test.

3.6.3 Tests for a Heat Pump Having a Two-Capacity Compressor (see section 1.2 of this appendix, Definitions), Including Two-Capacity, Northern Heat Pumps (see section 1.2 of this appendix, Definitions)

a. Conduct one maximum temperature test (H01), two high temperature tests (H12and H11), one frost accumulation test (H22), and one low temperature test (H32). Conduct an additional frost accumulation test (H21) and low temperature test (H31) if both of the following conditions exist:

(1) Knowledge of the heat pump's capacity and electrical power at low compressor capacity for outdoor temperatures of 37 °F and less is needed to complete the section 4.2.3 of this appendix seasonal performance calculations; and

(2) The heat pump's controls allow low-capacity operation at outdoor temperatures of 37 °F and less.

If the above two conditions are met, an alternative to conducting the H21 frost accumulation is to use the following equations to approximate the capacity and electrical power:

Determine the quantities Q hk=1 (47) and E hk=1 (47) from the H11 test and evaluate them according to section 3.7 of this appendix. Determine the quantities Q hk=1 (17) and E hk=1 (17) from the H31 test and evaluate them according to section 3.10 of this appendix.

b. Conduct the optional high temperature cyclic test (H1C1) to determine the heating mode cyclic-degradation coefficient, CD h. If this optional test is conducted but yields a tested CD h that exceeds the default CD h or if the optional test is not conducted, assign CD h the default value of 0.25. If a two-capacity heat pump locks out low capacity operation at lower outdoor temperatures, conduct the high temperature cyclic test (H1C 2) to determine the high-capacity heating mode cyclic-degradation coefficient, CD h (k=2). If this optional test at high capacity is conducted but yields a tested CD h (k = 2) that exceeds the default CD h (k = 2) or if the optional test is not conducted, assign CD h the default value. The default CD h (k=2) is the same value as determined or assigned for the low-capacity cyclic-degradation coefficient, CD h [or equivalently, CD h (k=1)]. Table 13 specifies test conditions for these nine tests.

Table 13—Heating Mode Test Conditions for Units Having a Two-Capacity Compressor

Test description Air entering indoor unit
temperature
( °F)
Air entering outdoor unit
temperature
( °F)
Compressor capacity Heating air volume rate Dry bulb Wet bulb Dry bulb Wet bulb H01 Test (required, steady)7060 (max)6256.5Low Heating Minimum. 1H12 Test (required, steady)7060 (max)4743High Heating Full-Load. 2H1C2 Test (optional 7, cyclic)7060 (max)4743High( 3) H11 Test (required)7060 (max)4743Low Heating Minimum. 1H1C1 Test (optional, cyclic)7060 (max)4743Low( 4) H22 Test (required)7060 (max)3533High Heating Full-Load. 2H21 Test 5 6 (required)7060 (max)3533Low Heating Minimum. 1H32 Test (required, steady)7060 (max)1715High Heating Full-Load. 2H31 Test 5 (required, steady)7060 (max)1715Low Heating Minimum. 1

1 Defined in section 3.1.4.5 of this appendix.

2 Defined in section 3.1.4.4 of this appendix.

3 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the H12 test.

4 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the H11 test.

5 Required only if the heat pump's performance when operating at low compressor capacity and outdoor temperatures less than 37 °F is needed to complete the section 4.2.3 HSPF calculations.

6 If table note #5 applies, the section 3.6.3 equations for Q hk=1 (35) and E hk=1 (17) may be used in lieu of conducting the H21 test.

7 Required only if the heat pump locks out low capacity operation at lower outdoor temperatures.

3.6.4 Tests for a Heat Pump Having a Variable-Speed Compressor

a. Conduct one maximum temperature test (H01), two high temperature tests (H1N and H11), one frost accumulation test (H2V), and one low temperature test (H32). Conducting one or both of the following tests is optional: An additional high temperature test (H12) and an additional frost accumulation test (H22). If desired, conduct the optional maximum temperature cyclic (H0C1) test to determine the heating mode cyclic-degradation coefficient, CD h. If this optional test is conducted but yields a tested CD h that exceeds the default CD h or if the optional test is not conducted, assign CD h the default value of 0.25. Test conditions for the eight tests are specified in Table 14 to this appendix. The compressor shall operate at the same heating full speed, measured by RPM or power input frequency (Hz), for the H12, H22 and H32 tests. For a cooling/heating heat pump, the compressor shall operate for the H1N test at a speed, measured by RPM or power input frequency (Hz), no lower than the speed used in the A2 test if the tested H1N heating capacity is less than the tested A2 cooling capacity. The compressor shall operate at the same heating minimum speed, measured by RPM or power input frequency (Hz), for the H01, H1C1, and H11 tests. Determine the heating intermediate compressor speed cited in Table 14 using the heating mode full and minimum compressors speeds and:

Where a tolerance on speed of plus 5 percent or the next higher inverter frequency step from the calculated value is allowed.

b. If the H12 test is conducted, set the 47 °F capacity and power input values used for calculation of HSPF equal to the measured values for that test:

Where:

Q hcalck=2(47) and E hcalck=2(47) are the capacity and power input representing full-speed operation at 47 °F for the HSPF calculations,

Q hk=2(47) is the capacity measured in the H12 test, and

E hk=2(47) is the power input measured in the H12 test.

Evaluate the quantities Q hk=2(47) and from E hk=2(47) according to section 3.7.

Otherwise, if the H1N test is conducted using the same compressor speed (RPM or power input frequency) as the H32 test, set the 47 °F capacity and power input values used for calculation of HSPF equal to the measured values for that test:

Where: Q hcalck=2(47) and E hcalck=2(47) are the capacity and power input representing full-speed operation at 47 °F for the HSPF calculations, Q hk=N(47) is the capacity measured in the H1N test, and E hk=N(47) is the power input measured in the H1N test.

Evaluate the quantities Q hk=N(47) and from E hk=N(47) according to section 3.7.

Otherwise (if no high temperature test is conducted using the same speed (RPM or power input frequency) as the H32 test), calculate the 47 °F capacity and power input values used for calculation of HSPF as follows:

Where: Q hcalck=2(47) and E hcalck=2(47) are the capacity and power input representing full-speed operation at 47 °F for the HSPF calculations, Q hk=2(17) is the capacity measured in the H32 test, E hk=2(17) is the power input measured in the H32 test, CSF is the capacity slope factor, equal to 0.0204/ °F for split systems and 0.0262/ °F for single-package systems, and PSF is the Power Slope Factor, equal to 0.00455/ °F.

c. If the H22 test is not done, use the following equations to approximate the capacity and electrical power at the H22 test conditions:

Where: Q hcalck=2(47) and E hcalck=2(47) are the capacity and power input representing full-speed operation at 47 °F for the HSPF calculations, calculated as described in section b above. Q hk=2(17) and E hk=2(17) are the capacity and power input measured in the H32 test.

d. Determine the quantities Q hk=2(17) and E hk=2(17) from the H32 test, determine the quantities Q hk=2(5) and E hk=2(5) from the H42 test, and evaluate all four according to section 3.10.

Table 14—Heating Mode Test Conditions for Units Having a Variable-Speed Compressor

Test description Air entering indoor unit
temperature ( °F)
Air entering outdoor unit
temperature ( °F)
Compressor speed Heating air volume rate Dry bulb Wet bulb Dry bulb Wet bulb H01 test (required, steady)7060 (max)6256.5Heating minimumHeating minimum. 1H12 test (optional, steady)7060 (max)4743Heating full 4Heating full-load. 3H11 test (required, steady)7060 (max)4743Heating minimumHeating minimum. 1H1N test (required, steady)7060 (max)4743Heating fullHeating full-load. 3H1C1 test (optional, cyclic)7060 (max)4743Heating minimum( 2) H22 test (optional)7060 (max)3533Heating full 4Heating full-load. 3H2V test (required)7060 (max)3533Heating intermediateHeating intermediate. 5H32 test (required, steady)7060 (max)1715Heating fullHeating full-load. 3

1 Defined in section 3.1.4.5 of this appendix.

2 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during an ON period at the same pressure or velocity as measured during the H11 test.

3 Defined in section 3.1.4.4 of this appendix.

4 The same compressor speed used in the H32 test. The H12 test is not needed if the H1N test uses this same compressor speed.

5 Defined in section 3.1.4.6 of this appendix.

3.6.5 Additional Test for a Heat Pump Having a Heat Comfort Controller

Test any heat pump that has a heat comfort controller (see section 1.2 of this appendix, Definitions) according to section 3.6.1, 3.6.2, or 3.6.3, whichever applies, with the heat comfort controller disabled. Additionally, conduct the abbreviated test described in section 3.1.10 of this appendix with the heat comfort controller active to determine the system's maximum supply air temperature. (Note: Heat pumps having a variable speed compressor and a heat comfort controller are not covered in the test procedure at this time.)

3.6.6 Heating Mode Tests for Northern Heat Pumps With Triple-Capacity Compressors.

Test triple-capacity, northern heat pumps for the heating mode as follows:

a. Conduct one maximum-temperature test (H01), two high-temperature tests (H12 and H11), one frost accumulation test (H22), two low-temperature tests (H32, H33), and one minimum-temperature test (H43). Conduct an additional frost accumulation test (H21) and low-temperature test (H31) if both of the following conditions exist: (1) Knowledge of the heat pump's capacity and electrical power at low compressor capacity for outdoor temperatures of 37 °F and less is needed to complete the section 4.2.6 seasonal performance calculations; and (2) the heat pump's controls allow low-capacity operation at outdoor temperatures of 37 °F and less. If the above two conditions are met, an alternative to conducting the H21 frost accumulation test to determine Q hk=1(35) and E hk=1(35) is to use the following equations to approximate this capacity and electrical power:

In evaluating the above equations, determine the quantities Q hk=1(47) from the H11 test and evaluate them according to section 3.7 of this appendix. Determine the quantities Q hk=1(17) and E hk=1(17) from the H31 test and evaluate them according to section 3.10 of this appendix. Use the paired values of Q hk=1(35) and E hk=1(35) derived from conducting the H21 frost accumulation test and evaluated as specified in section 3.9.1 of this appendix or use the paired values calculated using the above default equations, whichever contribute to a higher Region IV HSPF based on the DHRmin.

b. Conducting a frost accumulation test (H23) with the heat pump operating at its booster capacity is optional. If this optional test is not conducted, determine Q h k=3(35) and E hk=3(35) using the following equations to approximate this capacity and electrical power:

Where:

Determine the quantities Q hk=2(47) and E hk=2(47) from the H12 test and evaluate them according to section 3.7 of this appendix. Determine the quantities Q hk=2(35) and E hk=2(35) from the H22 test and evaluate them according to section 3.9.1 of this appendix. Determine the quantities Q hk=2(17) and E hk=2(17) from the H32 test, determine the quantities Q h k=3(17) and E hk=3(17) from the H33 test, and determine the quantities Q hk=3(5) and E hk=3(5) from the H43 test. Evaluate all six quantities according to section 3.10 of this appendix. Use the paired values of Q hk=3(35) and E hk=3(35) derived from conducting the H23 frost accumulation test and calculated as specified in section 3.9.1 of this appendix or use the paired values calculated using the above default equations, whichever contribute to a higher Region IV HSPF based on the DHRmin.

c. Conduct the optional high-temperature cyclic test (H1C1) to determine the heating mode cyclic-degradation coefficient, CD h. A default value for CD h may be used in lieu of conducting the cyclic. The default value of CD h is 0.25. If a triple-capacity heat pump locks out low capacity operation at lower outdoor temperatures, conduct the high-temperature cyclic test (H1C2) to determine the high-capacity heating mode cyclic-degradation coefficient, CD h (k=2). The default CD h (k=2) is the same value as determined or assigned for the low-capacity cyclic-degradation coefficient, CD h [or equivalently, CD h (k=1)]. Finally, if a triple-capacity heat pump locks out both low and high capacity operation at the lowest outdoor temperatures, conduct the low-temperature cyclic test (H3C3) to determine the booster-capacity heating mode cyclic-degradation coefficient, CD h (k=3). The default CD h (k=3) is the same value as determined or assigned for the high-capacity cyclic-degradation coefficient, CD h [or equivalently, CD h (k=2)]. Table 15 specifies test conditions for all 13 tests.

Table 15—Heating Mode Test Conditions for Units With a Triple-Capacity Compressor

Test description Air entering indoor unit
temperature
°F
Air entering outdoor unit
temperature
°F
Compressor capacity Heating air volume rate Dry bulb Wet bulb Dry bulb Wet bulb H01 Test (required, steady)7060 (max)6256.5LowHeating Minimum. 1H12 Test (required, steady)7060 (max)4743HighHeating Full-Load. 2H1C2 Test (optional, 8 cyclic)7060 (max)4743High( 3). H11 Test (required)7060 (max)4743LowHeating Minimum. 1H1C1 Test (optional, cyclic)7060 (max)4743Low( 4). H23 Test (optional, steady)7060 (max)3533BoosterHeating Full-Load. 2H22 Test (required)7060 (max)3533HighHeating Full-Load. 2H21 Test (required)7060 (max)3533LowHeating Minimum. 1H33 Test (required, steady)7060 (max)1715BoosterHeating Full-Load. 2H3C3 Test 5 6 (optional, cyclic)7060 (max)1715Booster( 7). H32 Test (required, steady)7060 (max)1715HighHeating Full-Load. 2H31 Test 5 (required, steady)7060 (max)1715LowHeating Minimum. 1H43 Test (required, steady)7060 (max)53 (max)BoosterHeating Full-Load. 2

1 Defined in section 3.1.4.5 of this appendix.

2 Defined in section 3.1.4.4 of this appendix.

3 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the H12 test.

4 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the H11 test.

5 Required only if the heat pump's performance when operating at low compressor capacity and outdoor temperatures less than 37 °F is needed to complete the section 4.2.6 HSPF calculations.

6 If table note 5 applies, the section 3.6.6 equations for Q hk=1(35) and E hk=1(17) may be used in lieu of conducting the H21 test.

7 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the H33 test.

8 Required only if the heat pump locks out low capacity operation at lower outdoor temperatures.

3.6.7 Tests for a Heat Pump Having a Single Indoor Unit Having Multiple Indoor Blowers and Offering Two Stages of Compressor Modulation

Conduct the heating mode tests specified in section 3.6.3 of this appendix.

3.7 Test Procedures for Steady-State Maximum Temperature and High Temperature Heating Mode Tests (the H01, H1, H12, H11, and H1N Tests)

a. For the pretest interval, operate the test room reconditioning apparatus and the heat pump until equilibrium conditions are maintained for at least 30 minutes at the specified section 3.6 test conditions. Use the exhaust fan of the airflow measuring apparatus and, if installed, the indoor blower of the heat pump to obtain and then maintain the indoor air volume rate and/or the external static pressure specified for the particular test. Continuously record the dry-bulb temperature of the air entering the indoor coil, and the dry-bulb temperature and water vapor content of the air entering the outdoor coil. Refer to section 3.11 of this appendix for additional requirements that depend on the selected secondary test method. After satisfying the pretest equilibrium requirements, make the measurements specified in Table 3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3) for the indoor air enthalpy method and the user-selected secondary method. Make said Table 3 measurements at equal intervals that span 5 minutes or less. Continue data sampling until a 30-minute period (e.g., seven consecutive 5-minute samples) is reached where the test tolerances specified in Table 16 are satisfied. For those continuously recorded parameters, use the entire data set for the 30-minute interval when evaluating Table 16 compliance. Determine the average electrical power consumption of the heat pump over the same 30-minute interval.

Table 16—Test Operating and Test Condition Tolerances for Section 3.7 and Section 3.10 Steady-State Heating Mode Tests

Test operating
tolerance 1
Test condition
tolerance 1
Indoor dry-bulb, °F: Entering temperature2.00.5 Leaving temperature2.0 Indoor wet-bulb, °F: Entering temperature1.0 Leaving temperature1.0 Outdoor dry-bulb, °F: Entering temperature2.00.5 Leaving temperature2 2.0 Outdoor wet-bulb, °F: Entering temperature1.00.3 Leaving temperature2 1.0 External resistance to airflow, inches of water0.053 0.02 Electrical voltage, % of rdg2.01.5 Nozzle pressure drop, % of rdg2.0

1 See section 1.2 of this appendix, Definitions.

2 Only applies when the Outdoor Air Enthalpy Method is used.

3 Only applies when testing non-ducted units.

b. Calculate indoor-side total heating capacity as specified in sections 7.3.4.1 and 7.3.4.3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3). To calculate capacity, use the averages of the measurements (e.g. inlet and outlet dry bulb temperatures measured at the psychrometers) that are continuously recorded for the same 30-minute interval used as described above to evaluate compliance with test tolerances. Do not adjust the parameters used in calculating capacity for the permitted variations in test conditions. Assign the average space heating capacity and electrical power over the 30-minute data collection interval to the variables Q h k and E h k(T) respectively. The “T” and superscripted “k” are the same as described in section 3.3 of this appendix. Additionally, for the heating mode, use the superscript to denote results from the optional H1N test, if conducted.

c. For coil-only system heat pumps, increase Q h k(T) by

where V s is the average measured indoor air volume rate expressed in units of cubic feet per minute of standard air (scfm). During the 30-minute data collection interval of a high temperature test, pay attention to preventing a defrost cycle. Prior to this time, allow the heat pump to perform a defrost cycle if automatically initiated by its own controls. As in all cases, wait for the heat pump's defrost controls to automatically terminate the defrost cycle. Heat pumps that undergo a defrost should operate in the heating mode for at least 10 minutes after defrost termination prior to beginning the 30-minute data collection interval. For some heat pumps, frost may accumulate on the outdoor coil during a high temperature test. If the indoor coil leaving air temperature or the difference between the leaving and entering air temperatures decreases by more than 1.5 °F over the 30-minute data collection interval, then do not use the collected data to determine capacity. Instead, initiate a defrost cycle. Begin collecting data no sooner than 10 minutes after defrost termination. Collect 30 minutes of new data during which the Table 16 test tolerances are satisfied. In this case, use only the results from the second 30-minute data collection interval to evaluate Q h k(47) and E h k(47).

d. If conducting the cyclic heating mode test, which is described in section 3.8 of this appendix, record the average indoor-side air volume rate, V , specific heat of the air, Cp,a (expressed on dry air basis), specific volume of the air at the nozzles, vn′ (or vn), humidity ratio at the nozzles, Wn, and either pressure difference or velocity pressure for the flow nozzles. If either or both of the below criteria apply, determine the average, steady-state, electrical power consumption of the indoor blower motor (E fan,1):

(1) The section 3.8 cyclic test will be conducted and the heat pump has a variable-speed indoor blower that is expected to be disabled during the cyclic test; or

(2) The heat pump has a (variable-speed) constant-air volume-rate indoor blower and during the steady-state test the average external static pressure (ΔP1) exceeds the applicable section 3.1.4.4 minimum (or targeted) external static pressure (ΔPmin) by 0.03 inches of water or more.

Determine E fan,1 by making measurements during the 30-minute data collection interval, or immediately following the test and prior to changing the test conditions. When the above “2” criteria applies, conduct the following four steps after determining E fan,1 (which corresponds to ΔP1):

(i) While maintaining the same test conditions, adjust the exhaust fan of the airflow measuring apparatus until the external static pressure increases to approximately ΔP1 + (ΔP1 − ΔPmin).

(ii) After re-establishing steady readings for fan motor power and external static pressure, determine average values for the indoor blower power (E fan,2) and the external static pressure (ΔP2) by making measurements over a 5-minute interval.

(iii) Approximate the average power consumption of the indoor blower motor if the 30-minute test had been conducted at ΔPmin using linear extrapolation:

(iv) Decrease the total space heating capacity, Q hk(T), by the quantity (E fan,1 − E fan,min), when expressed on a Btu/h basis. Decrease the total electrical power, E hk(T) by the same fan power difference, now expressed in watts.

e. If the temperature sensors used to provide the primary measurement of the indoor-side dry bulb temperature difference during the steady-state dry-coil test and the subsequent cyclic dry-coil test are different, include measurements of the latter sensors among the regularly sampled data. Beginning at the start of the 30-minute data collection period, measure and compute the indoor-side air dry-bulb temperature difference using both sets of instrumentation, ΔT (Set SS) and ΔT (Set CYC), for each equally spaced data sample. If using a consistent data sampling rate that is less than 1 minute, calculate and record minutely averages for the two temperature differences. If using a consistent sampling rate of one minute or more, calculate and record the two temperature differences from each data sample. After having recorded the seventh (i=7) set of temperature differences, calculate the following ratio using the first seven sets of values:

Each time a subsequent set of temperature differences is recorded (if sampling more frequently than every 5 minutes), calculate FCD using the most recent seven sets of values. Continue these calculations until the 30-minute period is completed or until a value for FCD is calculated that falls outside the allowable range of 0.94-1.06. If the latter occurs, immediately suspend the test and identify the cause for the disparity in the two temperature difference measurements. Recalibration of one or both sets of instrumentation may be required. If all the values for FCD are within the allowable range, save the final value of the ratio from the 30-minute test as FCD*. If the temperature sensors used to provide the primary measurement of the indoor-side dry bulb temperature difference during the steady-state dry-coil test and the subsequent cyclic dry-coil test are the same, set FCD*= 1. 3.8 Test Procedures for the Cyclic Heating Mode Tests (the H0C1, H1C, H1C1 and H1C2 Tests)

a. Except as noted below, conduct the cyclic heating mode test as specified in section 3.5 of this appendix. As adapted to the heating mode, replace section 3.5 references to “the steady-state dry coil test” with “the heating mode steady-state test conducted at the same test conditions as the cyclic heating mode test.” Use the test tolerances in Table 17 rather than Table 10. Record the outdoor coil entering wet-bulb temperature according to the requirements given in section 3.5 of this appendix for the outdoor coil entering dry-bulb temperature. Drop the subscript “dry” used in variables cited in section 3.5 of this appendix when referring to quantities from the cyclic heating mode test. Determine the total space heating delivered during the cyclic heating test, qcyc, as specified in section 3.5 of this appendix except for making the following changes:

(1) When evaluating Equation 3.5-1, use the values of V , Cp,a,vn′, (or vn), and Wn that were recorded during the section 3.7 steady-state test conducted at the same test conditions.

(2) Calculate Γ using

where FCD* is the value recorded during the section 3.7 steady-state test conducted at the same test condition.

b. For ducted coil-only system heat pumps (excluding the special case where a variable-speed fan is temporarily removed), increase qcyc by the amount calculated using Equation 3.5-3. Additionally, increase ecyc by the amount calculated using Equation 3.5-2. In making these calculations, use the average indoor air volume rate (V s) determined from the section 3.7 steady-state heating mode test conducted at the same test conditions.

c. For non-ducted heat pumps, subtract the electrical energy used by the indoor blower during the 3 minutes after compressor cutoff from the non-ducted heat pump's integrated heating capacity, qcyc.

d. If a heat pump defrost cycle is manually or automatically initiated immediately prior to or during the OFF/ON cycling, operate the heat pump continuously until 10 minutes after defrost termination. After that, begin cycling the heat pump immediately or delay until the specified test conditions have been re-established. Pay attention to preventing defrosts after beginning the cycling process. For heat pumps that cycle off the indoor blower during a defrost cycle, make no effort here to restrict the air movement through the indoor coil while the fan is off. Resume the OFF/ON cycling while conducting a minimum of two complete compressor OFF/ON cycles before determining qcyc and ecyc.

3.8.1 Heating Mode Cyclic-Degradation Coefficient Calculation

Use the results from the required cyclic test and the required steady-state test that were conducted at the same test conditions to determine the heating mode cyclic-degradation coefficient CD h. Add “(k=2)” to the coefficient if it corresponds to a two-capacity unit cycling at high capacity. For the below calculation of the heating mode cyclic degradation coefficient, do not include the duct loss correction from section 7.3.3.3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3) in determining Q h k(Tcyc) (or qcyc). If the optional cyclic test is conducted but yields a tested CD h that exceeds the default CD h or if the optional test is not conducted, assign CD h the default value of 0.25. The default value for two-capacity units cycling at high capacity, however, is the low-capacity coefficient, i.e., CD h (k=2) = CD h. The tested CD h is calculated as follows:

where: the average coefficient of performance during the cyclic heating mode test, dimensionless. the average coefficient of performance during the steady-state heating mode test conducted at the same test conditions—i.e., same outdoor dry bulb temperature, Tcyc, and speed/capacity, k, if applicable—as specified for the cyclic heating mode test, dimensionless. the heating load factor, dimensionless. Tcyc = the nominal outdoor temperature at which the cyclic heating mode test is conducted, 62 or 47 °F. Δτcyc = the duration of the OFF/ON intervals; 0.5 hours when testing a heat pump having a single-speed or two-capacity compressor and 1.0 hour when testing a heat pump having a variable-speed compressor.

Round the calculated value for CD h to the nearest 0.01. If CD h is negative, then set it equal to zero.

Table 17—Test Operating and Test Condition Tolerances for Cyclic Heating Mode Tests

Test operating
tolerance 1
Test condition
tolerance 1
Indoor entering dry-bulb temperature, 2 °F2.00.5 Indoor entering wet-bulb temperature, 2 °F1.0 Outdoor entering dry-bulb temperature, 2 °F2.00.5 Outdoor entering wet-bulb temperature, 2 °F2.01.0 External resistance to air-flow, 2 inches of water0.05 Airflow nozzle pressure difference or velocity pressure, 2% of reading2.03 2.0 Electrical voltage, 4 % of rdg2.01.5

1 See section 1.2 of this appendix, Definitions.

2 Applies during the interval that air flows through the indoor (outdoor) coil except for the first 30 seconds after flow initiation. For units having a variable-speed indoor blower that ramps, the tolerances listed for the external resistance to airflow shall apply from 30 seconds after achieving full speed until ramp down begins.

3 The test condition shall be the average nozzle pressure difference or velocity pressure measured during the steady-state test conducted at the same test conditions.

4 Applies during the interval that at least one of the following—the compressor, the outdoor fan, or, if applicable, the indoor blower—are operating, except for the first 30 seconds after compressor start-up.

3.9 Test Procedures for Frost Accumulation Heating Mode Tests (the H2, H22, H2V, and H21 tests)

a. Confirm that the defrost controls of the heat pump are set as specified in section 2.2.1 of this appendix. Operate the test room reconditioning apparatus and the heat pump for at least 30 minutes at the specified section 3.6 test conditions before starting the “preliminary” test period. The preliminary test period must immediately precede the “official” test period, which is the heating and defrost interval over which data are collected for evaluating average space heating capacity and average electrical power consumption.

b. For heat pumps containing defrost controls which are likely to cause defrosts at intervals less than one hour, the preliminary test period starts at the termination of an automatic defrost cycle and ends at the termination of the next occurring automatic defrost cycle. For heat pumps containing defrost controls which are likely to cause defrosts at intervals exceeding one hour, the preliminary test period must consist of a heating interval lasting at least one hour followed by a defrost cycle that is either manually or automatically initiated. In all cases, the heat pump's own controls must govern when a defrost cycle terminates.

c. The official test period begins when the preliminary test period ends, at defrost termination. The official test period ends at the termination of the next occurring automatic defrost cycle. When testing a heat pump that uses a time-adaptive defrost control system (see section 1.2 of this appendix, Definitions), however, manually initiate the defrost cycle that ends the official test period at the instant indicated by instructions provided by the manufacturer. If the heat pump has not undergone a defrost after 6 hours, immediately conclude the test and use the results from the full 6-hour period to calculate the average space heating capacity and average electrical power consumption.

For heat pumps that turn the indoor blower off during the defrost cycle, take steps to cease forced airflow through the indoor coil and block the outlet duct whenever the heat pump's controls cycle off the indoor blower. If it is installed, use the outlet damper box described in section 2.5.4.1 of this appendix to affect the blocked outlet duct.

d. Defrost termination occurs when the controls of the heat pump actuate the first change in converting from defrost operation to normal heating operation. Defrost initiation occurs when the controls of the heat pump first alter its normal heating operation in order to eliminate possible accumulations of frost on the outdoor coil.

e. To constitute a valid frost accumulation test, satisfy the test tolerances specified in Table 18 during both the preliminary and official test periods. As noted in Table 18, test operating tolerances are specified for two sub-intervals:

(1) When heating, except for the first 10 minutes after the termination of a defrost cycle (sub-interval H, as described in Table 18) and

(2) When defrosting, plus these same first 10 minutes after defrost termination (sub-interval D, as described in Table 18). Evaluate compliance with Table 18 test condition tolerances and the majority of the test operating tolerances using the averages from measurements recorded only during sub-interval H. Continuously record the dry bulb temperature of the air entering the indoor coil, and the dry bulb temperature and water vapor content of the air entering the outdoor coil. Sample the remaining parameters listed in Table 18 at equal intervals that span 5 minutes or less.

f. For the official test period, collect and use the following data to calculate average space heating capacity and electrical power. During heating and defrosting intervals when the controls of the heat pump have the indoor blower on, continuously record the dry-bulb temperature of the air entering (as noted above) and leaving the indoor coil. If using a thermopile, continuously record the difference between the leaving and entering dry-bulb temperatures during the interval(s) that air flows through the indoor coil. For coil-only system heat pumps, determine the corresponding cumulative time (in hours) of indoor coil airflow, Δτa. Sample measurements used in calculating the air volume rate (refer to sections 7.7.2.1 and 7.7.2.2 of ANSI/ASHRAE 37-2009) at equal intervals that span 10 minutes or less. (Note: In the first printing of ANSI/ASHRAE 37-2009, the second IP equation for Qmi should read:) Record the electrical energy consumed, expressed in watt-hours, from defrost termination to defrost termination, eDEF k(35), as well as the corresponding elapsed time in hours, Δτspan.

Table 18—Test Operating and Test Condition Tolerances for Frost Accumulation Heating Mode Tests

Test operating tolerance 1Test condition
tolerance 1
Sub-interval H 2
Sub-interval H 2Sub-interval D 3Indoor entering dry-bulb temperature, °F2.04 4.00.5 Indoor entering wet-bulb temperature, °F1.0 Outdoor entering dry-bulb temperature, °F2.010.01.0 Outdoor entering wet-bulb temperature, °F1.50.5 External resistance to airflow, inches of water0.055 0.02 Electrical voltage, % of rdg2.01.5

1 See section 1.2 of this appendix, Definitions.

2 Applies when the heat pump is in the heating mode, except for the first 10 minutes after termination of a defrost cycle.

3 Applies during a defrost cycle and during the first 10 minutes after the termination of a defrost cycle when the heat pump is operating in the heating mode.

4 For heat pumps that turn off the indoor blower during the defrost cycle, the noted tolerance only applies during the 10 minute interval that follows defrost termination.

5 Only applies when testing non-ducted heat pumps.

3.9.1 Average Space Heating Capacity and Electrical Power Calculations

a. Evaluate average space heating capacity, Q h k(35), when expressed in units of Btu per hour, using:

Where, V = the average indoor air volume rate measured during sub-interval H, cfm. Cp,a = 0.24 + 0.444 · Wn, the constant pressure specific heat of the air-water vapor mixture that flows through the indoor coil and is expressed on a dry air basis, Btu/lbmda · °F. vn′ = specific volume of the air-water vapor mixture at the nozzle, ft 3/lbmmx. Wn = humidity ratio of the air-water vapor mixture at the nozzle, lbm of water vapor per lbm of dry air. Δτspan = τ2 − τ1, the elapsed time from defrost termination to defrost termination, hr. Tal(τ) = dry bulb temperature of the air entering the indoor coil at elapsed time τ, °F; only recorded when indoor coil airflow occurs; assigned the value of zero during periods (if any) where the indoor blower cycles off. Ta2(τ) = dry bulb temperature of the air leaving the indoor coil at elapsed time τ, °F; only recorded when indoor coil airflow occurs; assigned the value of zero during periods (if any) where the indoor blower cycles off. τ1 = the elapsed time when the defrost termination occurs that begins the official test period, hr. τ2 = the elapsed time when the next automatically occurring defrost termination occurs, thus ending the official test period, hr. vn = specific volume of the dry air portion of the mixture evaluated at the dry-bulb temperature, vapor content, and barometric pressure existing at the nozzle, ft 3 per lbm of dry air.

To account for the effect of duct losses between the outlet of the indoor unit and the section 2.5.4 dry-bulb temperature grid, adjust Q h k(35) in accordance with section 7.3.4.3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3).

b. Evaluate average electrical power, E h k(35), when expressed in units of watts, using:

For coil-only system heat pumps, increase Q h k(35) by,

and increase E h k(35) by, where V s is the average indoor air volume rate measured during the frost accumulation heating mode test and is expressed in units of cubic feet per minute of standard air (scfm).

c. For heat pumps having a constant-air-volume-rate indoor blower, the five additional steps listed below are required if the average of the external static pressures measured during sub-interval H exceeds the applicable section 3.1.4.4, 3.1.4.5, or 3.1.4.6 minimum (or targeted) external static pressure (ΔPmin) by 0.03 inches of water or more:

(1) Measure the average power consumption of the indoor blower motor (E fan,1) and record the corresponding external static pressure (ΔP1) during or immediately following the frost accumulation heating mode test. Make the measurement at a time when the heat pump is heating, except for the first 10 minutes after the termination of a defrost cycle.

(2) After the frost accumulation heating mode test is completed and while maintaining the same test conditions, adjust the exhaust fan of the airflow measuring apparatus until the external static pressure increases to approximately ΔP1 + (ΔP1 − ΔPmin).

(3) After re-establishing steady readings for the fan motor power and external static pressure, determine average values for the indoor blower power (E fan,2) and the external static pressure (ΔP2) by making measurements over a 5-minute interval.

(4) Approximate the average power consumption of the indoor blower motor had the frost accumulation heating mode test been conducted at ΔPmin using linear extrapolation:

(5) Decrease the total heating capacity, Q h k(35), by the quantity [(E fan,1−E fan,min) · (Δτ a/Δτ span], when expressed on a Btu/h basis. Decrease the total electrical power, Eh k(35), by the same quantity, now expressed in watts.

3.9.2 Demand Defrost Credit

a. Assign the demand defrost credit, Fdef, that is used in section 4.2 of this appendix to the value of 1 in all cases except for heat pumps having a demand-defrost control system (see section 1.2 of this appendix, Definitions). For such qualifying heat pumps, evaluate Fdef using,

where: Δτdef = the time between defrost terminations (in hours) or 1.5, whichever is greater. A value of 6 must be assigned to Δτdef if this limit is reached during a frost accumulation test and the heat pump has not completed a defrost cycle. Δτmax = maximum time between defrosts as allowed by the controls (in hours) or 12, whichever is less, as provided in the certification report.

b. For two-capacity heat pumps and for section 3.6.2 units, evaluate the above equation using the Δτdef that applies based on the frost accumulation test conducted at high capacity and/or at the heating full-load air volume rate. For variable-speed heat pumps, evaluate Δτdef based on the required frost accumulation test conducted at the intermediate compressor speed.

3.10 Test Procedures for Steady-State Low Temperature Heating Mode Tests (the H3, H32, and H31 Tests)

Except for the modifications noted in this section, conduct the low temperature heating mode test using the same approach as specified in section 3.7 of this appendix for the maximum and high temperature tests. After satisfying the section 3.7 requirements for the pretest interval but before beginning to collect data to determine Q h k(17) and E h k(17), conduct a defrost cycle. This defrost cycle may be manually or automatically initiated. The defrost sequence must be terminated by the action of the heat pump's defrost controls. Begin the 30-minute data collection interval described in section 3.7 of this appendix, from which Q h k(17) and E h k(17) are determined, no sooner than 10 minutes after defrost termination. Defrosts should be prevented over the 30-minute data collection interval.

3.11 Additional Requirements for the Secondary Test Methods 3.11.1 If Using the Outdoor Air Enthalpy Method as the Secondary Test Method

a. For all cooling mode and heating mode tests, first conduct a test without the outdoor air-side test apparatus described in section 2.10.1 of this appendix connected to the outdoor unit (“free outdoor air” test).

b. For the first section 3.2 steady-state cooling mode test and the first section 3.6 steady-state heating mode test, conduct a second test in which the outdoor-side apparatus is connected (“ducted outdoor air” test). No other cooling mode or heating mode tests require the ducted outdoor air test so long as the unit operates the outdoor fan during all cooling mode steady-state tests at the same speed and all heating mode steady-state tests at the same speed. If using more than one outdoor fan speed for the cooling mode steady-state tests, however, conduct the ducted outdoor air test for each cooling mode test where a different fan speed is first used. This same requirement applies for the heating mode tests.

3.11.1.1 Free Outdoor Air Test

a. For the free outdoor air test, connect the indoor air-side test apparatus to the indoor coil; do not connect the outdoor air-side test apparatus. Allow the test room reconditioning apparatus and the unit being tested to operate for at least one hour. After attaining equilibrium conditions, measure the following quantities at equal intervals that span 5 minutes or less:

(1) The section 2.10.1 evaporator and condenser temperatures or pressures;

(2) Parameters required according to the indoor air enthalpy method.

Continue these measurements until a 30-minute period (e.g., seven consecutive 5-minute samples) is obtained where the Table 9 or Table 16, whichever applies, test tolerances are satisfied.

b. For cases where a ducted outdoor air test is not required per section 3.11.1.b of this appendix, the free outdoor air test constitutes the “official” test for which validity is not based on comparison with a secondary test.

c. For cases where a ducted outdoor air test is required per section 3.11.1.b of this appendix, the following conditions must be met for the free outdoor air test to constitute a valid “official” test:

(1) Achieve the energy balance specified in section 3.1.1 of this appendix for the ducted outdoor air test (i.e., compare the capacities determined using the indoor air enthalpy method and the outdoor air enthalpy method).

(2) The capacities determined using the indoor air enthalpy method from the ducted outdoor air and free outdoor tests must agree within 2 percent.

3.11.1.2 Ducted Outdoor Air Test

a. The test conditions and tolerances for the ducted outdoor air test are the same as specified for the free outdoor air test described in Section 3.11.1.1 of this appendix.

b. After collecting 30 minutes of steady-state data during the free outdoor air test, connect the outdoor air-side test apparatus to the unit for the ducted outdoor air test. Adjust the exhaust fan of the outdoor airflow measuring apparatus until averages for the evaporator and condenser temperatures, or the saturated temperatures corresponding to the measured pressures, agree within ±0.5 °F of the averages achieved during the free outdoor air test. Collect 30 minutes of steady-state data after re-establishing equilibrium conditions.

c. During the ducted outdoor air test, at intervals of 5 minutes or less, measure the parameters required according to the indoor air enthalpy method and the outdoor air enthalpy method for the prescribed 30 minutes.

d. For cooling mode ducted outdoor air tests, calculate capacity based on outdoor air-enthalpy measurements as specified in sections 7.3.3.2 and 7.3.3.3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3). For heating mode ducted tests, calculate heating capacity based on outdoor air-enthalpy measurements as specified in sections 7.3.4.2 and 7.3.3.4.3 of the same ANSI/ASHRAE Standard. Adjust the outdoor-side capacity according to section 7.3.3.4 of ANSI/ASHRAE 37-2009 to account for line losses when testing split systems. As described in section 8.6.2 of ANSI/ASHRAE 37-2009, use the outdoor air volume rate as measured during the ducted outdoor air tests to calculate capacity for checking the agreement with the capacity calculated using the indoor air enthalpy method.

3.11.2 If Using the Compressor Calibration Method as the Secondary Test Method

a. Conduct separate calibration tests using a calorimeter to determine the refrigerant flow rate. Or for cases where the superheat of the refrigerant leaving the evaporator is less than 5 °F, use the calorimeter to measure total capacity rather than refrigerant flow rate. Conduct these calibration tests at the same test conditions as specified for the tests in this appendix. Operate the unit for at least one hour or until obtaining equilibrium conditions before collecting data that will be used in determining the average refrigerant flow rate or total capacity. Sample the data at equal intervals that span 5 minutes or less. Determine average flow rate or average capacity from data sampled over a 30-minute period where the Table 9 (cooling) or the Table 16 (heating) tolerances are satisfied. Otherwise, conduct the calibration tests according to sections 5, 6, 7, and 8 of ASHRAE 23.1-2010 (incorporated by reference, see § 430.3); sections 5, 6, 7, 8, 9, and 11 of ASHRAE 41.9-2011 (incorporated by reference, see § 430.3); and section 7.4 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3).

b. Calculate space cooling and space heating capacities using the compressor calibration method measurements as specified in section 7.4.5 and 7.4.6 respectively, of ANSI/ASHRAE 37-2009.

3.11.3 If Using the Refrigerant-Enthalpy Method as the Secondary Test Method

Conduct this secondary method according to section 7.5 of ANSI/ASHRAE 37-2009. Calculate space cooling and heating capacities using the refrigerant-enthalpy method measurements as specified in sections 7.5.4 and 7.5.5, respectively, of the same ASHRAE Standard.

3.12 Rounding of Space Conditioning Capacities for Reporting Purposes

a. When reporting rated capacities, round them off as specified in § 430.23 (for a single unit) and in 10 Cspan 429.16 (for a sample).

b. For the capacities used to perform the calculations in section 4 of this appendix, however, round only to the nearest integer.

3.13 Laboratory Testing to Determine Off Mode Average Power Ratings

Voltage tolerances: As a percentage of reading, test operating tolerance shall be 2.0 percent and test condition tolerance shall be 1.5 percent (see section 1.2 of this appendix for definitions of these tolerances).

Conduct one of the following tests: If the central air conditioner or heat pump lacks a compressor crankcase heater, perform the test in section 3.13.1 of this appendix; if the central air conditioner or heat pump has a compressor crankcase heater that lacks controls and is not self-regulating, perform the test in section 3.13.1 of this appendix; if the central air conditioner or heat pump has a crankcase heater with a fixed power input controlled with a thermostat that measures ambient temperature and whose sensing element temperature is not affected by the heater, perform the test in section 3.13.1 of this appendix; if the central air conditioner or heat pump has a compressor crankcase heater equipped with self-regulating control or with controls for which the sensing element temperature is affected by the heater, perform the test in section 3.13.2 of this appendix.

3.13.1 This Test Determines the Off Mode Average Power Rating for Central Air Conditioners and Heat Pumps That Lack a Compressor Crankcase Heater, or Have a Compressor Crankcase Heating System That Can Be Tested Without Control of Ambient Temperature During the Test. This Test Has No Ambient Condition Requirements

a. Test Sample Set-up and Power Measurement: For coil-only systems, provide a furnace or modular blower that is compatible with the system to serve as an interface with the thermostat (if used for the test) and to provide low-voltage control circuit power. Make all control circuit connections between the furnace (or modular blower) and the outdoor unit as specified by the manufacturer's installation instructions. Measure power supplied to both the furnace or modular blower and power supplied to the outdoor unit. Alternatively, provide a compatible transformer to supply low-voltage control circuit power, as described in section 2.2.d of this appendix. Measure transformer power, either supplied to the primary winding or supplied by the secondary winding of the transformer, and power supplied to the outdoor unit. For blower coil and single-package systems, make all control circuit connections between components as specified by the manufacturer's installation instructions, and provide power and measure power supplied to all system components.

b. Configure Controls: Configure the controls of the central air conditioner or heat pump so that it operates as if connected to a building thermostat that is set to the OFF position. Use a compatible building thermostat if necessary to achieve this configuration. For a thermostat-controlled crankcase heater with a fixed power input, bypass the crankcase heater thermostat if necessary to energize the heater.

c. Measure P2x: If the unit has a crankcase heater time delay, make sure that time delay function is disabled or wait until delay time has passed. Determine the average power from non-zero value data measured over a 5-minute interval of the non-operating central air conditioner or heat pump and designate the average power as P2x, the heating season total off mode power.

d. Measure Px for coil-only split systems and for blower coil split systems for which a furnace or a modular blower is the designated air mover: Disconnect all low-voltage wiring for the outdoor components and outdoor controls from the low-voltage transformer. Determine the average power from non-zero value data measured over a 5-minute interval of the power supplied to the (remaining) low-voltage components of the central air conditioner or heat pump, or low-voltage power, Px. This power measurement does not include line power supplied to the outdoor unit. It is the line power supplied to the air mover, or, if a compatible transformer is used instead of an air mover, it is the line power supplied to the transformer primary coil. If a compatible transformer is used instead of an air mover and power output of the low-voltage secondary circuit is measured, Px is zero.

e. Calculate P2: Set the number of compressors equal to the unit's number of single-stage compressors plus 1.75 times the unit's number of compressors that are not single-stage.

For single-package systems and blower coil split systems for which the designated air mover is not a furnace or modular blower, divide the heating season total off mode power (P2x) by the number of compressors to calculate P2, the heating season per-compressor off mode power. Round P2 to the nearest watt. The expression for calculating P2 is as follows:

For coil-only split systems and blower coil split systems for which a furnace or a modular blower is the designated air mover, subtract the low-voltage power (Px) from the heating season total off mode power (P2x) and divide by the number of compressors to calculate P2, the heating season per-compressor off mode power. Round P2 to the nearest watt. The expression for calculating P2 is as follows:

f. Shoulder-season per-compressor off mode power, P1: If the system does not have a crankcase heater, has a crankcase heater without controls that is not self-regulating, or has a value for the crankcase heater turn-on temperature (as certified in the DOE Compliance Certification Database) that is higher than 71 °F, P1 is equal to P2.

Otherwise, de-energize the crankcase heater (by removing the thermostat bypass or otherwise disconnecting only the power supply to the crankcase heater) and repeat the measurement as described in section 3.13.1.c of this appendix. Designate the measured average power as P1x, the shoulder season total off mode power.

Determine the number of compressors as described in section 3.13.1.e of this appendix.

For single-package systems and blower coil systems for which the designated air mover is not a furnace or modular blower, divide the shoulder season total off mode power (P1x) by the number of compressors to calculate P1, the shoulder season per-compressor off mode power. Round P1 to the nearest watt. The expression for calculating P1 is as follows:

For coil-only split systems and blower coil split systems for which a furnace or a modular blower is the designated air mover, subtract the low-voltage power (Px) from the shoulder season total off mode power (P1x) and divide by the number of compressors to calculate P1, the shoulder season per-compressor off mode power. Round P1 to the nearest watt. The expression for calculating P1 is as follows:

3.13.2 This Test Determines the Off Mode Average Power Rating for Central Air Conditioners and Heat Pumps for Which Ambient Temperature Can Affect the Measurement of Crankcase Heater Power

a. Test Sample Set-up and Power Measurement: Set up the test and measurement as described in section 3.13.1.a of this appendix.

b. Configure Controls: Position a temperature sensor to measure the outdoor dry-bulb temperature in the air between 2 and 6 inches from the crankcase heater control temperature sensor or, if no such temperature sensor exists, position it in the air between 2 and 6 inches from the crankcase heater. Utilize the temperature measurements from this sensor for this portion of the test procedure. Configure the controls of the central air conditioner or heat pump so that it operates as if connected to a building thermostat that is set to the OFF position. Use a compatible building thermostat if necessary to achieve this configuration.

Conduct the test after completion of the B, B1, or B2 test. Alternatively, start the test when the outdoor dry-bulb temperature is at 82 °F and the temperature of the compressor shell (or temperature of each compressor's shell if there is more than one compressor) is at least 81 °F. Then adjust the outdoor temperature at a rate of change of no more than 20 °F per hour and achieve an outdoor dry-bulb temperature of 72 °F. Maintain this temperature within ±2 °F while making the power measurement, as described in section 3.13.2.c of this appendix.

c. Measure P1x: If the unit has a crankcase heater time delay, make sure that time delay function is disabled or wait until delay time has passed. Determine the average power from non-zero value data measured over a 5-minute interval of the non-operating central air conditioner or heat pump and designate the average power as P1x, the shoulder season total off mode power. For units with crankcase heaters which operate during this part of the test and whose controls cycle or vary crankcase heater power over time, the test period shall consist of three complete crankcase heater cycles or 18 hours, whichever comes first. Designate the average power over the test period as P1x, the shoulder season total off mode power.

d. Reduce outdoor temperature: Approach the target outdoor dry-bulb temperature by adjusting the outdoor temperature at a rate of change of no more than 20 °F per hour. This target temperature is five degrees Fahrenheit less than the temperature specified by the manufacturer in the DOE Compliance Certification Database at which the crankcase heater turns on. Maintain the target temperature within ±2 °F while making the power measurement, as described in section 3.13.2.e of this appendix.

e. Measure P2x: If the unit has a crankcase heater time delay, make sure that time delay function is disabled or wait until delay time has passed. Determine the average non-zero power of the non-operating central air conditioner or heat pump over a 5-minute interval and designate it as P2x, the heating season total off mode power. For units with crankcase heaters whose controls cycle or vary crankcase heater power over time, the test period shall consist of three complete crankcase heater cycles or 18 hours, whichever comes first. Designate the average power over the test period as P2x, the heating season total off mode power.

f. Measure Px for coil-only split systems and for blower coil split systems for which a furnace or modular blower is the designated air mover: Disconnect all low-voltage wiring for the outdoor components and outdoor controls from the low-voltage transformer. Determine the average power from non-zero value data measured over a 5-minute interval of the power supplied to the (remaining) low-voltage components of the central air conditioner or heat pump, or low-voltage power, Px.. This power measurement does not include line power supplied to the outdoor unit. It is the line power supplied to the air mover, or, if a compatible transformer is used instead of an air mover, it is the line power supplied to the transformer primary coil. If a compatible transformer is used instead of an air mover and power output of the low-voltage secondary circuit is measured, Px is zero.

g. Calculate P1:

Set the number of compressors equal to the unit's number of single-stage compressors plus 1.75 times the unit's number of compressors that are not single-stage.

For single-package systems and blower coil split systems for which the air mover is not a furnace or modular blower, divide the shoulder season total off mode power (P1x) by the number of compressors to calculate P1, the shoulder season per-compressor off mode power. Round to the nearest watt. The expression for calculating P1 is as follows:

For coil-only split systems and blower coil split systems for which a furnace or a modular blower is the designated air mover, subtract the low-voltage power (Px) from the shoulder season total off mode power (P1x) and divide by the number of compressors to calculate P1, the shoulder season per-compressor off mode power. Round to the nearest watt. The expression for calculating P1 is as follows:

h. Calculate P2:

Determine the number of compressors as described in section 3.13.2.g of this appendix.

For single-package systems and blower coil split systems for which the air mover is not a furnace, divide the heating season total off mode power (P2x) by the number of compressors to calculate P2, the heating season per-compressor off mode power. Round to the nearest watt. The expression for calculating P2 is as follows:

For coil-only split systems and blower coil split systems for which a furnace or a modular blower is the designated air mover, subtract the low-voltage power (Px) from the heating season total off mode power (P2x) and divide by the number of compressors to calculate P2, the heating season per-compressor off mode power. Round to the nearest watt. The expression for calculating P2 is as follows:

4. Calculations of Seasonal Performance Descriptors 4.1 Seasonal Energy Efficiency Ratio (SEER) Calculations. SEER must be calculated as follows: For equipment covered under sections 4.1.2, 4.1.3, and 4.1.4 of this appendix, evaluate the seasonal energy efficiency ratio, where: Tj = the outdoor bin temperature, °F. Outdoor temperatures are grouped or “binned.” Use bins of 5 °F with the 8 cooling season bin temperatures being 67, 72, 77, 82, 87, 92, 97, and 102 °F. j = the bin number. For cooling season calculations, j ranges from 1 to 8.

Additionally, for sections 4.1.2, 4.1.3, and 4.1.4 of this appendix, use a building cooling load, BL(Tj). When referenced, evaluate BL(Tj) for cooling using,

where:

Q ck=2(95) = the space cooling capacity determined from the A2 test and calculated as specified in section 3.3 of this appendix, Btu/h.

1.1 = sizing factor, dimensionless.

The temperatures 95 °F and 65 °F in the building load equation represent the selected outdoor design temperature and the zero-load base temperature, respectively.

4.1.1 SEER Calculations for a Blower Coil System Having a Single-Speed Compressor and Either a Fixed-Speed Indoor Blower or a Constant-Air-Volume-Rate Indoor Blower, or a Coil-Only System Air Conditioner or Heat Pump

a. Evaluate the seasonal energy efficiency ratio, expressed in units of Btu/watt-hour, using:

SEER = PLF(0.5) * EERB where: PLF(0.5) = 1 − 0.5 · CD c, the part-load performance factor evaluated at a cooling load factor of 0.5, dimensionless.

b. Refer to section 3.3 of this appendix regarding the definition and calculation of Q c(82) and E c(82). Evaluate the cooling mode cyclic degradation factor CD c as specified in section 3.5.3 of this appendix.

4.1.2 SEER Calculations for an Air Conditioner or Heat Pump Having a Single-Speed Compressor and a Variable-Speed Variable-Air-Volume-Rate Indoor Blower 4.1.2.1 Units Covered by Section 3.2.2.1 of This Appendix Where Indoor Blower Capacity Modulation Correlates With the Outdoor Dry Bulb Temperature

The manufacturer must provide information on how the indoor air volume rate or the indoor blower speed varies over the outdoor temperature range of 67 °F to 102 °F. Calculate SEER using Equation 4.1-1. Evaluate the quantity qc(Tj)/N in Equation 4.1-1 using,

where: Q c(Tj) = the space cooling capacity of the test unit when operating at outdoor temperature, Tj, Btu/h. nj/N = fractional bin hours for the cooling season; the ratio of the number of hours during the cooling season when the outdoor temperature fell within the range represented by bin temperature Tj to the total number of hours in the cooling season, dimensionless.

a. For the space cooling season, assign nj/N as specified in Table 19. Use Equation 4.1-2 to calculate the building load, BL(Tj). Evaluate Q c(Tj) using,

where: the space cooling capacity of the test unit at outdoor temperature Tj if operated at the cooling minimum air volume rate, Btu/h. the space cooling capacity of the test unit at outdoor temperature Tj if operated at the Cooling full-load air volume rate, Btu/h.

b. For units where indoor blower speed is the primary control variable, spanck=1 denotes the fan speed used during the required A1 and B1 tests (see section 3.2.2.1 of this appendix), spanck=2 denotes the fan speed used during the required A2 and B2 tests, and spanc(Tj) denotes the fan speed used by the unit when the outdoor temperature equals Tj. For units where indoor air volume rate is the primary control variable, the three spanc's are similarly defined only now being expressed in terms of air volume rates rather than fan speeds. Refer to sections 3.2.2.1, 3.1.4 to 3.1.4.2, and 3.3 of this appendix regarding the definitions and calculations of Q ck=1(82), Q ck=1(95), Q ck=2(82), and Q ck=2(95).

where: PLFj = 1 − CD c · [1 − X(Tj)], the part load factor, dimensionless. E c(Tj) = the electrical power consumption of the test unit when operating at outdoor temperature Tj, W.

c. The quantities X(Tj) and nj/N are the same quantities as used in Equation 4.1.2-1. Evaluate the cooling mode cyclic degradation factor CD c as specified in section 3.5.3 of this appendix.

d. Evaluate E c(Tj) using,

e. The parameters spanck=1, and spanck=2, and spanc(Tj) are the same quantities that are used when evaluating Equation 4.1.2-2. Refer to sections 3.2.2.1, 3.1.4 to 3.1.4.2, and 3.3 of this appendix regarding the definitions and calculations of E ck=1(82), E ck=1(95), E ck=2(82), and E ck=2(95).

4.1.2.2 Units Covered by Section 3.2.2.2 of This Appendix Where Indoor Blower Capacity Modulation Is Used To Adjust the Sensible to Total Cooling Capacity Ratio.

Calculate SEER as specified in section 4.1.1 of this appendix.

4.1.3 SEER Calculations for an Air Conditioner or Heat Pump Having a Two-Capacity Compressor

Calculate SEER using Equation 4.1-1. Evaluate the space cooling capacity, Q ck=1 (Tj), and electrical power consumption, E ck=1 (Tj), of the test unit when operating at low compressor capacity and outdoor temperature Tj using,

where Q ck=1 (82) and E ck=1 (82) are determined from the B1 test, Q ck=1 (67) and E ck=1 (67) are determined from the F1 test, and all four quantities are calculated as specified in section 3.3 of this appendix. Evaluate the space cooling capacity, Q ck=2 (Tj), and electrical power consumption, E ck=2 (Tj), of the test unit when operating at high compressor capacity and outdoor temperature Tj using, where Q ck=2(95) and E ck=2(95) are determined from the A2 test, Q ck=2(82), and E ck=2(82), are determined from the B2test, and all are calculated as specified in section 3.3 of this appendix.

The calculation of Equation 4.1-1 quantities qc(Tj)/N and ec(Tj)/N differs depending on whether the test unit would operate at low capacity (section 4.1.3.1 of this appendix), cycle between low and high capacity (section 4.1.3.2 of this appendix), or operate at high capacity (sections 4.1.3.3 and 4.1.3.4 of this appendix) in responding to the building load. For units that lock out low capacity operation at higher outdoor temperatures, the outdoor temperature at which the unit locks out must be that specified by the manufacturer in the certification report so that the appropriate equations are used. Use Equation 4.1-2 to calculate the building load, BL(Tj), for each temperature bin.

4.1.3.1 Steady-State Space Cooling Capacity at Low Compressor Capacity Is Greater Than or Equal to the Building Cooling Load at Temperature Tj, Q ck=1(Tj) ≥BL(Tj) where: Xk=1(Tj) = BL(Tj)/Q ck=1(Tj), the cooling mode low capacity load factor for temperature bin j, dimensionless. PLFj = 1 − CD c · [1 − Xk=1(Tj)], the part load factor, dimensionless.

Obtain the fractional bin hours for the cooling season, nj/N, from Table 19. Use Equations 4.1.3-1 and 4.1.3-2, respectively, to evaluate Q ck=1(Tj) and E ck=1(Tj). Evaluate the cooling mode cyclic degradation factor CD c as specified in section 3.5.3 of this appendix.

Table 19—Distribution of Fractional Hours Within Cooling Season Temperature Bins

Bin number,
j
Bin
temperature
range
°F
Representative temperature for bin
°F
Fraction of total
temperature
bin hours,
nj/N
165-69670.214 270-74720.231 375-79770.216 480-84820.161 585-89870.104 690-94920.052 795-99970.018 8100-1041020.004
4.1.3.2 Unit Alternates Between High (k=2) and Low (k=1) Compressor Capacity to Satisfy the Building Cooling Load at Temperature Tj, Q c k=1(Tj) <BL(Tj) <Q c k=2(Tj) Xk=2(Tj) = 1 − Xk=1(Tj), the cooling mode, high capacity load factor for temperature bin j, dimensionless.

Obtain the fractional bin hours for the cooling season, nj/N, from Table 19. Use Equations 4.1.3-1 and 4.1.3-2, respectively, to evaluate Q ck=1(Tj) and E ck=1(Tj). Use Equations 4.1.3-3 and 4.1.3-4, respectively, to evaluate Q ck=2(Tj) and E ck=2(Tj).

4.1.3.3 Unit Only Operates at High (k=2) Compressor Capacity at Temperature Tj and Its Capacity Is Greater Than the Building Cooling Load, BL(Tj) Q ck=2(Tj). This section applies to units that lock out low compressor capacity operation at higher outdoor temperatures. where: Xk=2(Tj) = BL(Tj)/Q ck=2(Tj), the cooling mode high capacity load factor for temperature bin j, dimensionless. PLFj = 1 − CDc(k = 2) * [1 − Xk=2(Tj) the part load factor, dimensionless. 4.1.3.4 Unit Must Operate Continuously at High (k=2) Compressor Capacity at Temperature Tj, BL(Tj) ≥Q ck=2(Tj)

Obtain the fractional bin hours for the cooling season, nj/N, from Table 19. Use Equations 4.1.3-3 and 4.1.3-4, respectively, to evaluate Q ck=2(Tj) and E ck=2(Tj).

4.1.4 SEER Calculations for an Air Conditioner or Heat Pump Having a Variable-Speed Compressor

Calculate SEER using Equation 4.1-1. Evaluate the space cooling capacity, Q ck=1(Tj), and electrical power consumption, E ck=1(Tj), of the test unit when operating at minimum compressor speed and outdoor temperature Tj. Use,

where Q ck=1(82) and E ck=1(82) are determined from the B1 test, Q ck=1(67) and E ck=1(67) are determined from the F1 test, and all four quantities are calculated as specified in section 3.3 of this appendix.

Evaluate the space cooling capacity, Q ck=2(Tj), and electrical power consumption, E ck=2(Tj), of the test unit when operating at full compressor speed and outdoor temperature Tj. Use Equations 4.1.3-3 and 4.1.3-4, respectively, where Q ck=2(95) and E ck=2(95) are determined from the A2 test, Q ck=2(82) and E ck=2(82) are determined from the B2 test, and all four quantities are calculated as specified in section 3.3 of this appendix. Calculate the space cooling capacity, Q ck=v(Tj), and electrical power consumption, E ck=v(Tj), of the test unit when operating at outdoor temperature Tj and the intermediate compressor speed used during the section 3.2.4 (and Table 8) EV test of this appendix using,

where Q ck=v(87) and E ck=v(87) are determined from the EV test and calculated as specified in section 3.3 of this appendix. Approximate the slopes of the k=v intermediate speed cooling capacity and electrical power input curves, MQ and ME, as follows:

Use Equations 4.1.4-1 and 4.1.4-2, respectively, to calculate Q ck=1(87) and E ck=1(87).

4.1.4.1 Steady-State Space Cooling Capacity When Operating at Minimum Compressor Speed Is Greater Than or Equal to the Building Cooling Load at Temperature Tj, Q ck=1(Tj) ≥BL(Tj) where: Xk=1(Tj) = BL(Tj)/Q ck=1(Tj), the cooling mode minimum speed load factor for temperature bin j, dimensionless. PLFj = 1 − CD c · [1 − Xk=1(Tj)], the part load factor, dimensionless. nj/N = fractional bin hours for the cooling season; the ratio of the number of hours during the cooling season when the outdoor temperature fell within the range represented by bin temperature Tj to the total number of hours in the cooling season, dimensionless.

Obtain the fractional bin hours for the cooling season, nj/N, from Table 19. Use Equations 4.1.3-1 and 4.1.3-2, respectively, to evaluate Q c k=l (Tj) and E c k=l (Tj). Evaluate the cooling mode cyclic degradation factor CD c as specified in section 3.5.3 of this appendix.

4.1.4.2 Unit Operates at an Intermediate Compressor Speed (k=i) In Order To Match the Building Cooling Load at Temperature Tj, Q c k=1(Tj) < BL(Tj) < Q c k=2(Tj) Where: Q c k=i(Tj) = BL(Tj), the space cooling capacity delivered by the unit in matching the building load at temperature Tj, Btu/h. The matching occurs with the unit operating at compressor speed k=i. EER k=i(Tj) = the steady-state energy efficiency ratio of the test unit when operating at a compressor speed of k=i and temperature Tj, Btu/h per W.

Obtain the fractional bin hours for the cooling season, nj/N, from Table 19 to this appendix. For each temperature bin where the unit operates at an intermediate compressor speed, determine the energy efficiency ratio EER k=i(Tj) using, EERk=i(Tj) = A + B Tj + C * T2j.

For each unit, determine the coefficients A, B, and C by conducting the following calculations once:

Where: T1 = the outdoor temperature at which the unit, when operating at minimum compressor speed, provides a space cooling capacity that is equal to the building load (Q c k=l(Tl) = BL(T1)), °F. Determine T1 by equating Equations 4.1.3-1 and 4.1-2 to this appendix and solving for outdoor temperature. Tv = the outdoor temperature at which the unit, when operating at the intermediate compressor speed used during the section 3.2.4 Ev test of this appendix, provides a space cooling capacity that is equal to the building load (Q c k=v(Tv) = BL(Tv)), °F. Determine Tv by equating Equations 4.1.4-3 and 4.1-2 to this appendix and solving for outdoor temperature. T2 = the outdoor temperature at which the unit, when operating at full compressor speed, provides a space cooling capacity that is equal to the building load (Q c k=2(T2) = BL(T2)), °F. Determine T2 by equating Equations 4.1.3-3 and 4.1-2 to this appendix and solving for outdoor temperature. 4.1.4.3 Unit Must Operate Continuously at Full (k=2) Compressor Speed at Temperature Tj, BL(Tj) ≥Q ck=2(Tj). Evaluate the Equation 4.1-1 Quantities as specified in section 4.1.3.4 of this appendix with the understanding that Q ck=2(Tj) and E ck=2(Tj) correspond to full compressor speed operation and are derived from the results of the tests specified in section 3.2.4 of this appendix. 4.1.5 SEER Calculations for an Air Conditioner or Heat Pump Having a Single Indoor Unit With Multiple Indoor Blowers

Calculate SEER using Eq. 4.1-1, where qc(Tj)/N and ec(Tj)/N are evaluated as specified in the applicable subsection.

4.1.5.1 For Multiple Indoor Blower Systems That Are Connected to a Single, Single-Speed Outdoor Unit

a. Calculate the space cooling capacity, Q ck=1(Tj), and electrical power consumption, E ck=1(Tj), of the test unit when operating at the cooling minimum air volume rate and outdoor temperature Tj using the equations given in section 4.1.2.1 of this appendix. Calculate the space cooling capacity, Q ck=2(Tj), and electrical power consumption, E ck=2(Tj), of the test unit when operating at the cooling full-load air volume rate and outdoor temperature Tj using the equations given in section 4.1.2.1 of this appendix. In evaluating the section 4.1.2.1 equations, determine the quantities Q ck=1(82) and E ck=1(82) from the B1 test, Q ck=1(95) and E ck=1(95) from the Al test, Q ck=2(82) and E ck=2(82) from the B2 test, andQ ck=2(95) and E ck=2(95) from the A2 test. Evaluate all eight quantities as specified in section 3.3 of this appendix. Refer to section 3.2.2.1 and Table 6 of this appendix for additional information on the four referenced laboratory tests.

b. Determine the cooling mode cyclic degradation coefficient, CDc, as per sections 3.2.2.1 and 3.5 to 3.5.3 of this appendix. Assign this same value to CDc(K=2).

c. Except for using the above values of Q ck=1(Tj), E ck=1(Tj), E ck=2(Tj), Q ck=2(Tj), CDc, and CDc (K=2), calculate the quantities qc(Tj)/N and ec(Tj)/N as specified in section 4.1.3.1 of this appendix for cases where Q ck=1(Tj) ≥BL(Tj). For all other outdoor bin temperatures, Tj, calculate qc(Tj)/N and ec(Tj)/N as specified in section 4.1.3.3 of this appendix if Q ck=2(Tj) >BL (Tj) or as specified in section 4.1.3.4 of this appendix if Q ck=2(Tj) ≤BL(Tj).

4.1.5.2 Unit Operates at an Intermediate Compressor Speed (k=i) In Order To Match the Building Cooling Load at Temperature Tj,Q ck=1(Tj) <BL(Tj) <Q ck=2(Tj) where, Q ck=i(Tj) = BL(Tj), the space cooling capacity delivered by the unit in matching the building load at temperature Tj, Btu/h. The matching occurs with the unit operating at compressor speed k = i. EERk=i(Tj), the steady-state energy efficiency ratio of the test unit when operating at a compressor speed of k = i and temperature Tj, Btu/h per W.

Obtain the fractional bin hours for the cooling season, nj/N, from Table 19. For each temperature bin where the unit operates at an intermediate compressor speed, determine the energy efficiency ratio EERk=i(Tj) using the following equations,

For each temperature bin where Q ck=1(Tj) <BL(Tj) <Q ck=v(Tj),

For each temperature bin where Q ck=v(Tj) ≤BL(Tj) <Q ck=2(Tj),

Where: EERk=1(Tj) is the steady-state energy efficiency ratio of the test unit when operating at minimum compressor speed and temperature Tj, Btu/h per W, calculated using capacity Q ck=1(Tj) calculated using Equation 4.1.4-1 and electrical power consumption E ck=1(Tj) calculated using Equation 4.1.4-2; EERk=v(Tj) is the steady-state energy efficiency ratio of the test unit when operating at intermediate compressor speed and temperature Tj, Btu/h per W, calculated using capacity Q ck=v(Tj) calculated using Equation 4.1.4-3 and electrical power consumption E ck=v(Tj) calculated using Equation 4.1.4-4; EERk=2(Tj) is the steady-state energy efficiency ratio of the test unit when operating at full compressor speed and temperature Tj, Btu/h per W, calculated using capacity Q ck=2(Tj) and electrical power consumption E ck=2(Tj), both calculated as described in section 4.1.4; and BL(Tj) is the building cooling load at temperature Tj, Btu/h. 4.2 Heating Seasonal Performance Factor (HSPF) Calculations

Unless an approved alternative efficiency determination method is used, as set forth in 10 Cspan 429.70(e), HSPF must be calculated as follows: Six generalized climatic regions are depicted in Figure 1 and otherwise defined in Table 20. For each of these regions and for each applicable standardized design heating requirement, evaluate the heating seasonal performance factor using,

where: e2(Tj)/N = The ratio of the electrical energy consumed by the heat pump during periods of the space heating season when the outdoor temperature fell within the range represented by bin temperature Tj to the total number of hours in the heating season (N), W. For heat pumps having a heat comfort controller, this ratio may also include electrical energy used by resistive elements to maintain a minimum air delivery temperature (see 4.2.5). RH(Tj)/N = The ratio of the electrical energy used for resistive space heating during periods when the outdoor temperature fell within the range represented by bin temperature Tj to the total number of hours in the heating season (N), W. Except as noted in section 4.2.5 of this appendix, resistive space heating is modeled as being used to meet that portion of the building load that the heat pump does not meet because of insufficient capacity or because the heat pump automatically turns off at the lowest outdoor temperatures. For heat pumps having a heat comfort controller, all or part of the electrical energy used by resistive heaters at a particular bin temperature may be reflected in eh(Tj)/N (see section 4.2.5 of this appendix). Tj = the outdoor bin temperature, °F. Outdoor temperatures are “binned” such that calculations are only performed based one temperature within the bin. Bins of 5 °F are used. nj/N= Fractional bin hours for the heating season; the ratio of the number of hours during the heating season when the outdoor temperature fell within the range represented by bin temperature Tj to the total number of hours in the heating season, dimensionless. Obtain nj/N values from Table 20. j = the bin number, dimensionless. J = for each generalized climatic region, the total number of temperature bins, dimensionless. Referring to Table 20, J is the highest bin number (j) having a nonzero entry for the fractional bin hours for the generalized climatic region of interest. Fdef = the demand defrost credit described in section 3.9.2 of this appendix, dimensionless. BL(Tj) = the building space conditioning load corresponding to an outdoor temperature of Tj; the heating season building load also depends on the generalized climatic region's outdoor design temperature and the design heating requirement, Btu/h.

Table 20—Generalized Climatic Region Information

Region No. I II III IV V VI Heating Load Hours, HLH7501,2501,7502,2502,750*2,750 Outdoor Design Temperature, TOD3727175−1030 j Tj ( °F)Fractional Bin Hours, nj/N 1 62.291.215.153.132.106.113 2 57.239.189.142.111.092.206 3 52.194.163.138.103.086.215 4 47.129.143.137.093.076.204 5 42.081.112.135.100.078.141 6 37.041.088.118.109.087.076 7 32.019.056.092.126.102.034 8 27.005.024.047.087.094.008 9 22.001.008.021.055.074.003 10 170.002.009.036.0550 11 1200.005.026.0470 12 700.002.013.0380 13 200.001.006.0290 14 −3000.002.0180 15 −8000.001.0100 16 −130000.0050 17 −180000.0020 18 −230000.0010

* Pacific Coast Region.

Evaluate the building heating load using

Where: TOD = the outdoor design temperature, °F. An outdoor design temperature is specified for each generalized climatic region in Table 20. C = 0.77, a correction factor which tends to improve the agreement between calculated and measured building loads, dimensionless. DHR = the design heating requirement (see section 1.2 of this appendix, Definitions), Btu/h.

Calculate the minimum and maximum design heating requirements for each generalized climatic region as follows:

where Q h k(47) is expressed in units of Btu/h and otherwise defined as follows:

a. For a single-speed heat pump tested as per section 3.6.1 of this appendix, Q h k(47) = Q h(47), the space heating capacity determined from the H1 test.

b. For a section 3.6.2 single-speed heat pump or a two-capacity heat pump not covered by item d, Q h k(47) = Q hk=2(47), the space heating capacity determined from the H1 or H12 test.

c. For a variable-speed heat pump, Q h k(47) = Q hk=N(47), the space heating capacity determined from the H1N test.

d. For two-capacity, northern heat pumps (see section 1.2 of this appendix, Definitions), Q kh(47) = Q k=1h(47), the space heating capacity determined from the H11 test.

For all heat pumps, HSPF accounts for the heating delivered and the energy consumed by auxiliary resistive elements when operating below the balance point. This condition occurs when the building load exceeds the space heating capacity of the heat pump condenser. For HSPF calculations for all heat pumps, see either section 4.2.1, 4.2.2, 4.2.3, or 4.2.4 of this appendix, whichever applies.

For heat pumps with heat comfort controllers (see section 1.2 of this appendix, Definitions), HSPF also accounts for resistive heating contributed when operating above the heat-pump-plus-comfort-controller balance point as a result of maintaining a minimum supply temperature. For heat pumps having a heat comfort controller, see section 4.2.5 of this appendix for the additional steps required for calculating the HSPF.

Table 21—Standardized Design Heating Requirements

[Btu/h]

5,000 10,000 15,000 20,000 25,000 30,000 35,000 40,000 50,000 60,000 70,000 80,000 90,000 100,000 110,000 130,000
4.2.1 Additional Steps for Calculating the HSPF of a Blower Coil System Heat Pump Having a Single-Speed Compressor and Either a Fixed-Speed Indoor Blower or a Constant-Air-Volume-Rate Indoor Blower Installed, or a Coil-Only System Heat Pump Where: whichever is less; the heating mode load factor for temperature bin j, dimensionless. Q h(Tj) = the space heating capacity of the heat pump when operating at outdoor temperature Tj, Btu/h. E h(Tj) = the electrical power consumption of the heat pump when operating at outdoor temperature Tj, W. δ(Tj) = the heat pump low temperature cut-out factor, dimensionless. PLFj = 1 − C D h · [1 −X(Tj)] the part load factor, dimensionless.

Use Equation 4.2-2 to determine BL(Tj). Obtain fractional bin hours for the heating season, nj/N, from Table 20. Evaluate the heating mode cyclic degradation factor C D h as specified in section 3.8.1 of this appendix.

Determine the low temperature cut-out factor using

Where: Toff = the outdoor temperature when the compressor is automatically shut off, °F. (If no such temperature exists, Tj is always greater than Toff and Ton). Ton = the outdoor temperature when the compressor is automatically turned back on, if applicable, following an automatic shut-off, °F.

Calculate Q h(Tj) and E h(Tj) using,

where Q h(47) and E h(47) are determined from the H1 test and calculated as specified in section 3.7 of this appendix; Q h(35) and E h(35) are determined from the H2 test and calculated as specified in section 3.9.1 of this appendix; and Q h(17) and E h(17) are determined from the H3 test and calculated as specified in section 3.10 of this appendix. 4.2.2 Additional Steps for Calculating the HSPF of a Heat Pump Having a Single-Speed Compressor and a Variable-Speed, Variable-Air-Volume-Rate Indoor Blower

The manufacturer must provide information about how the indoor air volume rate or the indoor blower speed varies over the outdoor temperature range of 65 °F to −23 °F. Calculate the quantities

in Equation 4.2-1 as specified in section 4.2.1 of this appendix with the exception of replacing references to the H1C test and section 3.6.1 of this appendix with the H1C1 test and section 3.6.2 of this appendix. In addition, evaluate the space heating capacity and electrical power consumption of the heat pump Q h(Tj) and E h(Tj) using where the space heating capacity and electrical power consumption at both low capacity (k=1) and high capacity (k=2) at outdoor temperature Tj are determined using

For units where indoor blower speed is the primary control variable, spanhk=1 denotes the fan speed used during the required H11 and H31 tests (see Table 12), spanhk=2 denotes the fan speed used during the required H12, H22, and H32 tests, and spanh(Tj) denotes the fan speed used by the unit when the outdoor temperature equals Tj. For units where indoor air volume rate is the primary control variable, the three spanh's are similarly defined only now being expressed in terms of air volume rates rather than fan speeds. Determine Q hk=1(47) and E hk=1(47) from the H11 test, and Q hk=2(47) and E hk=2(47) from the H12 test. Calculate all four quantities as specified in section 3.7 of this appendix. Determine Q hk=1(35) and E hk=1(35) as specified in section 3.6.2 of this appendix; determine Q hk=2(35) and E hk=2(35) and from the H22 test and the calculation specified in section 3.9 of this appendix. Determine Q hk=1(17) and E hk=1(17) from the H31 test, and Q hk=2(17) and E hk=2(17) from the H32 test. Calculate all four quantities as specified in section 3.10 of this appendix.

4.2.3 Additional Steps for Calculating the HSPF of a Heat Pump Having a Two-Capacity Compressor

The calculation of the Equation 4.2-1 to this appendix quantities differ depending upon whether the heat pump would operate at low capacity (section 4.2.3.1 of this appendix), cycle between low and high capacity (section 4.2.3.2 of this appendix), or operate at high capacity (sections 4.2.3.3 and 4.2.3.4 of this appendix) in responding to the building load. For heat pumps that lock out low capacity operation at low outdoor temperatures, the outdoor temperature at which the unit locks out must be that specified by the manufacturer in the certification report so that the appropriate equations can be selected.

a. Evaluate the space heating capacity and electrical power consumption of the heat pump when operating at low compressor capacity and outdoor temperature Tj using

b. Evaluate the space heating capacity and electrical power consumption (Q hk=2(Tj) and E hk=2 (Tj)) of the heat pump when operating at high compressor capacity and outdoor temperature Tj by solving Equations 4.2.2-3 and 4.2.2-4, respectively, for k=2. Determine Q hk=1(62) and E hk=1(62) from the H01 test, Q hk=1(47) and E hk=1(47) from the H11 test, and Q hk=2(47) and E hk=2(47) from the H12 test. Calculate all six quantities as specified in section 3.7 of this appendix. Determine Q hk=2(35) and E hk=2(35) from the H22 test and, if required as described in section 3.6.3 of this appendix, determine Q hk=1(35) and E hk=1(35) from the H21 test. Calculate the required 35 °F quantities as specified in section 3.9 of this appendix. Determine Q hk=2(17) and E hk=2(17) from the H32 test and, if required as described in section 3.6.3 of this appendix, determine Q hk=1(17) and E hk=1(17) from the H31 test. Calculate the required 17 °F quantities as specified in section 3.10 of this appendix.

4.2.3.1 Steady-State Space Heating Capacity When Operating at Low Compressor Capacity is Greater Than or Equal to the Building Heating Load at Temperature Tj, Q hk=1(Tj) ≥BL(Tj) Where: Xk=1(Tj) = BL(Tj)/Q hk=1(Tj), the heating mode low capacity load factor for temperature bin j, dimensionless. PLFj = 1 − CD h · [ 1 − Xk=1(Tj) ], the part load factor, dimensionless. δ′(Tj) = the low temperature cutoff factor, dimensionless.

Evaluate the heating mode cyclic degradation factor CD h as specified in section 3.8.1 of this appendix.

Determine the low temperature cut-out factor using

where Toff and Ton are defined in section 4.2.1 of this appendix. Use the calculations given in section 4.2.3.3 of this appendix, and not the above, if:

a. The heat pump locks out low capacity operation at low outdoor temperatures and

b. Tj is below this lockout threshold temperature.

4.2.3.2 Heat Pump Alternates Between High (k=2) and Low (k=1) Compressor Capacity To Satisfy the Building Heating Load at a Temperature Tj, Q hk=1(Tj) <BL(Tj) <Q hk=2(Tj) Xk=2(Tj) = 1 − Xk=1(Tj) the heating mode, high capacity load factor for temperaturebin j, dimensionless.

Determine the low temperature cut-out factor, δ′(Tj), using Equation 4.2.3-3.

4.2.3.3 Heat Pump Only Operates at High (k=2) Compressor Capacity at Temperature Tj and its Capacity Is Greater Than the Building Heating Load, BL(Tj) <Q hk=2(Tj)

This section applies to units that lock out low compressor capacity operation at low outdoor temperatures.

Where: Xk=2(Tj) = BL(Tj)/Q hk=2(Tj); and PLFj = 1−ChD (k = 2) * [1−Xk=2(Tj)].

If the H1C2 test described in section 3.6.3 and Table 13 of this appendix is not conducted, set CD h (k=2) equal to the default value specified in section 3.8.1 of this appendix.

Determine the low temperature cut-out factor, δ(Tj), using Equation 4.2.3-3.

4.2.3.4 Heat Pump Must Operate Continuously at High (k=2) Compressor Capacity at Temperature Tj, BL(Tj) ≥ Q h k=2(Tj) Where: 4.2.4 Additional Steps for Calculating the HSPF of a Heat Pump Having a Variable-Speed Compressor

Calculate HSPF using Equation 4.2-1. Evaluate the space heating capacity, Q hk=1(Tj), and electrical power consumption, E hk=1(Tj), of the heat pump when operating at minimum compressor speed and outdoor temperature Tj using

where Q hk=1(62) and E hk=1(62) are determined from the H01 test, Q hk=1(47) and E hk=1(47) are determined from the H11 test, and all four quantities are calculated as specified in section 3.7 of this appendix.

Evaluate the space heating capacity, Q hk=2(Tj), and electrical power consumption, E hk=2(Tj), of the heat pump when operating at full compressor speed and outdoor temperature Tj by solving Equations 4.2.2-3 and 4.2.2-4, respectively, for k=2. For Equation 4.2.2-3, use Q hcalck=2(47) to represent Q hk=2(47), and for Equation 4.2.2-4, use E hcalck=2(47) to represent E hcalck=2(47)—evaluate Q hcalck=2(47) and E hcalck=2(47) as specified in section 3.6.4b of this appendix.

where Q hk=v(35) and E hk=v(35) are determined from the H2V test and calculated as specified in section 3.9 of this appendix. Approximate the slopes of the k=v intermediate speed heating capacity and electrical power input curves, MQ and ME, as follows: 4.2.4.1 Steady-State Space Heating Capacity When Operating at Minimum Compressor Speed Is Greater Than or Equal to the Building Heating Load at Temperature Tj, Q hk=1(Tj ≥BL(Tj)

Evaluate the Equation 4.2-1 quantities

as specified in section 4.2.3.1 of this appendix. Except now use Equations 4.2.4-1 and 4.2.4-2 to evaluate Q hk=1(Tj) and E hk=1(Tj), respectively, and replace section 4.2.3.1 references to “low capacity” and section 3.6.3 of this appendix with “minimum speed” and section 3.6.4 of this appendix. Also, the last sentence of section 4.2.3.1 of this appendix does not apply. 4.2.4.2 Heat Pump Operates at an Intermediate Compressor Speed (k=i) in Order To Match the Building Heating Load at a Temperature Tj, Q hk=1(Tj) <BL(Tj) <Q hk=2(Tj) and δ(Tj) is evaluated using Equation 4.2.3-3 while, Q hk=i(Tj) = BL(Tj), the space heating capacity delivered by the unit in matching the building load at temperature (Tj), Btu/h. The matching occurs with the heat pump operating at compressor speed k=i. COPk=i(Tj) = the steady-state coefficient of performance of the heat pump when operating at compressor speed k=i and temperature Tj, dimensionless.

For each temperature bin where the heat pump operates at an intermediate compressor speed, determine COPk=i(Tj) using the following equations,

For each temperature bin where Q hk=1(Tj) <BL(Tj) <Q hk=v(Tj),

For each temperature bin where Q hk=v(Tj) ≤BL(Tj) <Q hk=2(Tj),

Where: COPhk=1(Tj) is the steady-state coefficient of performance of the heat pump when operating at minimum compressor speed and temperature Tj, dimensionless, calculated using capacity Q hk=1(Tj) calculated using Equation 4.2.4-1 and electrical power consumption E hk=1(Tj) calculated using Equation 4.2.4-2; COPhk=v(Tj) is the steady-state coefficient of performance of the heat pump when operating at intermediate compressor speed and temperature Tj, dimensionless, calculated using capacity Q hk=v(Tj) calculated using Equation 4.2.4-3 and electrical power consumption E hk=v(Tj) calculated using Equation 4.2.4-4; COPhk=2(Tj) is the steady-state coefficient of performance of the heat pump when operating at full compressor speed and temperature Tj, dimensionless, calculated using capacity Q hk=2(Tj) and electrical power consumption E hk=2(Tj), both calculated as described in section 4.2.4; and BL(Tj) is the building heating load at temperature Tj, Btu/h. 4.2.4.3 Heat Pump Must Operate Continuously at Full (k=2) Compressor Speed at Temperature Tj, BL(Tj) ≥Q hk=2(Tj)

Evaluate the Equation 4.2-1 Quantities

as specified in section 4.2.3.4 of this appendix with the understanding that Q hk=2(Tj) and E hk=2(Tj) correspond to full compressor speed operation and are derived from the results of the specified section 3.6.4 tests of this appendix. 4.2.5 Heat Pumps Having a Heat Comfort Controller

Heat pumps having heat comfort controllers, when set to maintain a typical minimum air delivery temperature, will cause the heat pump condenser to operate less because of a greater contribution from the resistive elements. With a conventional heat pump, resistive heating is only initiated if the heat pump condenser cannot meet the building load (i.e., is delayed until a second stage call from the indoor thermostat). With a heat comfort controller, resistive heating can occur even though the heat pump condenser has adequate capacity to meet the building load (i.e., both on during a first stage call from the indoor thermostat). As a result, the outdoor temperature where the heat pump compressor no longer cycles (i.e., starts to run continuously), will be lower than if the heat pump did not have the heat comfort controller.

4.2.5.1 Blower Coil System Heat Pump Having a Heat Comfort Controller: Additional Steps for Calculating the HSPF of a Heat Pump Having a Single-Speed Compressor and Either a Fixed-Speed Indoor Blower or a Constant-Air-Volume-Rate Indoor Blower Installed, or a Coil-Only System Heat Pump

Calculate the space heating capacity and electrical power of the heat pump without the heat comfort controller being active as specified in section 4.2.1 of this appendix (Equations 4.2.1-4 and 4.2.1-5) for each outdoor bin temperature, Tj, that is listed in Table 20. Denote these capacities and electrical powers by using the subscript “hp” instead of “h.” Calculate the mass flow rate (expressed in pounds-mass of dry air per hour) and the specific heat of the indoor air (expressed in Btu/lbmda · °F) from the results of the H1 test using:

where V s, V mx, v′n (or vn), and Wn are defined following Equation 3-1. For each outdoor bin temperature listed in Table 20, calculate the nominal temperature of the air leaving the heat pump condenser coil using,

Evaluate eh(Tj/N), RH(Tj)/N, X(Tj), PLFj, and δ(Tj) as specified in section 4.2.1 of this appendix. For each bin calculation, use the space heating capacity and electrical power from Case 1 or Case 2, whichever applies.

Case 1. For outdoor bin temperatures where To(Tj) is equal to or greater than TCC (the maximum supply temperature determined according to section 3.1.10 of this appendix), determine Q h(Tj) and E h(Tj) as specified in section 4.2.1 of this appendix (i.e., Q h(Tj) = Q hp(Tj) and E h(Tj) = E hp(Tj)). Note: Even though To(Tj) ≥Tcc, resistive heating may be required; evaluate Equation 4.2.1-2 for all bins.

Case 2. For outdoor bin temperatures where To(Tj) < TCC, determine Q h(Tj) and E h(Tj) using,

Note:

Even though To(Tj) Tcc, additional resistive heating may be required; evaluate Equation 4.2.1-2 for all bins.

4.2.5.2 Heat Pump Having a Heat Comfort Controller: Additional Steps for Calculating the HSPF of a Heat Pump Having a Single-Speed Compressor and a Variable-Speed, Variable-Air-Volume-Rate Indoor Blower

Calculate the space heating capacity and electrical power of the heat pump without the heat comfort controller being active as specified in section 4.2.2 of this appendix (Equations 4.2.2-1 and 4.2.2-2) for each outdoor bin temperature, Tj, that is listed in Table 20. Denote these capacities and electrical powers by using the subscript “hp” instead of “h.” Calculate the mass flow rate (expressed in pounds-mass of dry air per hour) and the specific heat of the indoor air (expressed in Btu/lbmda · °F) from the results of the H12 test using:

where V S, V mx, v′n (or vn), and Wn are defined following Equation 3-1. For each outdoor bin temperature listed in Table 20, calculate the nominal temperature of the air leaving the heat pump condenser coil using,

Evaluate eh(Tj)/N, RH(Tj)/N, X(Tj), PLFj, and δ(Tj) as specified in section 4.2.1 of this appendix with the exception of replacing references to the H1C test and section 3.6.1 of this appendix with the H1C1 test and section 3.6.2 of this appendix. For each bin calculation, use the space heating capacity and electrical power from Case 1 or Case 2, whichever applies.

Case 1. For outdoor bin temperatures where To(Tj) is equal to or greater than TCC (the maximum supply temperature determined according to section 3.1.10 of this appendix), determine Q h(Tj) and E h(Tj) as specified in section 4.2.2 of this appendix (i.e. Q h(Tj) = Q hp(Tj) and E h(Tj) = E hp(Tj)). Note: Even though To(Tj) ≥TCC, resistive heating may be required; evaluate Equation 4.2.1-2 for all bins.

Case 2. For outdoor bin temperatures where To(Tj) < TCC, determine Q h(Tj) and E h(Tj) using,

Note:

Even though To(Tj) Tcc, additional resistive heating may be required; evaluate Equation 4.2.1-2 for all bins.

4.2.5.3 Heat Pumps Having a Heat Comfort Controller: Additional Steps for Calculating the HSPF of a Heat Pump Having a Two-Capacity Compressor

Calculate the space heating capacity and electrical power of the heat pump without the heat comfort controller being active as specified in section 4.2.3 of this appendix for both high and low capacity and at each outdoor bin temperature, Tj, that is listed in Table 20. Denote these capacities and electrical powers by using the subscript “hp” instead of “h.” For the low capacity case, calculate the mass flow rate (expressed in pounds-mass of dry air per hour) and the specific heat of the indoor air (expressed in Btu/lbmda · °F) from the results of the H11 test using:

where V s, V mx, v′n (or vn), and Wn are defined following Equation 3-1. For each outdoor bin temperature listed in Table 20, calculate the nominal temperature of the air leaving the heat pump condenser coil when operating at low capacity using,

Repeat the above calculations to determine the mass flow rate (m dak=2) and the specific heat of the indoor air (Cp,dak=2) when operating at high capacity by using the results of the H12 test. For each outdoor bin temperature listed in Table 20, calculate the nominal temperature of the air leaving the heat pump condenser coil when operating at high capacity using,

Evaluate eh(Tj)/N, RH(Tj)/N, Xk=1(Tj), and/or Xk=2(Tj), PLFj, and δ′(Tj) or δ″(Tj) as specified in section 4.2.3.1. 4.2.3.2, 4.2.3.3, or 4.2.3.4 of this appendix, whichever applies, for each temperature bin. To evaluate these quantities, use the low-capacity space heating capacity and the low-capacity electrical power from Case 1 or Case 2, whichever applies; use the high-capacity space heating capacity and the high-capacity electrical power from Case 3 or Case 4, whichever applies.

Case 1. For outdoor bin temperatures where Tok=1(Tj) is equal to or greater than TCC (the maximum supply temperature determined according to section 3.1.10 of this appendix), determine Q hk=1(Tj) and E hk=1(Tj) as specified in section 4.2.3 of this appendix (i.e., Q hk=1(Tj) = Q hpk=1(Tj) and E hk=1(Tj) = E hpk=1(Tj).

Note:

Even though Tok=1(Tj) ≥TCC, resistive heating may be required; evaluate RH(Tj)/N for all bins.

Case 2. For outdoor bin temperatures where To k=1(Tj) < TCC, determine Q h k=1(Tj) and E h k=1(Tj) using,

Note:

Even though Tok=1(Tj) ≥Tcc, additional resistive heating may be required; evaluate RH(Tj)/N for all bins.

Case 3. For outdoor bin temperatures where Tok=2(Tj) is equal to or greater than TCC, determine Q hk=2(Tj) and E hk=2(Tj) as specified in section 4.2.3 of this appendix (i.e., Q hk=2(Tj) = Q hpk=2(Tj) and E hk=2(Tj) = E hpk=2(Tj)).

Note:

Even though Tok=2(Tj) <TCC, resistive heating may be required; evaluate RH(Tj)/N for all bins.

Case 4. For outdoor bin temperatures where Tok=2(Tj) <TCC, determine Q hk=2(Tj) and E hk=2(Tj) using,

Note:

Even though Tok=2(Tj) <Tcc, additional resistive heating may be required; evaluate RH(Tj)/N for all bins.

4.2.5.4 Heat Pumps Having a Heat Comfort Controller: Additional Steps for Calculating the HSPF of a Heat Pump Having a Variable-Speed Compressor. [Reserved]

4.2.6 Additional Steps for Calculating the HSPF of a Heat Pump Having a Triple-Capacity Compressor

The only triple-capacity heat pumps covered are triple-capacity, northern heat pumps. For such heat pumps, the calculation of the Eq. 4.2-1 quantities

differ depending on whether the heat pump would cycle on and off at low capacity (section 4.2.6.1 of this appendix), cycle on and off at high capacity (section 4.2.6.2 of this appendix), cycle on and off at booster capacity (section 4.2.6.3 of this appendix), cycle between low and high capacity (section 4.2.6.4 of this appendix), cycle between high and booster capacity (section 4.2.6.5 of this appendix), operate continuously at low capacity (4.2.6.6 of this appendix), operate continuously at high capacity (section 4.2.6.7 of this appendix), operate continuously at booster capacity (section 4.2.6.8 of this appendix), or heat solely using resistive heating (also section 4.2.6.8 of this appendix) in responding to the building load. As applicable, the manufacturer must supply information regarding the outdoor temperature range at which each stage of compressor capacity is active. As an informative example, data may be submitted in this manner: At the low (k=1) compressor capacity, the outdoor temperature range of operation is 40 °F ≤ T ≤ 65 °F; At the high (k=2) compressor capacity, the outdoor temperature range of operation is 20 °F ≤ T ≤ 50 °F; At the booster (k=3) compressor capacity, the outdoor temperature range of operation is −20 °F ≤ T ≤ 30 °F.

a. Evaluate the space heating capacity and electrical power consumption of the heat pump when operating at low compressor capacity and outdoor temperature Tj using the equations given in section 4.2.3 of this appendix for Q hk=1(Tj) and E hk=1 (Tj)) In evaluating the section 4.2.3 equations, Determine Q hk=1(62) and E hk=1(62) from the H01 test, Q hk=1(47) and E hk=1(47) from the H11 test, and Q hk=2(47) and E hk=2(47) from the H12 test. Calculate all four quantities as specified in section 3.7 of this appendix. If, in accordance with section 3.6.6 of this appendix, the H31 test is conducted, calculate Q hk=1(17) and E hk=1(17) as specified in section 3.10 of this appendix and determine Q hk=1(35) and E hk=1(35) as specified in section 3.6.6 of this appendix.

b. Evaluate the space heating capacity and electrical power consumption (Q hk=2(Tj) and E hk=2 (Tj)) of the heat pump when operating at high compressor capacity and outdoor temperature Tj by solving Equations 4.2.2-3 and 4.2.2-4, respectively, for k=2. Determine Q hk=1(62) and E hk=1(62) from the H01 test, Q hk=1(47) and E hk=1(47) from the H11 test, and Q hk=2(47) and E hk=2(47) from the H12 test, evaluated as specified in section 3.7 of this appendix. Determine the equation input for Q hk=2(35) and E hk=2(35) from the H22, evaluated as specified in section 3.9.1 of this appendix. Also, determine Q hk=2(17) and E hk=2(17) from the H32 test, evaluated as specified in section 3.10 of this appendix.

c. Evaluate the space heating capacity and electrical power consumption of the heat pump when operating at booster compressor capacity and outdoor temperature Tj using

Determine Q hk=3(17) and E hk=3(17) from the H33 test and determine Q hk=3(5) and E hk=3(5) from the H43 test. Calculate all four quantities as specified in section 3.10 of this appendix. Determine the equation input for Q hk=3(35) and E hk=3(35) as specified in section 3.6.6 of this appendix. 4.2.6.1 Steady-State Space Heating Capacity when Operating at Low Compressor Capacity is Greater than or Equal to the Building Heating Load at Temperature Tj, Q hk=1(Tj) ≥BL(Tj)., and the heat pump permits low compressor capacity at Tj.

Evaluate the quantities

using Eqs. 4.2.3-1 and 4.2.3-2, respectively. Determine the equation inputs Xk=1(Tj), PLFj, and δ′(Tj) as specified in section 4.2.3.1 of this appendix. In calculating the part load factor, PLFj, use the low-capacity cyclic-degradation coefficient CD h, [or equivalently, CD h(k=1)] determined in accordance with section 3.6.6 of this appendix.

4.2.6.2 Heat Pump Only Operates at High (k=2) Compressor Capacity at Temperature Tj and Its Capacity Is Greater Than or Equal to the Building Heating Load, BL(Tj) ≤Q hk=2(Tj)

Evaluate the quantities

as specified in section 4.2.3.3 of this appendix. Determine the equation inputs Xk=2(Tj), PLFj, and δ′(Tj) as specified in section 4.2.3.3 of this appendix. In calculating the part load factor, PLFj, use the high-capacity cyclic-degradation coefficient, CD h(k=2) determined in accordance with section 3.6.6 of this appendix.

4.2.6.3 Heat Pump Only Operates at Booster (k=3) Compressor Capacity at Temperature Tj, and its Capacity Is Greater Than or Equal to the Building Heating Load, BL(Tj) ≤ Q hk=3(Tj). where: Xk=3(Tj) = BL(Tj)/Q hk=3 (Tj) and PLFj = 1−CDh (k = 3) * [1−Xk=3 (Tj) Determine the low temperature cut-out factor, δ′(Tj), using Eq. 4.2.3-3. Use the booster-capacity cyclic-degradation coefficient, CD h(k=3) determined in accordance with section 3.6.6 of this appendix.

4.2.6.4 Heat Pump Alternates Between High (k=2) and Low (k=1) Compressor Capacity to Satisfy the Building Heating Load at a Temperature Tj, Q hk=1(Tj) <BL(Tj) <Q hk=2(Tj)

Evaluate the quantities

as specified in section 4.2.3.2 of this appendix. Determine the equation inputs Xk=1(Tj), Xk=2(Tj), and δ′(Tj) as specified in section 4.2.3.2 of this appendix.

4.2.6.5 Heat Pump Alternates Between High (k=2) and Booster (k=3) Compressor Capacity To Satisfy the Building Heating Load at a Temperature Tj, Q hk=2(Tj) <BL(Tj) <Q hk=3(Tj) and Xk=3(Tj) = Xk=2(Tj) = the heating mode, booster capacity load factor for temperature bin j, dimensionless. Determine the low temperature cut-out factor, δ′(Tj), using Eq. 4.2.3-3.

4.2.6.6 Heat Pump Only Operates at Low (k=1) Capacity at Temperature Tj and Its Capacity Is Less Than the Building Heating Load, BL(Tj) > Q hk=1(Tj) where the low temperature cut-out factor, δ′(Tj), is calculated using Eq. 4.2.3-3. 4.2.6.7 Heat Pump Only Operates at High (k=2) Capacity at Temperature Tj and Its Capacity Is Less Than the Building Heating Load, BL(Tj) > Q hk=2(Tj)

Evaluate the quantities

as specified in section 4.2.3.4 of this appendix. Calculate δ″(Tj) using the equation given in section 4.2.3.4 of this appendix.

4.2.6.8 Heat Pump Only Operates at Booster (k=3) Capacity at Temperature Tj and Its Capacity Is Less Than the Building Heating Load, BL(Tj) > Q hk=3(Tj) or the System Converts to Using Only Resistive Heating

where δ″(Tj) is calculated as specified in section 4.2.3.4 of this appendix if the heat pump is operating at its booster compressor capacity. If the heat pump system converts to using only resistive heating at outdoor temperature Tj, set δ′(Tj) equal to zero.

4.2.7 Additional Steps for Calculating the HSPF of a Heat Pump Having a Single Indoor Unit With Multiple Indoor Blowers

The calculation of the Eq. 4.2-1 quantities eh(Tj)/N and RH(Tj)/N are evaluated as specified in the applicable subsection.

4.2.7.1 For Multiple Indoor Blower Heat Pumps That Are Connected to a Singular, Single-Speed Outdoor Unit

a. Calculate the space heating capacity, Q hk=1(Tj), and electrical power consumption, E hk=1(Tj), of the heat pump when operating at the heating minimum air volume rate and outdoor temperature Tj using Eqs. 4.2.2-3 and 4.2.2-4, respectively. Use these same equations to calculate the space heating capacity, Q hk=2(Tj) and electrical power consumption, E hk=2(Tj), of the test unit when operating at the heating full-load air volume rate and outdoor temperature Tj. In evaluating Eqs. 4.2.2-3 and 4.2.2- 4, determine the quantities Q hk=1(47) and E hk=1(47) from the H11 test; determine Q hk=2 (47) and E hk=2(47) from the H12 test. Evaluate all four quantities according to section 3.7 of this appendix. Determine the quantities Q hk=1(35) and E hk=1(35) as specified in section 3.6.2 of this appendix. Determine Q hk=2(35) and E hk=2(35) from the H22 frost accumulation test as calculated according to section 3.9.1 of this appendix. Determine the quantities Q hk=1(17) and E hk=1(17) from the H31 test, and Q hk=2(17) and E hk=2(17) from the H32 test. Evaluate all four quantities according to section 3.10 of this appendix. Refer to section 3.6.2 and Table 12 of this appendix for additional information on the referenced laboratory tests.

b. Determine the heating mode cyclic degradation coefficient, CDh, as per sections 3.6.2 and 3.8 to 3.8.1 of this appendix. Assign this same value to CDh(k = 2).

c. Except for using the above values of Q hk=1(Tj), E hk=1(Tj), Q hk=2(Tj), E hk=2(Tj), CDh, and CDh(k = 2), calculate the quantities eh(Tj)/N as specified in section 4.2.3.1 of this appendix for cases where Q hk=1(Tj) ≥ BL(Tj). For all other outdoor bin temperatures, Tj, calculate eh(Tj)/N and RHh(Tj)/N as specified in section 4.2.3.3 of this appendix if Q hk=2(Tj) > BL(Tj) or as specified in section 4.2.3.4 of this appendix if Q hk=2(Tj) ≤ BL(Tj).

4.2.7.2 For Multiple Indoor Blower Heat Pumps Connected to Either a Single Outdoor Unit With a Two-capacity Compressor or to Two Separate Single-Speed Outdoor Units of Identical Model, calculate the quantities eh(Tj)/N and RH(Tj)/N as specified in section 4.2.3 of this appendix. 4.3 Calculations of Off-mode Power Consumption

For central air conditioners and heat pumps with a cooling capacity of:

Less than 36,000 Btu/h, determine the off mode represented value, PW,OFF, with the following equation:

greater than or equal to 36,000 Btu/h, calculate the capacity scaling factor according to: where Q C(95) is the total cooling capacity at the A or A2 test condition, and determine the off mode represented value, PW,OFF, with the following equation: 4.4 Rounding of SEER and HSPF for Reporting Purposes

After calculating SEER according to section 4.1 of this appendix and HSPF according to section 4.2 of this appendix round the values off as specified per § 430.23(m) of title 10 of the Code of Federal Regulations.

Table 22—Representative Cooling and Heating Load Hours for Each Generalized Climatic Region

Climatic region Cooling load hours
CLHR
Heating load hours
HLHR
I2,400750 II1,8001,250 III1,2001,750 IV8002,250 Rating Values1,0002,080 V4002,750 VI2002,750
4.5 Calculations of the SHR, Which Should Be Computed for Different Equipment Configurations and Test Conditions Specified in Table 23

Table 23—Applicable Test Conditions For Calculation of the Sensible Heat Ratio

Equipment configuration Reference
table Number of
appendix M
SHR computation with results
from
Computed values Units Having a Single-Speed Compressor and a Fixed-Speed Indoor blower, a Constant Air Volume Rate Indoor blower, or No Indoor blower4B TestSHR(B). Units Having a Single-Speed Compressor That Meet the section 3.2.2.1 Indoor Unit Requirements5B2 and B1 TestsSHR(B1), SHR(B2). Units Having a Two-Capacity Compressor6B2 and B1 TestsSHR(B1), SHR(B2). Units Having a Variable-Speed Compressor7B2 and B1 TestsSHR(B1), SHR(B2).

The SHR is defined and calculated as follows:

Where both the total and sensible cooling capacities are determined from the same cooling mode test and calculated from data collected over the same 30-minute data collection interval. 4.6 Calculations of the Energy Efficiency Ratio (EER).

Calculate the energy efficiency ratio using.

where Q ck(T) and E ck(T) are the space cooling capacity and electrical power consumption determined from the 30-minute data collection interval of the same steady-state wet coil cooling mode test and calculated as specified in section 3.3 of this appendix. Add the letter identification for each steady-state test as a subscript (e.g., EERA2) to differentiate among the resulting EER values. [82 span 1476, Jan. 5, 2017, as amended at 86 span 68393, Dec. 2, 2021; 87 span 64586, Oct. 25, 2022]

Appendix M1 - Appendix M1 to Subpart B of Part 430—Uniform Test Method for Measuring the Energy Consumption of Central Air Conditioners and Heat Pumps

Note:

On or after January 1, 2023, and prior to April 24, 2023, any representations, including compliance certifications, made with respect to the energy use, power, or efficiency of central air conditioners and central air conditioning heat pumps must be based on the results of testing pursuant to either this appendix or the procedures in appendix M1 as it appeared at 10 Cspan part 430, subpart B, in the 10 Cspan parts 200 to 499 edition revised as of January 1, 2022. Any representations made with respect to the energy use or efficiency of such central air conditioners and central air conditioning heat pumps must be in accordance with whichever version is selected.

On or after April 24, 2023, any representations, including compliance certifications, made with respect to the energy use, power, or efficiency of central air conditioners and central air conditioning heat pumps must be based on the results of testing pursuant to this appendix.

Prior to January 1, 2023, any representations, including compliance certifications, made with respect to the energy use, power, or efficiency of central air conditioners and central air conditioning heat pumps must be based on the results of testing pursuant to appendix M of this subpart.

On or after January 1, 2023, any representations, including compliance certifications, made with respect to the energy use, power, or efficiency of central air conditioners and central air conditioning heat pumps must be based on the results of testing pursuant to this appendix.

1 Scope and Definitions 1.1 Scope

This test procedure provides a method of determining SEER2, EER2, HSPF2 and PW,OFF for central air conditioners and central air conditioning heat pumps including the following categories:

(h) Split-system air conditioners, including single-split, multi-head mini-split, multi-split (including VRF), and multi-circuit systems

(i) Split-system heat pumps, including single-split, multi-head mini-split, multi-split (including VRF), and multi-circuit systems

(j) Single-package air conditioners

(k) Single-package heat pumps

(l) Small-duct, high-velocity systems (including VRF)

(m) Space-constrained products—air conditioners

(n) Space-constrained products—heat pumps

For the purposes of this appendix, the Department of Energy incorporates by reference specific sections of several industry standards, as listed in § 430.3. In cases where there is a conflict, the language of the test procedure in this appendix takes precedence over the incorporated standards.

All section references refer to sections within this appendix unless otherwise stated.

1.2 Definitions

Airflow-control settings are programmed or wired control system configurations that control a fan to achieve discrete, differing ranges of airflow—often designated for performing a specific function (e.g., cooling, heating, or constant circulation)—without manual adjustment other than interaction with a user-operable control (i.e., a thermostat) that meets the manufacturer specifications for installed-use. For the purposes of this appendix, manufacturer specifications for installed-use are those found in the product literature shipped with the unit.

Air sampling device is an assembly consisting of a manifold with several branch tubes with multiple sampling holes that draws an air sample from a critical location from the unit under test (e.g. indoor air inlet, indoor air outlet, outdoor air inlet, etc.).

Airflow prevention device denotes a device that prevents airflow via natural convection by mechanical means, such as an air damper box, or by means of changes in duct height, such as an upturned duct.

Aspirating psychrometer is a piece of equipment with a monitored airflow section that draws uniform airflow through the measurement section and has probes for measurement of air temperature and humidity.

Blower coil indoor unit means an indoor unit either with an indoor blower housed with the coil or with a separate designated air mover such as a furnace or a modular blower (as defined in appendix AA to this subpart).

Blower coil system refers to a split system that includes one or more blower coil indoor units.

Cased coil means a coil-only indoor unit with external cabinetry.

Ceiling-mount blower coil system means a split system for which a) the outdoor unit has a certified cooling capacity less than or equal to 36,000 Btu/h; b) the indoor unit(s) is/are shipped with manufacturer-supplied installation instructions that specify to secure the indoor unit only to the ceiling, within a furred-down space, or above a dropped ceiling of the conditioned space, with return air directly to the bottom of the unit without ductwork, or through the furred-down space, or optional insulated return air plenum that is shipped with the indoor unit; c) the installed height of the indoor unit is no more than 12 inches (not including condensate drain lines) and the installed depth (in the direction of airflow) of the indoor unit is no more than 30 inches; and d) supply air is discharged horizontally.

Coefficient of Performance (COP) means the ratio of the average rate of space heating delivered to the average rate of electrical energy consumed by the heat pump. Determine these rate quantities from a single test or, if derived via interpolation, determine at a single set of operating conditions. COP is a dimensionless quantity. When determined for a ducted coil-only system, COP must be calculated using the default values for heat output and power input of a fan motor specified in sections 3.7 and 3.9.1 of this appendix.

Coil-only indoor unit means an indoor unit that is distributed in commerce without an indoor blower or separate designated air mover. A coil-only indoor unit installed in the field relies on a separately installed furnace or a modular blower for indoor air movement.

Coil-only system means a system that includes only (one or more) coil-only indoor units.

Condensing unit removes the heat absorbed by the refrigerant to transfer it to the outside environment and consists of an outdoor coil, compressor(s), and air moving device.

Constant-air-volume-rate indoor blower means a fan that varies its operating speed to provide a fixed air-volume-rate from a ducted system.

Continuously recorded, when referring to a dry bulb measurement, dry bulb temperature used for test room control, wet bulb temperature, dew point temperature, or relative humidity measurements, means that the specified value must be sampled at regular intervals that are equal to or less than 15 seconds.

Cooling load factor (CLF) means the ratio having as its numerator the total cooling delivered during a cyclic operating interval consisting of one ON period and one OFF period, and as its denominator the total cooling that would be delivered, given the same ambient conditions, had the unit operated continuously at its steady-state, space-cooling capacity for the same total time (ON + OFF) interval.

Crankcase heater means any electrically powered device or mechanism for intentionally generating heat within and/or around the compressor sump volume. Crankcase heater control may be achieved using a timer or may be based on a change in temperature or some other measurable parameter, such that the crankcase heater is not required to operate continuously. A crankcase heater without controls operates continuously when the compressor is not operating.

Cyclic Test means a test where the unit's compressor is cycled on and off for specific time intervals. A cyclic test provides half the information needed to calculate a degradation coefficient.

Damper box means a short section of duct having an air damper that meets the performance requirements of section 2.5.7 of this appendix.

Degradation coefficient (CD) means a parameter used in calculating the part load factor. The degradation coefficient for cooling is denoted by CD c. The degradation coefficient for heating is denoted by CD h.

Demand-defrost control system means a system that defrosts the heat pump outdoor coil-only when measuring a predetermined degradation of performance. The heat pump's controls either:

(1) Monitor one or more parameters that always vary with the amount of frost accumulated on the outdoor coil (e.g., coil to air differential temperature, coil differential air pressure, outdoor fan power or current, optical sensors) at least once for every ten minutes of compressor ON-time when space heating; or

(2) Operate as a feedback system that measures the length of the defrost period and adjusts defrost frequency accordingly. In all cases, when the frost parameter(s) reaches a predetermined value, the system initiates a defrost. In a demand-defrost control system, defrosts are terminated based on monitoring a parameter(s) that indicates that frost has been eliminated from the coil. (Note: Systems that vary defrost intervals according to outdoor dry-bulb temperature are not demand-defrost systems.) A demand-defrost control system, which otherwise meets the requirements, may allow time-initiated defrosts if, and only if, such defrosts occur after 6 hours of compressor operating time.

Design heating requirement (DHR) predicts the space heating load of a residence when subjected to outdoor design conditions. Estimates for the minimum and maximum DHR are provided for six generalized U.S. climatic regions in section 4.2 of this appendix.

Dry-coil tests are cooling mode tests where the wet-bulb temperature of the air supplied to the indoor unit is maintained low enough that no condensate forms on the evaporator coil.

Ducted system means an air conditioner or heat pump that is designed to be permanently installed equipment and delivers conditioned air to the indoor space through a duct(s). The air conditioner or heat pump may be either a split-system or a single-package unit.

Energy efficiency ratio (EER) means the ratio of the average rate of space cooling delivered to the average rate of electrical energy consumed by the air conditioner or heat pump. Determine these rate quantities from a single test or, if derived via interpolation, determine at a single set of operating conditions. EER is expressed in units of

When determined for a ducted coil-only system, EER must include, from this appendix, the section 3.3 and 3.5.1 default values for the heat output and power input of a fan motor. The represented value of EER determined in accordance with appendix M1 is EER2.

Evaporator coil means an assembly that absorbs heat from an enclosed space and transfers the heat to a refrigerant.

Heat pump means a kind of central air conditioner that utilizes an indoor conditioning coil, compressor, and refrigerant-to-outdoor air heat exchanger to provide air heating, and may also provide air cooling, air dehumidifying, air humidifying, air circulating, and air cleaning.

Heat pump having a heat comfort controller means a heat pump with controls that can regulate the operation of the electric resistance elements to assure that the air temperature leaving the indoor section does not fall below a specified temperature. Heat pumps that actively regulate the rate of electric resistance heating when operating below the balance point (as the result of a second stage call from the thermostat) but do not operate to maintain a minimum delivery temperature are not considered as having a heat comfort controller.

Heating load factor (HLF) means the ratio having as its numerator the total heating delivered during a cyclic operating interval consisting of one ON period and one OFF period, and its denominator the heating capacity measured at the same test conditions used for the cyclic test, multiplied by the total time interval (ON plus OFF) of the cyclic-test.

Heating season means the months of the year that require heating, e.g., typically, and roughly, October through April.

Heating seasonal performance factor 2 (HSPF2) means the total space heating required during the heating season, expressed in Btu, divided by the total electrical energy consumed by the heat pump system during the same season, expressed in watt-hours. The HSPF2 used to evaluate compliance with 10 Cspan 430.32(c) is based on Region IV and the sampling plan stated in 10 Cspan 429.16(a). HSPF2 is determined in accordance with appendix M1.

Independent coil manufacturer (ICM) means a manufacturer that manufactures indoor units but does not manufacture single-package units or outdoor units.

Indoor unit means a separate assembly of a split system that includes—

(a) An arrangement of refrigerant-to-air heat transfer coil(s) for transfer of heat between the refrigerant and the indoor air,

(b) A condensate drain pan, and may or may not include,

(c) Sheet metal or plastic parts not part of external cabinetry to direct/route airflow over the coil(s),

(d) A cooling mode expansion device,

(e) External cabinetry, and

(f) An integrated indoor blower (i.e. a device to move air including its associated motor). A separate designated air mover that may be a furnace or a modular blower (as defined in appendix AA to the subpart) may be considered to be part of the indoor unit. A service coil is not an indoor unit.

Low-static blower coil system means a ducted multi-split or multi-head mini-split system for which all indoor units produce greater than 0.01 in. wc. and a maximum of 0.35 in. wc. external static pressure when operated at the cooling full-load air volume rate not exceeding 400 cfm per rated ton of cooling.

Mid-static blower coil system means a ducted multi-split or multi-head mini-split system for which all indoor units produce greater than 0.20 in. wc. and a maximum of 0.65 in. wc. when operated at the cooling full-load air volume rate not exceeding 400 cfm per rated ton of cooling.

Minimum-speed-limiting variable-speed heat pump means a heat pump for which the compressor minimum speed (represented by revolutions per minute or motor power input frequency) is higher than its minimum value for operation in a 47 °F ambient temperature for any bin temperature Tj for which the calculated heating load is less than the calculated intermediate-speed capacity.

Mobile home blower coil system means a split system that contains an outdoor unit and an indoor unit that meet the following criteria:

(1) Both the indoor and outdoor unit are shipped with manufacturer-supplied installation instructions that specify installation only in a mobile home with the home and equipment complying with HUD Manufactured Home Construction Safety Standard 24 Cspan part 3280;

(2) The indoor unit cannot exceed 0.40 in. wc. when operated at the cooling full-load air volume rate not exceeding 400 cfm per rated ton of cooling; and

(3) The indoor and outdoor unit each must bear a label in at least 1/4 inch font that reads “For installation only in HUD manufactured home per Construction Safety Standard 24 Cspan part 3280.”

Mobile home coil-only system means a coil-only split system that includes an outdoor unit and coil-only indoor unit that meet the following criteria:

(1) The outdoor unit is shipped with manufacturer-supplied installation instructions that specify installation only for mobile homes that comply with HUD Manufactured Home Construction Safety Standard 24 Cspan part 3280,

(2) The coil-only indoor unit is shipped with manufacturer-supplied installation instructions that specify installation only in or with a mobile home furnace, modular blower, or designated air mover that complies with HUD Manufactured Home Construction Safety Standard 24 Cspan part 3280, and has dimensions no greater than 20” wide, 34” high and 21” deep, and

(3) The coil-only indoor unit and outdoor unit each has a label in at least 1/4 inch font that reads “For installation only in HUD manufactured home per Construction Safety Standard 24 Cspan part 3280.”

Multi-head mini-split system means a split system that has one outdoor unit and that has two or more indoor units connected with a single refrigeration circuit. The indoor units operate in unison in response to a single indoor thermostat.

Multiple-circuit (or multi-circuit) system means a split system that has one outdoor unit and that has two or more indoor units installed on two or more refrigeration circuits such that each refrigeration circuit serves a compressor and one and only one indoor unit, and refrigerant is not shared from circuit to circuit.

Multiple-split (or multi-split) system means a split system that has one outdoor unit and two or more coil-only indoor units and/or blower coil indoor units connected with a single refrigerant circuit. The indoor units operate independently and can condition multiple zones in response to at least two indoor thermostats or temperature sensors. The outdoor unit operates in response to independent operation of the indoor units based on control input of multiple indoor thermostats or temperature sensors, and/or based on refrigeration circuit sensor input (e.g., suction pressure).

Nominal capacity means the capacity that is claimed by the manufacturer on the product name plate. Nominal cooling capacity is approximate to the air conditioner cooling capacity tested at A or A2 condition. Nominal heating capacity is approximate to the heat pump heating capacity tested in the H1N test.

Non-ducted indoor unit means an indoor unit that is designed to be permanently installed, mounted on room walls and/or ceilings, and that directly heats or cools air within the conditioned space.

Normalized Gross Indoor Fin Surface (NGIFS) means the gross fin surface area of the indoor unit coil divided by the cooling capacity measured for the A or A2 Test, whichever applies.

Off-mode power consumption means the power consumption when the unit is connected to its main power source but is neither providing cooling nor heating to the building it serves.

Off-mode season means, for central air conditioners other than heat pumps, the shoulder season and the entire heating season; and for heat pumps, the shoulder season only.

Outdoor unit means a separate assembly of a split system that transfers heat between the refrigerant and the outdoor air, and consists of an outdoor coil, compressor(s), an air moving device, and in addition for heat pumps, may include a heating mode expansion device, reversing valve, and/or defrost controls.

Outdoor unit manufacturer (OUM) means a manufacturer of single-package units, outdoor units, and/or both indoor units and outdoor units.

Part-load factor (PLF) means the ratio of the cyclic EER (or COP for heating) to the steady-state EER (or COP), where both EERs (or COPs) are determined based on operation at the same ambient conditions.

Seasonal energy efficiency ratio 2 (SEER2) means the total heat removed from the conditioned space during the annual cooling season, expressed in Btu's, divided by the total electrical energy consumed by the central air conditioner or heat pump during the same season, expressed in watt-hours. SEER2 is determined in accordance with appendix M1.

Service coil means an arrangement of refrigerant-to-air heat transfer coil(s), condensate drain pan, sheet metal or plastic parts to direct/route airflow over the coil(s), which may or may not include external cabinetry and/or a cooling mode expansion device, distributed in commerce solely for replacing an uncased coil or cased coil that has already been placed into service, and that has been labeled “for indoor coil replacement only” on the nameplate and in manufacturer technical and product literature. The model number for any service coil must include some mechanism (e.g., an additional letter or number) for differentiating a service coil from a coil intended for an indoor unit.

Shoulder season means the months of the year in between those months that require cooling and those months that require heating, e.g., typically, and roughly, April through May, and September through October.

Single-package unit means any central air conditioner or heat pump that has all major assemblies enclosed in one cabinet.

Single-split system means a split system that has one outdoor unit and one indoor unit connected with a single refrigeration circuit.

Small-duct, high-velocity system means a split system for which all indoor units are blower coil indoor units that produce at least 1.2 inches (of water column) of external static pressure when operated at the full-load air volume rate certified by the manufacturer of at least 220 scfm per rated ton of cooling.

Split system means any central air conditioner or heat pump that has at least two separate assemblies that are connected with refrigerant piping when installed. One of these assemblies includes an indoor coil that exchanges heat with the indoor air to provide heating or cooling, while one of the others includes an outdoor coil that exchanges heat with the outdoor air. Split systems may be either blower coil systems or coil-only systems.

Standard Air means dry air having a mass density of 0.075 lb/ft 3.

Steady-state test means a test where the test conditions are regulated to remain as constant as possible while the unit operates continuously in the same mode.

Temperature bin means the 5 °F increments that are used to partition the outdoor dry-bulb temperature ranges of the cooling (≥65 °F) and heating (<65 °F) seasons.

Test condition tolerance means the maximum permissible difference between the average value of the measured test parameter and the specified test condition.

Test operating tolerance means the maximum permissible range that a measurement may vary over the specified test interval. The difference between the maximum and minimum sampled values must be less than or equal to the specified test operating tolerance.

Tested combination means a multi-head mini-split, multi-split, or multi-circuit system having the following features:

(1) The system consists of one outdoor unit with one or more compressors matched with between two and five indoor units;

(2) The indoor units must:

(i) Collectively, have a nominal cooling capacity greater than or equal to 95 percent and less than or equal to 105 percent of the nominal cooling capacity of the outdoor unit;

(ii) Each represent the highest sales volume model family, if this is possible while meeting all the requirements of this section. If this is not possible, one or more of the indoor units may represent another indoor model family in order that all the other requirements of this section are met.

(iii) Individually not have a nominal cooling capacity greater than 50 percent of the nominal cooling capacity of the outdoor unit, unless the nominal cooling capacity of the outdoor unit is 24,000 Btu/h or less;

(iv) Operate at fan speeds consistent with manufacturer's specifications; and

(v) All be subject to the same minimum external static pressure requirement while able to produce the same external static pressure at the exit of each outlet plenum when connected in a manifold configuration as required by the test procedure.

(3) Where referenced, “nominal cooling capacity” means, for indoor units, the highest cooling capacity listed in published product literature for 95 °F outdoor dry bulb temperature and 80 °F dry bulb, 67 °F wet bulb indoor conditions, and for outdoor units, the lowest cooling capacity listed in published product literature for these conditions. If incomplete or no operating conditions are published, use the highest (for indoor units) or lowest (for outdoor units) such cooling capacity available for sale.

Time-adaptive defrost control system is a demand-defrost control system that measures the length of the prior defrost period(s) and uses that information to automatically determine when to initiate the next defrost cycle.

Time-temperature defrost control systems initiate or evaluate initiating a defrost cycle only when a predetermined cumulative compressor ON-time is obtained. This predetermined ON-time is generally a fixed value (e.g., 30, 45, 90 minutes) although it may vary based on the measured outdoor dry-bulb temperature. The ON-time counter accumulates if controller measurements (e.g., outdoor temperature, evaporator temperature) indicate that frost formation conditions are present, and it is reset/remains at zero at all other times. In one application of the control scheme, a defrost is initiated whenever the counter time equals the predetermined ON-time. The counter is reset when the defrost cycle is completed.

In a second application of the control scheme, one or more parameters are measured (e.g., air and/or refrigerant temperatures) at the predetermined, cumulative, compressor ON-time. A defrost is initiated only if the measured parameter(s) falls within a predetermined range. The ON-time counter is reset regardless of whether or not a defrost is initiated. If systems of this second type use cumulative ON-time intervals of 10 minutes or less, then the heat pump may qualify as having a demand defrost control system (see definition).

Triple-capacity, northern heat pump means a heat pump that provides two stages of cooling and three stages of heating. The two common stages for both the cooling and heating modes are the low capacity stage and the high capacity stage. The additional heating mode stage is the booster capacity stage, which offers the highest heating capacity output for a given set of ambient operating conditions.

Triple-split system means a split system that is composed of three separate assemblies: An outdoor fan coil section, a blower coil indoor unit, and an indoor compressor section.

Two-capacity (or two-stage) compressor system means a central air conditioner or heat pump that has a compressor or a group of compressors operating with only two stages of capacity. For such systems, low capacity means the compressor(s) operating at low stage, or at low load test conditions. The low compressor stage that operates for heating mode tests may be the same or different from the low compressor stage that operates for cooling mode tests. For such systems, high capacity means the compressor(s) operating at high stage, or at full load test conditions.

Two-capacity, northern heat pump means a heat pump that has a factory or field-selectable lock-out feature to prevent space cooling at high-capacity. Two-capacity heat pumps having this feature will typically have two sets of ratings, one with the feature disabled and one with the feature enabled. The heat pump is a two-capacity northern heat pump only when this feature is enabled at all times. The certified indoor coil model number must reflect whether the ratings pertain to the lockout enabled option via the inclusion of an extra identifier, such as “+LO”. When testing as a two-capacity, northern heat pump, the lockout feature must remain enabled for all tests.

Uncased coil means a coil-only indoor unit without external cabinetry.

Variable refrigerant flow (VRF) system means a multi-split system with at least three compressor capacity stages, distributing refrigerant through a piping network to multiple indoor blower coil units each capable of individual zone temperature control, through proprietary zone temperature control devices and a common communications network. Note: Single-phase VRF systems less than 65,000 Btu/h are central air conditioners and central air conditioning heat pumps.

Variable-speed communicating coil-only central air conditioner or heat pump means a variable-speed compressor system having a coil-only indoor unit that is installed with a control system that:

(a) Communicates the difference in space temperature and space setpoint temperature (not a setpoint value inferred from on/off thermostat signals) to the control that sets compressor speed;

(b) Provides a signal to the indoor fan to set fan speed appropriate for compressor staging; and

(c) Has installation instructions indicating that the control system having these capabilities must be installed.

Variable-speed compressor system means a central air conditioner or heat pump that has a compressor that uses a variable-speed drive to vary the compressor speed to achieve variable capacities.

Variable-speed non-communicating coil-only central air conditioner or heat pump means a variable-speed compressor system having a coil-only indoor unit that is does not meet the definition of variable-speed communicating coil-only central air conditioner or heat pump.

Wall-mount blower coil system means a split system air conditioner or heat pump for which:

(a) The outdoor unit has a certified cooling capacity less than or equal to 36,000 Btu/h;

(b) The indoor unit(s) is/are shipped with manufacturer-supplied installation instructions that specify mounting only by:

(1) Securing the back side of the unit to a wall within the conditioned space, or

(2) Securing the unit to adjacent wall studs or in an enclosure, such as a closet, such that the indoor unit's front face is flush with a wall in the conditioned space;

(c) Has front air return without ductwork and is not capable of horizontal air discharge; and

(d) Has a height no more than 45 inches, a depth (perpendicular to the wall) no more than 22 inches (including tubing connections), and a width no more than 24 inches (parallel to the wall).

Wet-coil test means a test conducted at test conditions that typically cause water vapor to condense on the test unit evaporator coil.

2 Testing Overview and Conditions

(A) Test VRF systems using AHRI 1230-2010 (incorporated by reference, see § 430.3) and appendix M. Where AHRI 1230-2010 refers to the appendix C therein substitute the provisions of this appendix. In cases where there is a conflict, the language of the test procedure in this appendix takes precedence over AHRI 1230-2010.

For definitions use section 1 of appendix M and section 3 of AHRI 1230-2010. For rounding requirements, refer to § 430.23(m). For determination of certified ratings, refer to § 429.16 of this chapter.

For test room requirements, refer to section 2.1 of this appendix. For test unit installation requirements refer to sections 2.2.a, 2.2.b, 2.2.c, 2.2.1, 2.2.2, 2.2.3.a, 2.2.3.c, 2.2.4, 2.2.5, and 2.4 to 2.12 of this appendix, and sections 5.1.3 and 5.1.4 of AHRI 1230-2010. The “manufacturer's published instructions,” as stated in section 8.2 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3) and “manufacturer's installation instructions” discussed in this appendix mean the manufacturer's installation instructions that come packaged with or appear in the labels applied to the unit. This does not include online manuals. Installation instructions that appear in the labels applied to the unit take precedence over installation instructions that are shipped with the unit.

For general requirements for the test procedure, refer to section 3.1 of this appendix, except for sections 3.1.3 and 3.1.4, which are requirements for indoor air volume and outdoor air volume. For indoor air volume and outdoor air volume requirements, refer instead to section 6.1.5 (except where section 6.1.5 refers to Table 8, refer instead to Table 4 of this appendix) and 6.1.6 of AHRI 1230-2010.

For the test method, refer to sections 3.3 to 3.5 and 3.7 to 3.13 of this appendix. For cooling mode and heating mode test conditions, refer to section 6.2 of AHRI 1230-2010. For calculations of seasonal performance descriptors, refer to section 4 of this appendix.

(B) For systems other than VRF, only a subset of the sections listed in this test procedure apply when testing and determining represented values for a particular unit. Table 1 to this appendix shows the sections of the test procedure that apply to each system. Table 1 is meant to assist manufacturers in finding the appropriate sections of the test procedure. Manufacturers are responsible for determining which sections apply to each unit tested based on the model characteristics. The appendix sections provide the specific requirements for testing. To use Table 1, first refer to the sections listed under “all units”. Then refer to additional requirements based on:

(1) System configuration(s),

(2) The compressor staging or modulation capability, and

(3) Any special features.

Testing requirements for space-constrained products do not differ from similar products that are not space-constrained, and thus space-constrained products are not listed separately in Table 1. Air conditioners and heat pumps are not listed separately in Table 1, but heating procedures and calculations apply only to heat pumps.

The “manufacturer's published instructions,” as stated in Section 8.2 of ANSI/ASHRAE Standard 37-2009 (incorporated by reference, see § 430.3) and “manufacturer's installation instructions” discussed in this appendix mean the manufacturer's installation instructions that come packaged with the unit or appear in the labels applied to the unit. Manufacturer's installation instructions do not include online manuals. Installation instructions that appear in the labels applied to the unit shall take precedence over installation instructions that come packaged with the unit.

2.1 Test Room Requirements.

a. Test using two side-by-side rooms: An indoor test room and an outdoor test room. For multiple-split, single-zone-multi-coil or multi-circuit air conditioners and heat pumps, however, use as many indoor test rooms as needed to accommodate the total number of indoor units. These rooms must comply with the requirements specified in sections 8.1.2 and 8.1.3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3).

b. Inside these test rooms, use artificial loads during cyclic tests and frost accumulation tests, if needed, to produce stabilized room air temperatures. For one room, select an electric resistance heater(s) having a heating capacity that is approximately equal to the heating capacity of the test unit's condenser. For the second room, select a heater(s) having a capacity that is close to the sensible cooling capacity of the test unit's evaporator. Cycle the heater located in the same room as the test unit evaporator coil ON and OFF when the test unit cycles ON and OFF. Cycle the heater located in the same room as the test unit condensing coil ON and OFF when the test unit cycles OFF and ON.

2.2 Test Unit Installation Requirements.

a. Install the unit according to section 8.2 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3), subject to the following additional requirements:

(1) When testing split systems, follow the requirements given in section 6.1.3.5 of AHRI 210/240-2008 (incorporated by reference, see § 430.3). For the vapor refrigerant line(s), use the insulation included with the unit; if no insulation is provided, use insulation meeting the specifications for the insulation in the installation instructions included with the unit by the manufacturer; if no insulation is included with the unit and the installation instructions do not contain provisions for insulating the line(s), fully insulate the vapor refrigerant line(s) with vapor proof insulation having an inside diameter that matches the refrigerant tubing and a nominal thickness of at least 0.5 inches. For the liquid refrigerant line(s), use the insulation included with the unit; if no insulation is provided, use insulation meeting the specifications for the insulation in the installation instructions included with the unit by the manufacturer; if no insulation is included with the unit and the installation instructions do not contain provisions for insulating the line(s), leave the liquid refrigerant line(s) exposed to the air for air conditioners and heat pumps that heat and cool; or, for heating-only heat pumps, insulate the liquid refrigerant line(s) with insulation having an inside diameter that matches the refrigerant tubing and a nominal thickness of at least 0.5 inches. However, these requirements do not take priority over instructions for application of insulation for the purpose of improving refrigerant temperature measurement accuracy as required by sections 2.10.2 and 2.10.3 of this appendix. Insulation must be the same for the cooling and heating tests.

(2) When testing split systems, if the indoor unit does not ship with a cooling mode expansion device, test the system using the device as specified in the installation instructions provided with the indoor unit. If none is specified, test the system using a fixed orifice or piston type expansion device that is sized appropriately for the system.

(3) When testing triple-split systems (see section 1.2 of this appendix, Definitions), use the tubing length specified in section 6.1.3.5 of AHRI 210/240-2008 (incorporated by reference, see § 430.3) to connect the outdoor coil, indoor compressor section, and indoor coil while still meeting the requirement of exposing 10 feet of the tubing to outside conditions;

(4) When testing split systems having multiple indoor coils, connect each indoor blower coil unit to the outdoor unit using:

(a) 25 feet of tubing, or

(b) Tubing furnished by the manufacturer, whichever is longer.

(5) When testing split systems having multiple indoor coils, expose at least 10 feet of the system interconnection tubing to the outside conditions. If they are needed to make a secondary measurement of capacity or for verification of refrigerant charge, install refrigerant pressure measuring instruments as described in section 8.2.5 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3). Section 2.10 of this appendix specifies which secondary methods require refrigerant pressure measurements and section 2.2.5.5 of this appendix discusses use of pressure measurements to verify charge. At a minimum, insulate the low-pressure line(s) of a split system with insulation having an inside diameter that matches the refrigerant tubing and a nominal thickness of 0.5 inch.

b. For units designed for both horizontal and vertical installation or for both up-flow and down-flow vertical installations, use the orientation for testing specified by the manufacturer in the certification report. Conduct testing with the following installed:

(1) The most restrictive filter(s);

(2) Supplementary heating coils; and

(3) Other equipment specified as part of the unit, including all hardware used by a heat comfort controller if so equipped (see section 1 of this appendix, Definitions). For small-duct, high-velocity systems, configure all balance dampers or restrictor devices on or inside the unit to fully open or lowest restriction.

c. Testing a ducted unit without having an indoor air filter installed is permissible as long as the minimum external static pressure requirement is adjusted as stated in Table 4, note 3 (see section 3.1.4 of this appendix). Except as noted in section 3.1.10 of this appendix, prevent the indoor air supplementary heating coils from operating during all tests. For uncased coils, create an enclosure using 1 inch fiberglass foil-faced ductboard having a nominal density of 6 pounds per cubic foot. Or alternatively, construct an enclosure using sheet metal or a similar material and insulating material having a thermal resistance (“R” value) between 4 and 6 hr · ft 2 · °F/Btu. Size the enclosure and seal between the coil and/or drainage pan and the interior of the enclosure as specified in installation instructions shipped with the unit. Also seal between the plenum and inlet and outlet ducts.

d. When testing a coil-only system, install a toroidal-type transformer to power the system's low-voltage components, complying with any additional requirements for the transformer mentioned in the installation manuals included with the unit by the system manufacturer. If the installation manuals do not provide specifications for the transformer, use a transformer having the following features:

(1) A nominal volt-amp rating such that the transformer is loaded between 25 and 90 percent of this rating for the highest level of power measured during the off mode test (section 3.13 of this appendix);

(2) Designed to operate with a primary input of 230 V, single phase, 60 Hz; and

(3) That provides an output voltage that is within the specified range for each low-voltage component. Include the power consumption of the components connected to the transformer as part of the total system power consumption during the off mode tests; do not include the power consumed by the transformer when no load is connected to it.

e. Test an outdoor unit with no match (i.e., that is not distributed in commerce with any indoor units) using a coil-only indoor unit with a single cooling air volume rate whose coil has:

(1) Round tubes of outer diameter no less than 0.375 inches, and

(2) A normalized gross indoor fin surface (NGIFS) no greater than 1.0 square inch per British thermal unit per hour (sq. in./Btu/hr). NGIFS is calculated as follows:

NGIFS = 2 × Lf × Wf × Nf ÷ Q c(95)

where, Lf = Indoor coil fin length in inches, also height of the coil transverse to the tubes. Wf = Indoor coil fin width in inches, also depth of the coil. Nf = Number of fins. Q c = the measured space cooling capacity of the tested outdoor unit/indoor unit combination as determined from the A2 or A Test whichever applies, Btu/h.

f. If the outdoor unit or the outdoor portion of a single-package unit has a drain pan heater to prevent freezing of defrost water, energize the heater, subject to control to de-energize it when not needed by the heater's thermostat or the unit's control system, for all tests.

g. If pressure measurement devices are connected to a cooling/heating heat pump refrigerant circuit, the refrigerant charge Mt that could potentially transfer out of the connected pressure measurement systems (transducers, gauges, connections, and lines) between operating modes must be less than 2 percent of the factory refrigerant charge listed on the nameplate of the outdoor unit. If the outdoor unit nameplate has no listed refrigerant charge, or the heat pump is shipped without a refrigerant charge, use a factory refrigerant charge equal to 30 ounces per ton of certified cooling capacity. Use Equation 2.2-1 to calculate Mt for heat pumps that have a single expansion device located in the outdoor unit to serve each indoor unit, and use Equation 2.2-2 to calculate Mt for heat pumps that have two expansion devices per indoor unit.

where: Vi (i=2,3,4 . . .) = the internal volume of the pressure measurement system (pressure lines, fittings, and gauge and/or transducer) at the location i (as indicated in Table 2), (cubic inches) fi (i=5,6) = 0 if the pressure measurement system is pitched upwards from the pressure tap location to the gauge or transducer, 1 if it is not. r = the density associated with liquid refrigerant at 100 °F bubble point conditions (ounces per cubic inch)

Table 2—Pressure Measurement Locations

Location Compressor Discharge1 Between Outdoor Coil and Outdoor Expansion Valve(s)2 Liquid Service Valve3 Indoor Coil Inlet4 Indoor Coil Outlet5 Common Suction Port (i.e., vapor service valve)6 Compressor Suction7

Calculate the internal volume of each pressure measurement system using internal volume reported for pressure transducers and gauges in product literature, if available. If such information is not available, use the value of 0.1 cubic inch internal volume for each pressure transducer, and 0.2 cubic inches for each pressure gauge.

In addition, for heat pumps that have a single expansion device located in the outdoor unit to serve each indoor unit, the internal volume of the pressure system at location 2 (as indicated in Table 2) must be no more than 1 cubic inches. Once the pressure measurement lines are set up, no change should be made until all tests are finished.

2.2.1 Defrost Control Settings

Set heat pump defrost controls at the normal settings which most typify those encountered in generalized climatic region IV. (Refer to Figure 1 and Table 20 of section 4.2 of this appendix for information on region IV.) For heat pumps that use a time-adaptive defrost control system (see section 1.2 of this appendix, Definitions), the manufacturer must specify in the certification report the frosting interval to be used during frost accumulation tests and provide the procedure for manually initiating the defrost at the specified time.

2.2.2 Special Requirements for Units Having a Multiple-Speed Outdoor Fan

Configure the multiple-speed outdoor fan according to the installation manual included with the unit by the manufacturer, and thereafter, leave it unchanged for all tests. The controls of the unit must regulate the operation of the outdoor fan during all lab tests except dry coil cooling mode tests. For dry coil cooling mode tests, the outdoor fan must operate at the same speed used during the required wet coil test conducted at the same outdoor test conditions.

2.2.3 Special Requirements for Multi-Split Air Conditioners and Heat Pumps and Ducted Systems Using a Single Indoor Section Containing Multiple Indoor Blowers That Would Normally Operate Using Two or More Indoor Thermostats

Because these systems will have more than one indoor blower and possibly multiple outdoor fans and compressor systems, references in this test procedure to a singular indoor blower, outdoor fan, and/or compressor means all indoor blowers, all outdoor fans, and all compressor systems that are energized during the test.

a. Additional requirements for multi-split air conditioners and heat pumps. For any test where the system is operated at part load (i.e., one or more compressors “off”, operating at the intermediate or minimum compressor speed, or at low compressor capacity), the manufacturer must designate in the certification report the indoor coil(s) that are not providing heating or cooling during the test. For variable-speed systems, the manufacturer must designate in the certification report at least one indoor unit that is not providing heating or cooling for all tests conducted at minimum compressor speed. For all other part-load tests, the manufacturer must choose to turn off zero, one, two, or more indoor units. The chosen configuration must remain unchanged for all tests conducted at the same compressor speed/capacity. For any indoor coil that is not providing heating or cooling during a test, cease forced airflow through this indoor coil and block its outlet duct.

b. Additional requirements for ducted split systems with a single indoor unit containing multiple indoor blowers (or for single-package units with an indoor section containing multiple indoor blowers) where the indoor blowers are designed to cycle on and off independently of one another and are not controlled such that all indoor blowers are modulated to always operate at the same air volume rate or speed. For any test where the system is operated at its lowest capacity—i.e., the lowest total air volume rate allowed when operating the single-speed compressor or when operating at low compressor capacity—turn off indoor blowers accounting for at least one-third of the full-load air volume rate unless prevented by the controls of the unit. In such cases, turn off as many indoor blowers as permitted by the unit's controls. Where more than one option exists for meeting this “off” requirement, the manufacturer must indicate in its certification report which indoor blower(s) are turned off. The chosen configuration shall remain unchanged for all tests conducted at the same lowest capacity configuration. For any indoor coil turned off during a test, cease forced airflow through any outlet duct connected to a switched-off indoor blower.

c. For test setups where the laboratory's physical limitations require use of more than the required line length of 25 feet as listed in section 2.2.a.(4) of this appendix, then the actual refrigerant line length used by the laboratory may exceed the required length and the refrigerant line length correction factors in Table 4 of AHRI 1230-2010 are applied to the cooling capacity measured for each cooling mode test.

2.2.4 Wet-Bulb Temperature Requirements for the Air Entering the Indoor and Outdoor Coils 2.2.4.1 Cooling Mode Tests

For wet-coil cooling mode tests, regulate the water vapor content of the air entering the indoor unit so that the wet-bulb temperature is as listed in Tables 5 to 8. As noted in these same tables, achieve a wet-bulb temperature during dry-coil cooling mode tests that results in no condensate forming on the indoor coil. Controlling the water vapor content of the air entering the outdoor side of the unit is not required for cooling mode tests except when testing:

(1) Units that reject condensate to the outdoor coil during wet coil tests. Tables 5-8 list the applicable wet-bulb temperatures.

(2) Single-package units where all or part of the indoor section is located in the outdoor test room. The average dew point temperature of the air entering the outdoor coil during wet coil tests must be within ±3.0 °F of the average dew point temperature of the air entering the indoor coil over the 30-minute data collection interval described in section 3.3 of this appendix. For dry coil tests on such units, it may be necessary to limit the moisture content of the air entering the outdoor coil of the unit to meet the requirements of section 3.4 of this appendix.

2.2.4.2 Heating Mode Tests

For heating mode tests, regulate the water vapor content of the air entering the outdoor unit to the applicable wet-bulb temperature listed in Tables 12 to 15. The wet-bulb temperature entering the indoor side of the heat pump must not exceed 60 °F. Additionally, if the Outdoor Air Enthalpy test method (section 2.10.1 of this appendix) is used while testing a single-package heat pump where all or part of the outdoor section is located in the indoor test room, adjust the wet-bulb temperature for the air entering the indoor side to yield an indoor-side dew point temperature that is as close as reasonably possible to the dew point temperature of the outdoor-side entering air.

2.2.5 Additional Refrigerant Charging Requirements 2.2.5.1 Instructions to Use for Charging

a. Where the manufacturer's installation instructions contain two sets of refrigerant charging criteria, one for field installations and one for lab testing, use the field installation criteria.

b. For systems consisting of an outdoor unit manufacturer's outdoor section and indoor section with differing charging procedures, adjust the refrigerant charge per the outdoor installation instructions.

c. For systems consisting of an outdoor unit manufacturer's outdoor unit and an independent coil manufacturer's indoor unit with differing charging procedures, adjust the refrigerant charge per the indoor unit's installation instructions. If instructions are provided only with the outdoor unit or are provided only with an independent coil manufacturer's indoor unit, then use the provided instructions.

2.2.5.2 Test(s) to Use for Charging

a. Use the tests or operating conditions specified in the manufacturer's installation instructions for charging. The manufacturer's installation instructions may specify use of tests other than the A or A2 test for charging, but, unless the unit is a heating-only heat pump, determine the air volume rate by the A or A2 test as specified in section 3.1 of this appendix.

b. If the manufacturer's installation instructions do not specify a test or operating conditions for charging or there are no manufacturer's instructions, use the following test(s):

(1) For air conditioners or cooling and heating heat pumps, use the A or A2 test.

(2) For cooling and heating heat pumps that do not operate in the H1 or H12 test (e.g. due to shut down by the unit limiting devices) when tested using the charge determined at the A or A2 test, and for heating-only heat pumps, use the H1 or H12 test.

2.2.5.3 Parameters to Set and Their Target Values

a. Consult the manufacturer's installation instructions regarding which parameters (e.g., superheat) to set and their target values. If the instructions provide ranges of values, select target values equal to the midpoints of the provided ranges.

b. In the event of conflicting information between charging instructions (i.e., multiple conditions given for charge adjustment where all conditions specified cannot be met), follow the following hierarchy.

(1) For fixed orifice systems:

(i) Superheat

(ii) High side pressure or corresponding saturation or dew-point temperature

(iii) Low side pressure or corresponding saturation or dew-point temperature

(iv) Low side temperature

(v) High side temperature

(vi) Charge weight

(2) For expansion valve systems:

(i) Subcooling

(ii) High side pressure or corresponding saturation or dew-point temperature

(iii) Low side pressure or corresponding saturation or dew-point temperature

(iv) Approach temperature (difference between temperature of liquid leaving condenser and condenser average inlet air temperature)

(v) Charge weight

c. If there are no installation instructions and/or they do not provide parameters and target values, set superheat to a target value of 12 °F for fixed orifice systems or set subcooling to a target value of 10 °F for expansion valve systems.

2.2.5.4 Charging Tolerances

a. If the manufacturer's installation instructions specify tolerances on target values for the charging parameters, set the values within these tolerances.

b. Otherwise, set parameter values within the following test condition tolerances for the different charging parameters:

11. Superheat: ± 2.0 °F

12. Subcooling: ± 2.0 °F

13. High side pressure or corresponding saturation or dew point temperature: ± 4.0 psi or ± 1.0 °F

14. Low side pressure or corresponding saturation or dew point temperature: ± 2.0 psi or ± 0.8 °F

15. High side temperature: ± 2.0 °F

16. Low side temperature: ± 2.0 °F

17. Approach temperature: ± 1.0 °F

18. Charge weight: ± 2.0 ounce

2.2.5.5 Special Charging Instructions

a. Cooling and Heating Heat Pumps

If, using the initial charge set in the A or A2 test, the conditions are not within the range specified in manufacturer's installation instructions for the H1 or H12 test, make as small as possible an adjustment to obtain conditions for this test in the specified range. After this adjustment, recheck conditions in the A or A2 test to confirm that they are still within the specified range for the A or A2 test.

b. Single-Package Systems

i. Unless otherwise directed by the manufacturer's installation instructions, install one or more refrigerant line pressure gauges during the setup of the unit, located depending on the parameters used to verify or set charge, as described:

(1) Install a pressure gauge at the location of the service valve on the liquid line if charging is on the basis of subcooling, or high side pressure or corresponding saturation or dew point temperature;

(2) Install a pressure gauge at the location of the service valve on the suction line if charging is on the basis of superheat, or low side pressure or corresponding saturation or dew point temperature.

ii. Use methods for installing pressure gauge(s) at the required location(s) as indicated in manufacturer's instructions if specified.

2.2.5.6 Near-Azeotropic and Zeotropic Refrigerants

Perform charging of near-azeotropic and zeotropic refrigerants only with refrigerant in the liquid state.

2.2.5.7 Adjustment of Charge Between Tests

After charging the system as described in this test procedure, use the set refrigerant charge for all tests used to determine performance. Do not adjust the refrigerant charge at any point during testing. If measurements indicate that refrigerant charge has leaked during the test, repair the refrigerant leak, repeat any necessary set-up steps, and repeat all tests.

2.3 Indoor Air Volume Rates

If a unit's controls allow for overspeeding the indoor blower (usually on a temporary basis), take the necessary steps to prevent overspeeding during all tests.

2.3.1 Cooling Tests

a. Set indoor blower airflow-control settings (e.g., fan motor pin settings, fan motor speed) according to the requirements that are specified in section 3.1.4 of this appendix.

b. Express the Cooling full-load air volume rate, the Cooling Minimum Air Volume Rate, and the Cooling Intermediate Air Volume Rate in terms of standard air.

2.3.2 Heating Tests

a. Set indoor blower airflow-control settings (e.g., fan motor pin settings, fan motor speed) according to the requirements that are specified in section 3.1.4 of this appendix.

b. Express the heating full-load air volume rate, the heating minimum air volume rate, the heating intermediate air volume rate, and the heating nominal air volume rate in terms of standard air.

2.4 Indoor Coil Inlet and Outlet Duct Connections

Insulate and/or construct the outlet plenum as described in section 2.4.1 of this appendix and, if installed, the inlet plenum described in section 2.4.2 of this appendix with thermal insulation having a nominal overall resistance (R-value) of at least 19 hr·ft 2 °F/Btu.

2.4.1 Outlet Plenum for the Indoor Unit

a. Attach a plenum to the outlet of the indoor coil. (Note: For some packaged systems, the indoor coil may be located in the outdoor test room.)

b. For systems having multiple indoor coils, or multiple indoor blowers within a single indoor section, attach a plenum to each indoor coil or indoor blower outlet. In order to reduce the number of required airflow measurement apparatuses (section 2.6 of this appendix), each such apparatus may serve multiple outlet plenums connected to a single common duct leading to the apparatus. More than one indoor test room may be used, which may use one or more common ducts leading to one or more airflow measurement apparatuses within each test room that contains multiple indoor coils. At the plane where each plenum enters a common duct, install an adjustable airflow damper and use it to equalize the static pressure in each plenum. The outlet air temperature grid(s) (section 2.5.4 of this appendix) and airflow measuring apparatus shall be located downstream of the inlet(s) to the common duct(s). For multiple-circuit (or multi-circuit) systems for which each indoor coil outlet is measured separately and its outlet plenum is not connected to a common duct connecting multiple outlet plenums, install the outlet air temperature grid and airflow measuring apparatus at each outlet plenum.

c. For small-duct, high-velocity systems, install an outlet plenum that has a diameter that is equal to or less than the value listed in Table 3. The limit depends only on the Cooling full-load air volume rate (see section 3.1.4.1.1 of this appendix) and is effective regardless of the flange dimensions on the outlet of the unit (or an air supply plenum adapter accessory, if installed in accordance with the manufacturer's installation instructions).

d. Add a static pressure tap to each face of the (each) outlet plenum, if rectangular, or at four evenly distributed locations along the circumference of an oval or round plenum. Create a manifold that connects the four static pressure taps. Figure 9 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3) shows allowed options for the manifold configuration. The cross-sectional dimensions of plenum must be equal to the dimensions of the indoor unit outlet. See Figures 7a, 7b, and 7c of ANSI/ASHRAE 37-2009 for the minimum length of the (each) outlet plenum and the locations for adding the static pressure taps for ducted blower coil indoor units and single-package systems. See Figure 8 of ANSI/ASHRAE 37-2009 for coil-only indoor units.

Table 3—Size of Outlet Plenum for Small-Duct High-Velocity Indoor Units

Cooling full-load air
volume rate
(scfm)
Maximum diameter* of outlet plenum
(inches)
≤5006 501 to 7007 701 to 9008 901 to 11009 1101 to 140010 1401 to 175011

* If the outlet plenum is rectangular, calculate its equivalent diameter using (4A/P,) where A is the cross-sectional area and P is the perimeter of the rectangular plenum, and compare it to the listed maximum diameter.

2.4.2 Inlet Plenum for the Indoor Unit

Install an inlet plenum when testing a coil-only indoor unit, a ducted blower coil indoor unit, or a single-package system. See Figures 7b and 7c of ANSI/ASHRAE 37-2009 for cross-sectional dimensions, the minimum length of the inlet plenum, and the locations of the static-pressure taps for ducted blower coil indoor units and single-package systems. See Figure 8 of ANSI/ASHRAE 37-2009 for coil-only indoor units. The inlet plenum duct size shall equal the size of the inlet opening of the air-handling (blower coil) unit or furnace. For a ducted blower coil indoor unit the set up may omit the inlet plenum if an inlet airflow prevention device is installed with a straight internally unobstructed duct on its outlet end with a minimum length equal to 1.5 times the square root of the cross-sectional area of the indoor unit inlet. See section 2.1.5.2 of this appendix for requirements for the locations of static pressure taps built into the inlet airflow prevention device. For all of these arrangements, make a manifold that connects the four static-pressure taps using one of the three configurations specified in section 2.4.1.d. of this appendix. Never use an inlet plenum when testing a non-ducted system.

2.5 Indoor Coil Air Property Measurements and Airflow Prevention Devices.

Follow instructions for indoor coil air property measurements as described in section 2.14 of this appendix, unless otherwise instructed in this section.

a. Measure the dry-bulb temperature and water vapor content of the air entering and leaving the indoor coil. If needed, use an air sampling device to divert air to a sensor(s) that measures the water vapor content of the air. See section 5.3 of ANSI/ASHRAE 41.1-2013 (incorporated by reference, see § 430.3) for guidance on constructing an air sampling device. No part of the air sampling device or the tubing transferring the sampled air to the sensor must be within two inches of the test chamber floor, and the transfer tubing must be insulated. The sampling device may also be used for measurement of dry bulb temperature by transferring the sampled air to a remotely located sensor(s). The air sampling device and the remotely located temperature sensor(s) may be used to determine the entering air dry bulb temperature during any test. The air sampling device and the remotely located sensor(s) may be used to determine the leaving air dry bulb temperature for all tests except:

(1) Cyclic tests; and

(2) Frost accumulation tests.

b. Install grids of temperature sensors to measure dry bulb temperatures of both the entering and leaving airstreams of the indoor unit. These grids of dry bulb temperature sensors may be used to measure average dry bulb temperature entering and leaving the indoor unit in all cases (as an alternative to the dry bulb sensor measuring the sampled air). The leaving airstream grid is required for measurement of average dry bulb temperature leaving the indoor unit for cyclic tests and frost accumulation tests. The grids are also required to measure the air temperature distribution of the entering and leaving airstreams as described in sections 3.1.8 of this appendix. Two such grids may be applied as a thermopile, to directly obtain the average temperature difference rather than directly measuring both entering and leaving average temperatures.

c. Use of airflow prevention devices. Use an inlet and outlet air damper box, or use an inlet upturned duct and an outlet air damper box when conducting one or both of the cyclic tests listed in sections 3.2 and 3.6 of this appendix on ducted systems. If not conducting any cyclic tests, an outlet air damper box is required when testing ducted and non-ducted heat pumps that cycle off the indoor blower during defrost cycles and there is no other means for preventing natural or forced convection through the indoor unit when the indoor blower is off. Never use an inlet damper box or an inlet upturned duct when testing non-ducted indoor units. An inlet upturned duct is a length of ductwork installed upstream from the inlet such that the indoor duct inlet opening, facing upwards, is sufficiently high to prevent natural convection transfer out of the duct. If an inlet upturned duct is used, install a dry bulb temperature sensor near the inlet opening of the indoor duct at a centerline location not higher than the lowest elevation of the duct edges at the inlet, and ensure that any pair of 5-minute averages of the dry bulb temperature at this location, measured at least every minute during the compressor OFF period of the cyclic test, do not differ by more than 1.0 °F.

2.5.1 Test Set-Up on the Inlet Side of the Indoor Coil: for Cases Where the Inlet Airflow Prevention Device is Installed

a. Install an airflow prevention device as specified in section 2.5.1.1 or 2.5.1.2 of this appendix, whichever applies.

b. For an inlet damper box, locate the grid of entering air dry-bulb temperature sensors, if used, and the air sampling device, or the sensor used to measure the water vapor content of the inlet air, at a location immediately upstream of the damper box inlet. For an inlet upturned duct, locate the grid of entering air dry-bulb temperature sensors, if used, and the air sampling device, or the sensor used to measure the water vapor content of the inlet air, at a location at least one foot downstream from the beginning of the insulated portion of the duct but before the static pressure measurement.

2.5.1.1 If the section 2.4.2 inlet plenum is installed, construct the airflow prevention device having a cross-sectional flow area equal to or greater than the flow area of the inlet plenum. Install the airflow prevention device upstream of the inlet plenum and construct ductwork connecting it to the inlet plenum. If needed, use an adaptor plate or a transition duct section to connect the airflow prevention device with the inlet plenum. Insulate the ductwork and inlet plenum with thermal insulation that has a nominal overall resistance (R-value) of at least 19 hr · ft 2 · °F/Btu.

2.5.1.2 If the section 2.4.2 inlet plenum is not installed, construct the airflow prevention device having a cross-sectional flow area equal to or greater than the flow area of the air inlet of the indoor unit. Install the airflow prevention device immediately upstream of the inlet of the indoor unit. If needed, use an adaptor plate or a short transition duct section to connect the airflow prevention device with the unit's air inlet. Add static pressure taps at the center of each face of a rectangular airflow prevention device, or at four evenly distributed locations along the circumference of an oval or round airflow prevention device. Locate the pressure taps at a distance from the indoor unit inlet equal to 0.5 times the square root of the cross sectional area of the indoor unit inlet. This location must be between the damper and the inlet of the indoor unit, if a damper is used. Make a manifold that connects the four static pressure taps using one of the configurations shown in Figure 9 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3). Insulate the ductwork with thermal insulation that has a nominal overall resistance (R-value) of at least 19 hr·ft 2· °F/Btu.

2.5.2 Test Set-Up on the Inlet Side of the Indoor Unit: for Cases Where No Airflow Prevention Device is Installed

If using the section 2.4.2 inlet plenum and a grid of dry bulb temperature sensors, mount the grid at a location upstream of the static pressure taps described in section 2.4.2 of this appendix, preferably at the entrance plane of the inlet plenum. If the section 2.4.2 inlet plenum is not used (i.e. for non-ducted units) locate a grid approximately 6 inches upstream of the indoor unit inlet. In the case of a system having multiple non-ducted indoor units, do this for each indoor unit. Position an air sampling device, or the sensor used to measure the water vapor content of the inlet air, immediately upstream of the (each) entering air dry-bulb temperature sensor grid. If a grid of sensors is not used, position the entering air sampling device (or the sensor used to measure the water vapor content of the inlet air) as if the grid were present.

2.5.3 Indoor Coil Static Pressure Difference Measurement

Fabricate pressure taps meeting all requirements described in section 6.5.2 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3) and illustrated in Figure 2A of AMCA 210-2007 (incorporated by reference, see § 430.3), however, if adhering strictly to the description in section 6.5.2 of ANSI/ASHRAE 37-2009, the minimum pressure tap length of 2.5 times the inner diameter of Figure 2A of AMCA 210-2007 is waived. Use a differential pressure measuring instrument that is accurate to within ±0.01 inches of water and has a resolution of at least 0.01 inches of water to measure the static pressure difference between the indoor coil air inlet and outlet. Connect one side of the differential pressure instrument to the manifolded pressure taps installed in the outlet plenum. Connect the other side of the instrument to the manifolded pressure taps located in either the inlet plenum or incorporated within the airflow prevention device. For non-ducted systems that are tested with multiple outlet plenums, measure the static pressure within each outlet plenum relative to the surrounding atmosphere.

2.5.4 Test Set-Up on the Outlet Side of the Indoor Coil

a. Install an interconnecting duct between the outlet plenum described in section 2.4.1 of this appendix and the airflow measuring apparatus described below in section 2.6 of this appendix. The cross-sectional flow area of the interconnecting duct must be equal to or greater than the flow area of the outlet plenum or the common duct used when testing non-ducted units having multiple indoor coils. If needed, use adaptor plates or transition duct sections to allow the connections. To minimize leakage, tape joints within the interconnecting duct (and the outlet plenum). Construct or insulate the entire flow section with thermal insulation having a nominal overall resistance (R-value) of at least 19 hr·ft 2· °F/Btu.

b. Install a grid(s) of dry-bulb temperature sensors inside the interconnecting duct. Also, install an air sampling device, or the sensor(s) used to measure the water vapor content of the outlet air, inside the interconnecting duct. Locate the dry-bulb temperature grid(s) upstream of the air sampling device (or the in-duct sensor(s) used to measure the water vapor content of the outlet air). Turn off the sampler fan motor during the cyclic tests. Air leaving an indoor unit that is sampled by an air sampling device for remote water-vapor-content measurement must be returned to the interconnecting duct at a location:

(1) Downstream of the air sampling device;

(2) On the same side of the outlet air damper as the air sampling device; and

(3) Upstream of the section 2.6 airflow measuring apparatus.

2.5.4.1 Outlet Air Damper Box Placement and Requirements

If using an outlet air damper box (see section 2.5 of this appendix), the leakage rate from the combination of the outlet plenum, the closed damper, and the duct section that connects these two components must not exceed 20 cubic feet per minute when a negative pressure of 1 inch of water column is maintained at the plenum's inlet.

2.5.4.2 Procedures to Minimize Temperature Maldistribution

Use these procedures if necessary to correct temperature maldistributions. Install a mixing device(s) upstream of the outlet air, dry-bulb temperature grid (but downstream of the outlet plenum static pressure taps). Use a perforated screen located between the mixing device and the dry-bulb temperature grid, with a maximum open area of 40 percent. One or both items should help to meet the maximum outlet air temperature distribution specified in section 3.1.8 of this appendix. Mixing devices are described in sections 5.3.2 and 5.3.3 of ANSI/ASHRAE 41.1-2013 and section 5.2.2 of ASHRAE 41.2-1987 (RA 1992) (incorporated by reference, see § 430.3).

2.5.4.3 Minimizing Air Leakage

For small-duct, high-velocity systems, install an air damper near the end of the interconnecting duct, just prior to the transition to the airflow measuring apparatus of section 2.6 of this appendix. To minimize air leakage, adjust this damper such that the pressure in the receiving chamber of the airflow measuring apparatus is no more than 0.5 inch of water higher than the surrounding test room ambient. If applicable, in lieu of installing a separate damper, use the outlet air damper box of sections 2.5 and 2.5.4.1 of this appendix if it allows variable positioning. Also apply these steps to any conventional indoor blower unit that creates a static pressure within the receiving chamber of the airflow measuring apparatus that exceeds the test room ambient pressure by more than 0.5 inches of water column.

2.5.5 Dry Bulb Temperature Measurement

a. Measure dry bulb temperatures as specified in sections 4, 5.3, 6, and 7 of ANSI/ASHRAE 41.1-2013 (incorporated by reference, see § 430.3).

b. Distribute the sensors of a dry-bulb temperature grid over the entire flow area. The required minimum is 9 sensors per grid.

2.5.6 Water Vapor Content Measurement

Determine water vapor content by measuring dry-bulb temperature combined with the air wet-bulb temperature, dew point temperature, or relative humidity. If used, construct and apply wet-bulb temperature sensors as specified in sections 4, 5, 6, 7.2, 7.3, and 7.4 of ASHRAE 41.6-2014 (incorporated by reference, see § 430.3). The temperature sensor (wick removed) must be accurate to within ±0.2 °F. If used, apply dew point hygrometers as specified in sections 4, 5, 6, 7.1, and 7.4 of ASHRAE 41.6-2014. The dew point hygrometers must be accurate to within ±0.4 °F when operated at conditions that result in the evaluation of dew points above 35 °F. If used, a relative humidity (RH) meter must be accurate to within ±0.7% RH. Other means to determine the psychrometric state of air may be used as long as the measurement accuracy is equivalent to or better than the accuracy achieved from using a wet-bulb temperature sensor that meets the above specifications.

2.5.7 Air Damper Box Performance Requirements

If used (see section 2.5 of this appendix), the air damper box(es) must be capable of being completely opened or completely closed within 10 seconds for each action.

2.6 Airflow Measuring Apparatus

a. Fabricate and operate an airflow measuring apparatus as specified in section 6.2 and 6.3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3). Place the static pressure taps and position the diffusion baffle (settling means) relative to the chamber inlet as indicated in Figure 12 of AMCA 210-07 and/or Figure 14 of ASHRAE 41.2-1987 (RA 1992) (incorporated by reference, see § 430.3). When measuring the static pressure difference across nozzles and/or velocity pressure at nozzle throats using electronic pressure transducers and a data acquisition system, if high frequency fluctuations cause measurement variations to exceed the test tolerance limits specified in section 9.2 and Table 2 of ANSI/ASHRAE 37-2009, dampen the measurement system such that the time constant associated with response to a step change in measurement (time for the response to change 63% of the way from the initial output to the final output) is no longer than five seconds.

b. Connect the airflow measuring apparatus to the interconnecting duct section described in section 2.5.4 of this appendix. See sections 6.1.1, 6.1.2, and 6.1.4, and Figures 1, 2, and 4 of ANSI/ASHRAE 37-2009; and Figures D1, D2, and D4 of AHRI 210/240-2008 (incorporated by reference, see § 430.3) with Addendum 1 and 2 for illustrative examples of how the test apparatus may be applied within a complete laboratory set-up. Instead of following one of these examples, an alternative set-up may be used to handle the air leaving the airflow measuring apparatus and to supply properly conditioned air to the test unit's inlet. The alternative set-up, however, must not interfere with the prescribed means for measuring airflow rate, inlet and outlet air temperatures, inlet and outlet water vapor contents, and external static pressures, nor create abnormal conditions surrounding the test unit. (Note: Do not use an enclosure as described in section 6.1.3 of ANSI/ASHRAE 37-2009 when testing triple-split units.)

2.7 Electrical Voltage Supply

Perform all tests at the voltage specified in section 6.1.3.2 of AHRI 210/240-2008 (incorporated by reference, see § 430.3) for “Standard Rating Tests.” If either the indoor or the outdoor unit has a 208V or 200V nameplate voltage and the other unit has a 230V nameplate rating, select the voltage supply on the outdoor unit for testing. Otherwise, supply each unit with its own nameplate voltage. Measure the supply voltage at the terminals on the test unit using a volt meter that provides a reading that is accurate to within ±1.0 percent of the measured quantity.

2.8 Electrical Power and Energy Measurements

a. Use an integrating power (watt-hour) measuring system to determine the electrical energy or average electrical power supplied to all components of the air conditioner or heat pump (including auxiliary components such as controls, transformers, crankcase heater, integral condensate pump on non-ducted indoor units, etc.). The watt-hour measuring system must give readings that are accurate to within ±0.5 percent. For cyclic tests, this accuracy is required during both the ON and OFF cycles. Use either two different scales on the same watt-hour meter or two separate watt-hour meters. Activate the scale or meter having the lower power rating within 15 seconds after beginning an OFF cycle. Activate the scale or meter having the higher power rating within 15 seconds prior to beginning an ON cycle. For ducted blower coil systems, the ON cycle lasts from compressor ON to indoor blower OFF. For ducted coil-only systems, the ON cycle lasts from compressor ON to compressor OFF. For non-ducted units, the ON cycle lasts from indoor blower ON to indoor blower OFF. When testing air conditioners and heat pumps having a variable-speed compressor, avoid using an induction watt/watt-hour meter.

b. When performing section 3.5 and/or 3.8 cyclic tests on non-ducted units, provide instrumentation to determine the average electrical power consumption of the indoor blower motor to within ±1.0 percent. If required according to sections 3.3, 3.4, 3.7, 3.9.1 of this appendix, and/or 3.10 of this appendix, this same instrumentation requirement (to determine the average electrical power consumption of the indoor blower motor to within ±1.0 percent) applies when testing air conditioners and heat pumps having a variable-speed constant-air-volume-rate indoor blower or a variable-speed, variable-air-volume-rate indoor blower.

2.9 Time Measurements

Make elapsed time measurements using an instrument that yields readings accurate to within ±0.2 percent.

2.10 Test Apparatus for the Secondary Space Conditioning Capacity Measurement

For all tests, use the indoor air enthalpy method to measure the unit's capacity. This method uses the test set-up specified in sections 2.4 to 2.6 of this appendix. In addition, for all steady-state tests, conduct a second, independent measurement of capacity as described in section 3.1.1 of this appendix. For split systems, use one of the following secondary measurement methods: outdoor air enthalpy method, compressor calibration method, or refrigerant enthalpy method. For single-package units, use either the outdoor air enthalpy method or the compressor calibration method as the secondary measurement.

2.10.1 Outdoor Air Enthalpy Method

a. To make a secondary measurement of indoor space conditioning capacity using the outdoor air enthalpy method, do the following:

(1) Measure the electrical power consumption of the test unit;

(2) Measure the air-side capacity at the outdoor coil; and

(3) Apply a heat balance on the refrigerant cycle.

b. The test apparatus required for the outdoor air enthalpy method is a subset of the apparatus used for the indoor air enthalpy method. Required apparatus includes the following:

(1) On the outlet side, an outlet plenum containing static pressure taps (sections 2.4, 2.4.1, and 2.5.3 of this appendix),

(2) An airflow measuring apparatus (section 2.6 of this appendix),

(3) A duct section that connects these two components and itself contains the instrumentation for measuring the dry-bulb temperature and water vapor content of the air leaving the outdoor coil (sections 2.5.4, 2.5.5, and 2.5.6 of this appendix), and

(4) On the inlet side, a sampling device and temperature grid (section 2.11.b of this appendix).

c. During the free outdoor air tests described in sections 3.11.1 and 3.11.1.1 of this appendix, measure the evaporator and condenser temperatures or pressures. On both the outdoor coil and the indoor coil, solder a thermocouple onto a return bend located at or near the midpoint of each coil or at points not affected by vapor superheat or liquid subcooling. Alternatively, if the test unit is not sensitive to the refrigerant charge, install pressure gages to the access valves or to ports created from tapping into the suction and discharge lines according to sections 7.4.2 and 8.2.5 of ANSI/ASHRAE 37-2009. Use this alternative approach when testing a unit charged with a zeotropic refrigerant having a temperature glide in excess of 1 °F at the specified test conditions.

2.10.2 Compressor Calibration Method

Measure refrigerant pressures and temperatures to determine the evaporator superheat and the enthalpy of the refrigerant that enters and exits the indoor coil. Determine refrigerant flow rate or, when the superheat of the refrigerant leaving the evaporator is less than 5 °F, total capacity from separate calibration tests conducted under identical operating conditions. When using this method, install instrumentation and measure refrigerant properties according to section 7.4.2 and 8.2.5 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3). If removing the refrigerant before applying refrigerant lines and subsequently recharging, use the steps in 7.4.2 of ANSI/ASHRAE 37-2009 in addition to the methods of section 2.2.5 of this appendix to confirm the refrigerant charge. Use refrigerant temperature and pressure measuring instruments that meet the specifications given in sections 5.1.1 and 5.2 of ANSI/ASHRAE 37-2009.

2.10.3 Refrigerant Enthalpy Method

For this method, calculate space conditioning capacity by determining the refrigerant enthalpy change for the indoor coil and directly measuring the refrigerant flow rate. Use section 7.5.2 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3) for the requirements for this method, including the additional instrumentation requirements, and information on placing the flow meter and a sight glass. Use refrigerant temperature, pressure, and flow measuring instruments that meet the specifications given in sections 5.1.1, 5.2, and 5.5.1 of ANSI/ASHRAE 37-2009. Refrigerant flow measurement device(s), if used, must be either elevated at least two feet from the test chamber floor or placed upon insulating material having a total thermal resistance of at least R-12 and extending at least one foot laterally beyond each side of the device(s)' exposed surfaces.

2.11 Measurement of Test Room Ambient Conditions

Follow instructions for setting up air sampling device and aspirating psychrometer as described in section 2.14 of this appendix, unless otherwise instructed in this section.

a. If using a test set-up where air is ducted directly from the conditioning apparatus to the indoor coil inlet (see Figure 2, Loop Air-Enthalpy Test Method Arrangement, of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3)), add instrumentation to permit measurement of the indoor test room dry-bulb temperature.

b. On the outdoor side, use one of the following two approaches, except that approach (1) is required for all evaporatively cooled units and units that transfer condensate to the outdoor unit for evaporation using condenser heat.

(1) Use sampling tree air collection on all air-inlet surfaces of the outdoor unit.

(2) Use sampling tree air collection on one or more faces of the outdoor unit and demonstrate air temperature uniformity as follows. Install a grid of evenly distributed thermocouples on each air-permitting face on the inlet of the outdoor unit. Install the thermocouples on the air sampling device, locate them individually or attach them to a wire structure. If not installed on the air sampling device, install the thermocouple grid 6 to 24 inches from the unit. Evenly space the thermocouples across the coil inlet surface and install them to avoid sampling of discharge air or blockage of air recirculation. The grid of thermocouples must provide at least 16 measuring points per face or one measurement per square foot of inlet face area, whichever is less. Construct this grid and use as per section 5.3 of ANSI/ASHRAE 41.1-2013 (incorporated by reference, see § 430.3). The maximum difference between the average temperatures measured during the test period of any two pairs of these individual thermocouples located at any of the faces of the inlet of the outdoor unit, must not exceed 2.0 °F, otherwise use approach (1).

Locate the air sampling devices at the geometric center of each side; the branches may be oriented either parallel or perpendicular to the longer edges of the air inlet area. Size the air sampling devices in the outdoor air inlet location such that they cover at least 75% of the face area of the side of the coil that they are measuring.

Review air distribution at the test facility point of supply to the unit and remediate as necessary prior to the beginning of testing. Mixing fans can be used to ensure adequate air distribution in the test room. If used, orient mixing fans such that they are pointed away from the air intake so that the mixing fan exhaust does not affect the outdoor coil air volume rate. Particular attention should be given to prevent the mixing fans from affecting (enhancing or limiting) recirculation of condenser fan exhaust air back through the unit. Any fan used to enhance test room air mixing shall not cause air velocities in the vicinity of the test unit to exceed 500 feet per minute.

The air sampling device may be larger than the face area of the side being measured. Take care, however, to prevent discharge air from being sampled. If an air sampling device dimension extends beyond the inlet area of the unit, block holes in the air sampling device to prevent sampling of discharge air. Holes can be blocked to reduce the region of coverage of the intake holes both in the direction of the trunk axis or perpendicular to the trunk axis. For intake hole region reduction in the direction of the trunk axis, block holes of one or more adjacent pairs of branches (the branches of a pair connect opposite each other at the same trunk location) at either the outlet end or the closed end of the trunk. For intake hole region reduction perpendicular to the trunk axis, block off the same number of holes on each branch on both sides of the trunk.

Connect a maximum of four (4) air sampling devices to each aspirating psychrometer. In order to proportionately divide the flow stream for multiple air sampling devices for a given aspirating psychrometer, the tubing or conduit conveying sampled air to the psychrometer must be of equivalent lengths for each air sampling device. Preferentially, the air sampling device should be hard connected to the aspirating psychrometer, but if space constraints do not allow this, the assembly shall have a means of allowing a flexible tube to connect the air sampling device to the aspirating psychrometer. Insulate and route the tubing or conduit to prevent heat transfer to the air stream. Insulate any surface of the air conveying tubing in contact with surrounding air at a different temperature than the sampled air with thermal insulation with a nominal thermal resistance (R-value) of at least 19 hr • ft 2 • °F/Btu. Alternatively the conduit may have lower thermal resistance if additional sensor(s) are used to measure dry bulb temperature at the outlet of each air sampling device. No part of the air sampling device or the tubing conducting the sampled air to the sensors may be within two inches of the test chamber floor.

Take pairs of measurements (e.g. dry bulb temperature and wet bulb temperature) used to determine water vapor content of sampled air in the same location.

2.12 Measurement of Indoor Blower Speed

When required, measure fan speed using a revolution counter, tachometer, or stroboscope that gives readings accurate to within ±1.0 percent.

2.13 Measurement of Barometric Pressure

Determine the average barometric pressure during each test. Use an instrument that meets the requirements specified in section 5.2 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3).

2.14 Air Sampling Device and Aspirating Psychrometer Requirements

Make air temperature measurements in accordance with ANSI/ASHRAE 41.1-2013 (incorporated by reference, see § 430.3), unless otherwise instructed in this section.

2.14.1 Air Sampling Device Requirements

The air sampling device is intended to draw in a sample of the air at the critical locations of a unit under test. Construct the device from stainless steel, plastic or other suitable, durable materials. It shall have a main flow trunk tube with a series of branch tubes connected to the trunk tube. Holes must be on the side of the sampler facing the upstream direction of the air source. Use other sizes and rectangular shapes, and scale them accordingly with the following guidelines:

1. Minimum hole density of 6 holes per square foot of area to be sampled.

2. Sampler branch tube pitch (spacing) of 6 ± 3 in.

3. Manifold trunk to branch diameter ratio having a minimum of 3:1 ratio.

4. Distribute hole pitch (spacing) equally over the branch ( 1/2 pitch from the closed end to the nearest hole).

5. Maximum individual hole to branch diameter ratio of 1:2 (1:3 preferred).

The minimum average velocity through the air sampling device holes must be 2.5 ft/s as determined by evaluating the sum of the open area of the holes as compared to the flow area in the aspirating psychrometer.

2.14.2 Aspirating Psychrometer

The psychrometer consists of a flow section and a fan to draw air through the flow section and measures an average value of the sampled air stream. At a minimum, the flow section shall have a means for measuring the dry bulb temperature (typically, a resistance temperature device (RTD) and a means for measuring the humidity (RTD with wetted sock, chilled mirror hygrometer, or relative humidity sensor). The aspirating psychrometer shall include a fan that either can be adjusted manually or automatically to maintain required velocity across the sensors.

Construct the psychrometer using suitable material which may be plastic (such as polycarbonate), aluminum or other metallic materials. Construct all psychrometers for a given system being tested, using the same material. Design the psychrometers such that radiant heat from the motor (for driving the fan that draws sampled air through the psychrometer) does not affect sensor measurements. For aspirating psychrometers, velocity across the wet bulb sensor must be 1000 ± 200 ft/min. For all other psychrometers, velocity must be as specified by the sensor manufacturer.

3 Testing Procedures 3.1 General Requirements

If, during the testing process, an equipment set-up adjustment is made that would have altered the performance of the unit during any already completed test, then repeat all tests affected by the adjustment. For cyclic tests, instead of maintaining an air volume rate, for each airflow nozzle, maintain the static pressure difference or velocity pressure during an ON period at the same pressure difference or velocity pressure as measured during the steady-state test conducted at the same test conditions.

Use the testing procedures in this section to collect the data used for calculating

(1) Performance metrics for central air conditioners and heat pumps during the cooling season;

(2) Performance metrics for heat pumps during the heating season; and

(3) Power consumption metric(s) for central air conditioners and heat pumps during the off mode season(s).

3.1.1 Primary and Secondary Test Methods

For all tests, use the indoor air enthalpy method test apparatus to determine the unit's space conditioning capacity. The procedure and data collected, however, differ slightly depending upon whether the test is a steady-state test, a cyclic test, or a frost accumulation test. The following sections described these differences. For full-capacity cooling-mode test and (for a heat pump) the full-capacity heating-mode test, use one of the acceptable secondary methods specified in section 2.10 of this appendix to determine indoor space conditioning capacity. Calculate this secondary check of capacity according to section 3.11 of this appendix. The two capacity measurements must agree to within 6 percent to constitute a valid test. For this capacity comparison, use the Indoor Air Enthalpy Method capacity that is calculated in section 7.3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3) (and, if testing a coil-only system, compare capacities before making the after-test fan heat adjustments described in section 3.3, 3.4, 3.7, and 3.10 of this appendix). However, include the appropriate section 3.3 to 3.5 and 3.7 to 3.10 fan heat adjustments within the indoor air enthalpy method capacities used for the section 4 seasonal calculations of this appendix.

3.1.2 Manufacturer-Provided Equipment Overrides

Where needed, the manufacturer must provide a means for overriding the controls of the test unit so that the compressor(s) operates at the specified speed or capacity and the indoor blower operates at the specified speed or delivers the specified air volume rate. For variable-speed non-communicating coil-only air conditioners and heat pumps, the control system shall be provided with a control signal indicating operation at high or low stage, rather than testing with the compressor speed fixed at specific speeds, with the exception that compressor speed override may be used for heating mode test H12.

3.1.3 Airflow Through the Outdoor Coil

For all tests, meet the requirements given in section 6.1.3.4 of AHRI 210/240-2008 (incorporated by reference, see § 430.3) when obtaining the airflow through the outdoor coil.

3.1.3.1 Double-Ducted

For products intended to be installed with the outdoor airflow ducted, install the unit with outdoor coil ductwork installed per manufacturer installation instructions. The unit must operate between 0.10 and 0.15 in H2O external static pressure. Make external static pressure measurements in accordance with ANSI/ASHRAE 37-2009 section 6.4 and 6.5.

3.1.4 Airflow Through the Indoor Coil

Determine airflow setting(s) before testing begins. Unless otherwise specified within this or its subsections, make no changes to the airflow setting(s) after initiation of testing.

3.1.4.1 Cooling Full-Load Air Volume Rate 3.1.4.1.1 Cooling Full-Load Air Volume Rate for Ducted Units

Identify the certified Cooling full-load air volume rate and certified instructions for setting fan speed or controls. If there is no certified Cooling full-load air volume rate, use a value equal to the certified cooling capacity of the unit times 400 scfm per 12,000 Btu/h. If there are no instructions for setting fan speed or controls, use the as-shipped settings. Use the following procedure to confirm and, if necessary, adjust the Cooling full-load air volume rate and the fan speed or control settings to meet each test procedure requirement:

a. For all ducted blower-coil systems, except those having a constant-air-volume-rate indoor blower:

Step (1) Operate the unit under conditions specified for the A test (for single-stage units) or A2 test (for non-single-stage units) using the certified fan speed or controls settings, and adjust the exhaust fan of the airflow measuring apparatus to achieve the certified cooling full-load air volume rate;

Step (2) Measure the external static pressure;

Step (3) If this external static pressure is equal to or greater than the applicable minimum external static pressure cited in Table 4 to this appendix, the pressure requirement is satisfied; proceed to step 7 of this section. If this external static pressure is not equal to or greater than the applicable minimum external static pressure cited in Table 4, proceed to step 4 of this section;

Step (4) Increase the external static pressure by adjusting the exhaust fan of the airflow measuring apparatus until the first to occur of:

(i) The applicable Table 4 to this appendix minimum is equaled or

(ii) The measured air volume rate equals 90 percent or less of the cooling full-load air volume rate;

Step (5) If the conditions of step 4 (i) of this section occur first, the pressure requirement is satisfied; proceed to step 7 of this section. If the conditions of step 4 (ii) of this section occur first, proceed to step 6 of this section;

Step (6) Make an incremental change to the setup of the indoor blower (e.g., next highest fan motor pin setting, next highest fan motor speed) and repeat the evaluation process beginning at step 1 of this section. If the indoor blower setup cannot be further changed, increase the external static pressure by adjusting the exhaust fan of the airflow measuring apparatus until the applicable Table 4 to this appendix minimum is equaled; proceed to step 7 of this section;

Step (7) The airflow constraints have been satisfied. Use the measured air volume rate as the cooling full-load air volume rate. Use the final indoor fan speed or control settings of the unit under test for all tests that use the cooling full-load air volume rate. Adjust the fan of the airflow measurement apparatus if needed to obtain the same full-load air volume rate (in scfm) for all such tests, unless the system modulates indoor blower speed with outdoor dry bulb temperature or to adjust the sensible to total cooling capacity ratio—in this case, use an air volume rate that represents a normal installation and calculate the target external static pressure as described in section 3.1.4.2 of this appendix.

b. For ducted blower-coil systems with a constant-air-volume-rate indoor blower. For all tests that specify the cooling full-load air volume rate, obtain an external static pressure as close to (but not less than) the applicable Table 4 to this appendix value that does not cause either automatic shutdown of the indoor blower or a value of air volume rate variation QVar, defined as follows, that is greater than 10 percent.

Where: Qmax = maximum measured airflow value Qmin = minimum measured airflow value QVar = airflow variance, percent

Additional test steps as described in section 3.3.f of this appendix are required if the measured external static pressure exceeds the target value by more than 0.03 inches of water.

c. For coil-only indoor units. For the A or A2 Test, (exclusively), the pressure drop across the indoor coil assembly must not exceed 0.30 inches of water. If this pressure drop is exceeded, reduce the air volume rate until the measured pressure drop equals the specified maximum. Use this reduced air volume rate for all tests that require the Cooling full-load air volume rate.

Table 4—Minimum External Static Pressure for Ducted Blower Coil Systems

Product variety Minimum
external
static pressure
(in. wc.)
Conventional (i.e., all central air conditioners and heat pumps not otherwise listed in this table)0.50 Ceiling-mount and Wall-mount0.30 Mobile Home0.30 Low Static0.10 Mid Static0.30 Small Duct, High Velocity1.15 Space-constrained0.30

1 For ducted units tested without an air filter installed, increase the applicable tabular value by 0.08 inches of water.

2 See section 1.2, Definitions, to determine for which Table 4 product variety and associated minimum external static pressure requirement equipment qualifies.

3 If a closed-loop, air-enthalpy test apparatus is used on the indoor side, limit the resistance to airflow on the inlet side of the indoor blower coil to a maximum value of 0.1 inch of water.

d. For ducted systems having multiple indoor blowers within a single indoor section, obtain the full-load air volume rate with all indoor blowers operating unless prevented by the controls of the unit. In such cases, turn on the maximum number of indoor blowers permitted by the unit's controls. Where more than one option exists for meeting this “on” indoor blower requirement, which indoor blower(s) are turned on must match that specified in the certification report. Conduct section 3.1.4.1.1 setup steps for each indoor blower separately. If two or more indoor blowers are connected to a common duct as per section 2.4.1 of this appendix, temporarily divert their air volume to the test room when confirming or adjusting the setup configuration of individual indoor blowers. The allocation of the system's full-load air volume rate assigned to each “on” indoor blower must match that specified by the manufacturer in the certification report.

3.1.4.1.2 Cooling Full-Load Air Volume Rate for Non-Ducted Units

For non-ducted units, the Cooling full-load air volume rate is the air volume rate that results during each test when the unit is operated at an external static pressure of zero inches of water.

3.1.4.2 Cooling Minimum Air Volume Rate

Identify the certified cooling minimum air volume rate and certified instructions for setting fan speed or controls. If there is no certified cooling minimum air volume rate, use the final indoor blower control settings as determined when setting the cooling full-load air volume rate, and readjust the exhaust fan of the airflow measuring apparatus if necessary to reset to the cooling full load air volume obtained in section 3.1.4.1 of this appendix. Otherwise, calculate the target external static pressure and follow instructions a, b, c, d, or e of this section. The target external static pressure, ΔPst__i, for any test “i” with a specified air volume rate not equal to the Cooling full-load air volume rate is determined as follows:

Where: ΔPst__i = target minimum external static pressure for test i; ΔPst__full = minimum external static pressure for test A or A2 (Table 4); Qi = air volume rate for test i; and Qfull = Cooling full-load air volume rate as measured after setting and/or adjustment as described in section 3.1.4.1.1 of this appendix.

a. For a ducted blower-coil system without a constant-air-volume indoor blower, adjust for external static pressure as follows:

Step (1) Operate the unit under conditions specified for the B1 test using the certified fan speed or controls settings, and adjust the exhaust fan of the airflow measuring apparatus to achieve the certified cooling minimum air volume rate;

Step (2) Measure the external static pressure;

Step (3) If this pressure is equal to or greater than the minimum external static pressure computed in step 2 of this section, the pressure requirement is satisfied; proceed to step 7 of this section. If this pressure is not equal to or greater than the minimum external static pressure computed in step 2 of this section, proceed to step 4 of this section;

Step (4) Increase the external static pressure by adjusting the exhaust fan of the airflow measuring apparatus until either:

(i) The pressure is equal to the target minimum external static pressure, ΔPst_i, computed in step 1 of this section; or

(ii) The measured air volume rate equals 90 percent or less of the cooling minimum air volume rate, whichever occurs first;

Step (5) If the conditions of step 4 (i) of this section occur first, the pressure requirement is satisfied; proceed to step 7 of this section. If the conditions of step 4 (ii) of this section occur first, proceed to step 6 of this section;

Step (6) Make an incremental change to the setup of the indoor blower (e.g., next highest fan motor pin setting, next highest fan motor speed) and repeat the evaluation process beginning at step 1 of this section. If the indoor blower setup cannot be further changed, increase the external static pressure by adjusting the exhaust fan of the airflow measuring apparatus until it equals the minimum external static pressure computed in step 2 of this section; proceed to step 7 of this section;

Step (7) The airflow constraints have been satisfied. Use the measured air volume rate as the cooling minimum air volume rate. Use the final indoor fan speed or control settings of the unit under test for all tests that use the cooling minimum air volume rate. Adjust the fan of the airflow measurement apparatus if needed to obtain the same cooling minimum air volume rate (in scfm) for all such tests, unless the system modulates the indoor blower speed with outdoor dry bulb temperature or to adjust the sensible to total cooling capacity ratio—in this case, use an air volume rate that represents a normal installation and calculate the target minimum external static pressure as described in this section.

b. For ducted units with constant-air-volume indoor blowers, conduct all tests that specify the cooling minimum air volume rate—(i.e., the A1, B1, C1, F1, and G1 Tests)—at an external static pressure that does not cause either an automatic shutdown of the indoor blower or a value of air volume rate variation QVar, defined in section 3.1.4.1.1.b of this appendix, that is greater than 10 percent, while being as close to, but not less than the target minimum external static pressure. Additional test steps as described in section 3.3.f of this appendix are required if the measured external static pressure exceeds the target value by more than 0.03 inches of water.

c. For ducted two-capacity coil-only systems, the cooling minimum air volume rate is the higher of—

(1) The rate specified by the installation instructions included with the unit by the manufacturer; or

(2) 75 percent of the cooling full-load air volume rate. During the laboratory tests on a coil-only (fanless) system, obtain this cooling minimum air volume rate regardless of the pressure drop across the indoor coil assembly.

d. For non-ducted units, the cooling minimum air volume rate is the air volume rate that results during each test when the unit operates at an external static pressure of zero inches of water and at the indoor blower setting used at low compressor capacity (two-capacity system) or minimum compressor speed (variable-speed system). For units having a single-speed compressor and a variable-speed variable-air-volume-rate indoor blower, use the lowest fan setting allowed for cooling.

e. For ducted systems having multiple indoor blowers within a single indoor section, operate the indoor blowers such that the lowest air volume rate allowed by the unit's controls is obtained when operating the lone single-speed compressor or when operating at low compressor capacity while meeting the requirements of section 2.2.3.2 of this appendix for the minimum number of blowers that must be turned off. Using the target external static pressure and the certified air volume rates, follow the procedures described in section 3.1.4.2.a of this appendix if the indoor blowers are not constant-air-volume indoor blowers or as described in section 3.1.4.2.b of this appendix if the indoor blowers are not constant-air-volume indoor blowers. The sum of the individual “on” indoor blowers' air volume rates is the cooling minimum air volume rate for the system.

f. For ducted variable-speed compressor systems tested with a coil-only indoor unit, the cooling minimum air volume rate is the higher of:

(1) The rate specified by the installation instructions included with the unit by the manufacturer; or

(2) 75 percent of the cooling full-load air volume rate. During the laboratory tests on a coil-only (fanless) system, obtain this cooling minimum air volume rate regardless of the pressure drop across the indoor coil assembly.

3.1.4.3 Cooling Intermediate Air Volume Rate

Identify the certified cooling intermediate air volume rate and certified instructions for setting fan speed or controls. If there is no certified cooling intermediate air volume rate, use the final indoor blower control settings as determined when setting the cooling full load air volume rate, and readjust the exhaust fan of the airflow measuring apparatus if necessary to reset to the cooling full load air volume obtained in section 3.1.4.1 of this appendix. Otherwise, calculate target minimum external static pressure as described in section 3.1.4.2 of this appendix, and set the air volume rate as follows.

a. For a ducted blower coil system without a constant-air-volume indoor blower, adjust for external static pressure as described in section 3.1.4.2.a of this appendix for cooling minimum air volume rate.

b. For a ducted blower-coil system with a constant-air-volume indoor blower, conduct the EV Test at an external static pressure that does not cause either an automatic shutdown of the indoor blower or a value of air volume rate variation QVar, defined in section 3.1.4.1.1.b of this appendix, that is greater than 10 percent, while being as close to, but not less than the target minimum external static pressure. Additional test steps as described in section 3.3.f of this appendix are required if the measured external static pressure exceeds the target value by more than 0.03 inches of water.

c. For non-ducted units, the cooling intermediate air volume rate is the air volume rate that results when the unit operates at an external static pressure of zero inches of water and at the fan speed selected by the controls of the unit for the EV Test conditions.

d. For ducted variable-speed compressor systems tested with a coil-only indoor unit, use the cooling minimum air volume rate as determined in section 3.1.4.2(f) of this appendix, without regard to the pressure drop across the indoor coil assembly.

3.1.4.4 Heating Full-Load Air Volume Rate 3.1.4.4.1 Ducted Heat Pumps Where the Heating and Cooling Full-Load Air Volume Rates Are the Same

a. Use the Cooling full-load air volume rate as the heating full-load air volume rate for:

(1) Ducted blower coil system heat pumps that do not have a constant-air-volume indoor blower, and that operate at the same airflow-control setting during both the A (or A2) and the H1 (or H12) Tests;

(2) Ducted blower coil system heat pumps with constant-air-flow indoor blowers that provide the same airflow for the A (or A2) and the H1 (or H12) Tests; and

(3) Ducted heat pumps that are tested with a coil-only indoor unit (except two-capacity northern heat pumps that are tested only at low capacity cooling—see section 3.1.4.4.2 of this appendix).

b. For heat pumps that meet the above criteria “1” and “3,” no minimum requirements apply to the measured external or internal, respectively, static pressure. Use the final indoor blower control settings as determined when setting the Cooling full-load air volume rate, and readjust the exhaust fan of the airflow measuring apparatus if necessary to reset to the cooling full-load air volume obtained in section 3.1.4.1 of this appendix. For heat pumps that meet the above criterion “2,” test at an external static pressure that does not cause an automatic shutdown of the indoor blower or air volume rate variation QVar, defined in section 3.1.4.1.1.b of this appendix, greater than 10 percent, while being as close to, but not less than, the same Table 4 minimum external static pressure as was specified for the A (or A2) cooling mode test. Additional test steps as described in section 3.9.1.c of this appendix are required if the measured external static pressure exceeds the target value by more than 0.03 inches of water.

3.1.4.4.2 Ducted Heat Pumps Where the Heating and Cooling Full-Load Air Volume Rates Are Different Due to Changes in Indoor Blower Operation, i.e. Speed Adjustment by the System Controls

Identify the certified heating full-load air volume rate and certified instructions for setting fan speed or controls. If there is no certified heating full-load air volume rate, use the final indoor blower control settings as determined when setting the cooling full-load air volume rate, and readjust the exhaust fan of the airflow measuring apparatus if necessary to reset to the cooling full-load air volume obtained in section 3.1.4.1 of this appendix. Otherwise, calculate the target minimum external static pressure as described in section 3.1.4.2 of this appendix and set the air volume rate as follows.

a. For ducted blower coil system heat pumps that do not have a constant-air-volume indoor blower, adjust for external static pressure as described in section 3.1.4.2.a of this appendix for cooling minimum air volume rate.

b. For ducted heat pumps tested with constant-air-volume indoor blowers installed, conduct all tests that specify the heating full-load air volume rate at an external static pressure that does not cause an automatic shutdown of the indoor blower or air volume rate variation QVar, defined in section 3.1.4.1.1.b of this appendix, greater than 10 percent, while being as close to, but not less than the target minimum external static pressure. Additional test steps as described in section 3.9.1.c of this appendix are required if the measured external static pressure exceeds the target value by more than 0.03 inches of water.

c. When testing ducted, two-capacity blower coil system northern heat pumps (see section 1.2 of this appendix, Definitions), use the appropriate approach of the above two cases. For coil-only system northern heat pumps, the heating full-load air volume rate is the lesser of the rate specified by the manufacturer in the installation instructions included with the unit or 133 percent of the cooling full-load air volume rate. For this latter case, obtain the heating full-load air volume rate regardless of the pressure drop across the indoor coil assembly.

d. For ducted systems having multiple indoor blowers within a single indoor section, obtain the heating full-load air volume rate using the same “on” indoor blowers as used for the Cooling full-load air volume rate. Using the target external static pressure and the certified air volume rates, follow the procedures as described in section 3.1.4.4.2.a of this appendix if the indoor blowers are not constant-air-volume indoor blowers or as described in section 3.1.4.4.2.b of this appendix if the indoor blowers are constant-air-volume indoor blowers. The sum of the individual “on” indoor blowers' air volume rates is the heating full-load air volume rate for the system.

3.1.4.4.3 Ducted Heating-Only Heat Pumps

Identify the certified heating full-load air volume rate and certified instructions for setting fan speed or controls. If there is no certified heating full-load air volume rate, use a value equal to the certified heating capacity of the unit times 400 scfm per 12,000 Btu/h. If there are no instructions for setting fan speed or controls, use the as-shipped settings.

a. For all ducted heating-only blower-coil system heat pumps, except those having a constant-air-volume-rate indoor blower: conduct the following steps only during the first test, the H1 or H12 test:

Step (1) Adjust the exhaust fan of the airflow measuring apparatus to achieve the certified heating full-load air volume rate.

Step (2) Measure the external static pressure.

Step (3) If this pressure is equal to or greater than the Table 4 to this appendix minimum external static pressure that applies given the heating-only heat pump's rated heating capacity, the pressure requirement is satisfied; proceed to step 7 of this section. If this pressure is not equal to or greater than the applicable Table 4 minimum external static pressure, proceed to step 4 of this section;

Step (4) Increase the external static pressure by adjusting the exhaust fan of the airflow measuring apparatus until either:

(i) The pressure is equal to the applicable Table 4 to this appendix minimum external static pressure; or

(ii) The measured air volume rate equals 90 percent or less of the heating full-load air volume rate, whichever occurs first;

Step (5) If the conditions of step 4 (i) of this section occur first, the pressure requirement is satisfied; proceed to step 7 of this section. If the conditions of step 4 (ii) of this section occur first, proceed to step 6 of this section;

Step (6) Make an incremental change to the setup of the indoor blower (e.g., next highest fan motor pin setting, next highest fan motor speed) and repeat the evaluation process beginning at step 1 of this section. If the indoor blower setup cannot be further changed, increase the external static pressure by adjusting the exhaust fan of the airflow measuring apparatus until it equals the applicable Table 4 to this appendix minimum external static pressure; proceed to step 7 of this section;

Step (7) The airflow constraints have been satisfied. Use the measured air volume rate as the heating full-load air volume rate. Use the final indoor fan speed or control settings of the unit under test for all tests that use the heating full-load air volume rate. Adjust the fan of the airflow measurement apparatus if needed to obtain the same heating full-load air volume rate (in scfm) for all such tests, unless the system modulates indoor blower speed with outdoor dry bulb temperature—in this case, use an air volume rate that represents a normal installation and calculate the target minimum external static pressure as described in section 3.1.4.2 of this appendix.

b. For ducted heating-only blower coil system heat pumps having a constant-air-volume-rate indoor blower. For all tests that specify the heating full-load air volume rate, obtain an external static pressure that does not cause an automatic shutdown of the indoor blower or air volume rate variation QVar, defined in section 3.1.4.1.1.b of this section, greater than 10 percent, while being as close to, but not less than, the applicable Table 4 minimum. Additional test steps as described in section 3.9.1.c of this appendix are required if the measured external static pressure exceeds the target value by more than 0.03 inches of water.

c. For ducted heating-only coil-only system heat pumps in the H1 or H12 Test, (exclusively), the pressure drop across the indoor coil assembly must not exceed 0.30 inches of water. If this pressure drop is exceeded, reduce the air volume rate until the measured pressure drop equals the specified maximum. Use this reduced air volume rate for all tests that require the heating full-load air volume rate.

3.1.4.4.4 Non-Ducted Heat Pumps, Including Non-Ducted Heating-Only Heat Pumps

For non-ducted heat pumps, the heating full-load air volume rate is the air volume rate that results during each test when the unit operates at an external static pressure of zero inches of water.

3.1.4.5 Heating Minimum Air Volume Rate 3.1.4.5.1 Ducted Heat Pumps Where the Heating and Cooling Minimum Air Volume Rates are the Same

a. Use the cooling minimum air volume rate as the heating minimum air volume rate for:

(1) Ducted blower coil system heat pumps that do not have a constant-air-volume indoor blower, and that operates at the same airflow-control setting during both the A1 and the H11 tests;

(2) Ducted blower coil system heat pumps with constant-air-flow indoor blowers installed that provide the same airflow for the A1 and the H11 Tests; and

(3) Ducted coil-only system heat pumps.

b. For heat pumps that meet the above criteria “1” and “3,” no minimum requirements apply to the measured external or internal, respectively, static pressure. Use the final indoor blower control settings as determined when setting the cooling minimum air volume rate, and readjust the exhaust fan of the airflow measuring apparatus if necessary to reset to the cooling minimum air volume rate obtained in section 3.1.4.2 of this appendix. For heat pumps that meet the above criterion “2,” test at an external static pressure that does not cause an automatic shutdown of the indoor blower or air volume rate variation QVar, defined in section 3.1.4.1.1.b, greater than 10 percent, while being as close to, but not less than, the same target minimum external static pressure as was specified for the A1 cooling mode test. Additional test steps as described in section 3.9.1.c of this appendix are required if the measured external static pressure exceeds the target value by more than 0.03 inches of water.

3.1.4.5.2 Ducted Heat Pumps Where the Heating and Cooling Minimum Air Volume Rates Are Different Due to Indoor Blower Operation, i.e. Speed Adjustment by the System Controls

Identify the certified heating minimum air volume rate and certified instructions for setting fan speed or controls. If there is no certified heating minimum air volume rate, use the final indoor blower control settings as determined when setting the cooling minimum air volume rate, and readjust the exhaust fan of the airflow measuring apparatus if necessary to reset to the cooling minimum air volume obtained in section 3.1.4.2 of this appendix. Otherwise, calculate the target minimum external static pressure as described in section 3.1.4.2 of this appendix.

a. For ducted blower coil system heat pumps that do not have a constant-air-volume indoor blower, adjust for external static pressure as described in section 3.1.4.2.a of this appendix for cooling minimum air volume rate.

b. For ducted heat pumps tested with constant-air-volume indoor blowers installed, conduct all tests that specify the heating minimum air volume rate—(i.e., the H01, H11, H21, and H31 Tests)—at an external static pressure that does not cause an automatic shutdown of the indoor blower while being as close to, but not less than the air volume rate variation QVar, defined in section 3.1.4.1.1.b of this appendix, greater than 10 percent, while being as close to, but not less than the target minimum external static pressure. Additional test steps as described in section 3.9.1.c of this appendix are required if the measured external static pressure exceeds the target value by more than 0.03 inches of water.

c. For ducted two-capacity blower coil system northern heat pumps, use the appropriate approach of the above two cases.

d. For ducted two-capacity coil-only system heat pumps, use the cooling minimum air volume rate as the heating minimum air volume rate. For ducted two-capacity coil-only system northern heat pumps, use the cooling full-load air volume rate as the heating minimum air volume rate. For ducted two-capacity heating-only coil-only system heat pumps, the heating minimum air volume rate is the higher of the rate specified by the manufacturer in the test setup instructions included with the unit or 75 percent of the heating full-load air volume rate. During the laboratory tests on a coil-only system, obtain the heating minimum air volume rate without regard to the pressure drop across the indoor coil assembly.

e. For non-ducted heat pumps, the heating minimum air volume rate is the air volume rate that results during each test when the unit operates at an external static pressure of zero inches of water and at the indoor blower setting used at low compressor capacity (two-capacity system) or minimum compressor speed (variable-speed system). For units having a single-speed compressor and a variable-speed, variable-air-volume-rate indoor blower, use the lowest fan setting allowed for heating.

f. For ducted systems with multiple indoor blowers within a single indoor section, obtain the heating minimum air volume rate using the same “on” indoor blowers as used for the cooling minimum air volume rate. Using the target external static pressure and the certified air volume rates, follow the procedures as described in section 3.1.4.5.2.a of this appendix if the indoor blowers are not constant-air-volume indoor blowers or as described in section 3.1.4.5.2.b of this appendix if the indoor blowers are constant-air-volume indoor blowers. The sum of the individual “on” indoor blowers' air volume rates is the heating full-load air volume rate for the system.

3.1.4.6 Heating Intermediate Air Volume Rate

Identify the certified heating intermediate air volume rate and certified instructions for setting fan speed or controls. If there is no certified heating intermediate air volume rate, use the final indoor blower control settings as determined when setting the heating full-load air volume rate, and readjust the exhaust fan of the airflow measuring apparatus if necessary to reset to the cooling full-load air volume obtained in section 3.1.4.2 of this appendix. Calculate the target minimum external static pressure as described in section 3.1.4.2 of this appendix.

a. For ducted blower coil system heat pumps that do not have a constant-air-volume indoor blower, adjust for external static pressure as described in section 3.1.4.2.a of this appendix for cooling minimum air volume rate.

b. For ducted heat pumps tested with constant-air-volume indoor blowers installed, conduct the H2V Test at an external static pressure that does not cause an automatic shutdown of the indoor blower or air volume rate variation QVar, defined in section 3.1.4.1.1.b of this appendix, greater than 10 percent, while being as close to, but not less than the target minimum external static pressure. Additional test steps as described in section 3.9.1.c of this appendix are required if the measured external static pressure exceeds the target value by more than 0.03 inches of water.

c. For non-ducted heat pumps, the heating intermediate air volume rate is the air volume rate that results when the heat pump operates at an external static pressure of zero inches of water and at the fan speed selected by the controls of the unit for the H2V Test conditions.

d. For ducted variable-speed compressor systems tested with a coil-only indoor unit, use the heating minimum air volume rate, which (as specified in section 3.1.4.5.1.a.(3) of this appendix) is equal to the cooling minimum air volume rate, without regard to the pressure drop across the indoor coil assembly.

3.1.4.7 Heating Nominal Air Volume Rate

The manufacturer must specify the heating nominal air volume rate and the instructions for setting fan speed or controls. Calculate target minimum external static pressure as described in section 3.1.4.2 of this appendix. Make adjustments as described in section 3.1.4.6 of this appendix for heating intermediate air volume rate so that the target minimum external static pressure is met or exceeded. For ducted variable-speed compressor systems tested with a coil-only indoor unit, use the heating full-load air volume rate as the heating nominal air volume rate.

3.1.5 Indoor Test Room Requirement When the Air Surrounding the Indoor Unit is Not Supplied From the Same Source as the Air Entering the Indoor Unit

If using a test set-up where air is ducted directly from the air reconditioning apparatus to the indoor coil inlet (see Figure 2, Loop Air-Enthalpy Test Method Arrangement, of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3)), maintain the dry bulb temperature within the test room within ±5.0 °F of the applicable sections 3.2 and 3.6 dry bulb temperature test condition for the air entering the indoor unit. Dew point must be within 2 °F of the required inlet conditions.

3.1.6 Air Volume Rate Calculations

For all steady-state tests and for frost accumulation (H2, H21, H22, H2V) tests, calculate the air volume rate through the indoor coil as specified in sections 7.7.2.1 and 7.7.2.2 of ANSI/ASHRAE 37-2009. When using the outdoor air enthalpy method, follow sections 7.7.2.1 and 7.7.2.2 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3) to calculate the air volume rate through the outdoor coil. To express air volume rates in terms of standard air, use:

Where: V s = air volume rate of standard (dry) air, (ft 3/min)da V mx = air volume rate of the air-water vapor mixture, (ft 3/min)mx vn′ = specific volume of air-water vapor mixture at the nozzle, ft 3 per lbm of the air-water vapor mixture Wn = humidity ratio at the nozzle, lbm of water vapor per lbm of dry air 0.075 = the density associated with standard (dry) air, (lbm/ft 3) vn = specific volume of the dry air portion of the mixture evaluated at the dry-bulb temperature, vapor content, and barometric pressure existing at the nozzle, ft 3 per lbm of dry air. Note:

In the first printing of ANSI/ASHRAE 37-2009, the second IP equation for Qmi should read,

3.1.7 Test Sequence

Before making test measurements used to calculate performance, operate the equipment for the “break-in” period specified in the certification report, which may not exceed 20 hours. Each compressor of the unit must undergo this “break-in” period. When testing a ducted unit (except if a heating-only heat pump), conduct the A or A2 Test first to establish the cooling full-load air volume rate. For ducted heat pumps where the heating and cooling full-load air volume rates are different, make the first heating mode test one that requires the heating full-load air volume rate. For ducted heating-only heat pumps, conduct the H1 or H12 Test first to establish the heating full-load air volume rate. When conducting a cyclic test, always conduct it immediately after the steady-state test that requires the same test conditions. For variable-speed systems, the first test using the cooling minimum air volume rate should precede the EV Test, and the first test using the heating minimum air volume rate must precede the H2V Test. The test laboratory makes all other decisions on the test sequence.

3.1.8 Requirement for the Air Temperature Distribution Leaving the Indoor Coil

For at least the first cooling mode test and the first heating mode test, monitor the temperature distribution of the air leaving the indoor coil using the grid of individual sensors described in sections 2.5 and 2.5.4 of this appendix. For the 30-minute data collection interval used to determine capacity, the maximum spread among the outlet dry bulb temperatures from any data sampling must not exceed 1.5 °F. Install the mixing devices described in section 2.5.4.2 of this appendix to minimize the temperature spread.

3.1.9 Requirement for the Air Temperature Distribution Entering the Outdoor Coil

Monitor the Temperatures of the Air Entering the Outdoor Coil Using Air Sampling Devices and/or Temperature Sensor Grids, Maintaining the Required Tolerances, if Applicable, as Described in section 2.11 of this appendix

3.1.10 Control of Auxiliary Resistive Heating Elements

Except as noted, disable heat pump resistance elements used for heating indoor air at all times, including during defrost cycles and if they are normally regulated by a heat comfort controller. For heat pumps equipped with a heat comfort controller, enable the heat pump resistance elements only during the below-described, short test. For single-speed heat pumps covered under section 3.6.1 of this appendix, the short test follows the H1 or, if conducted, the H1C Test. For two-capacity heat pumps and heat pumps covered under section 3.6.2 of this appendix, the short test follows the H12 Test. Set the heat comfort controller to provide the maximum supply air temperature. With the heat pump operating and while maintaining the heating full-load air volume rate, measure the temperature of the air leaving the indoor-side beginning 5 minutes after activating the heat comfort controller. Sample the outlet dry-bulb temperature at regular intervals that span 5 minutes or less. Collect data for 10 minutes, obtaining at least 3 samples. Calculate the average outlet temperature over the 10-minute interval, TCC.

3.2 Cooling Mode Tests for Different Types of Air Conditioners and Heat Pumps 3.2.1 Tests for a System Having a Single-Speed Compressor and Fixed Cooling Air Volume Rate

This set of tests is for single-speed-compressor units that do not have a cooling minimum air volume rate or a cooling intermediate air volume rate that is different than the cooling full load air volume rate. Conduct two steady-state wet coil tests, the A and B Tests. Use the two optional dry-coil tests, the steady-state C Test and the cyclic D Test, to determine the cooling mode cyclic degradation coefficient, CD c. If the two optional tests are conducted but yield a tested CD c that exceeds the default CD c or if the two optional tests are not conducted, assign CD c the default value of 0.25 (for outdoor units with no match) or 0.2 (for all other systems). Table 5 specifies test conditions for these four tests.

Table 5—Cooling Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed Cooling Air Volume Rate

Test description Air entering indoor
unit temperature
( °F)
Air entering outdoor
unit temperature
( °F)
Cooling air volume rate Dry bulb Wet bulb Dry bulb Wet bulb A Test—required (steady, wet coil)8067951 75Cooling full-load 2. B Test—required (steady, wet coil)8067821 65Cooling full-load 2. C Test—optional (steady, dry coil)80( 3)82Cooling full-load 2. D Test—optional (cyclic, dry coil)80( 3)82( 4).

1 The specified test condition only applies if the unit rejects condensate to the outdoor coil.

2 Defined in section 3.1.4.1 of this appendix.

3 The entering air must have a low enough moisture content so no condensate forms on the indoor coil. (It is recommended that an indoor wet-bulb temperature of 57 °F or less be used.)

4 Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity pressure as measured during the C Test.

3.2.2 Tests for a Unit Having a Single-Speed Compressor Where the Indoor Section Uses a Single Variable-Speed Variable-Air-Volume Rate Indoor Blower or Multiple Indoor Blowers 3.2.2.1 Indoor Blower Capacity Modulation That Correlates With the Outdoor Dry Bulb Temperature or Systems With a Single Indoor Coil but Multiple Indoor Blowers

Conduct four steady-state wet coil tests: The A2, A1, B2, and B1 tests. Use the two optional dry-coil tests, the steady-state C1 test and the cyclic D1 test, to determine the cooling mode cyclic degradation coefficient, CD c. If the two optional tests are conducted but yield a tested CD c that exceeds the default CD c or if the two optional tests are not conducted, assign CD c the default value of 0.2.

3.2.2.2 Indoor Blower Capacity Modulation Based on Adjusting the Sensible to Total (S/T) Cooling Capacity Ratio

The testing requirements are the same as specified in section 3.2.1 of this appendix and Table 5. Use a cooling full-load air volume rate that represents a normal installation. If performed, conduct the steady-state C Test and the cyclic D Test with the unit operating in the same S/T capacity control mode as used for the B Test.

Table 6—Cooling Mode Test Conditions for Units With a Single-Speed Compressor That Meet the Section 3.2.2.1 Indoor Unit Requirements

Test description Air entering indoor
unit temperature
( °F)
Air entering outdoor
unit temperature
( °F)
Cooling air volume rate Dry bulb Wet bulb Dry bulb Wet bulb A2 Test—required (steady, wet coil)8067951 75Cooling full-load 2. A1 Test—required (steady, wet coil)8067951 75Cooling minimum 3. B2 Test—required (steady, wet coil)8067821 65Cooling full-load 2. B1 Test—required (steady, wet coil)8067821 65Cooling minimum 3. C1 Test 4—optional (steady, dry coil)80( 4)82Cooling minimum 3. D1 Test 4—optional (cyclic, dry coil)80( 4)82( 5).

1 The specified test condition only applies if the unit rejects condensate to the outdoor coil.

2 Defined in section 3.1.4.1 of this appendix.

3 Defined in section 3.1.4.2 of this appendix.

4 The entering air must have a low enough moisture content so no condensate forms on the indoor coil. (It is recommended that an indoor wet-bulb temperature of 57 °F or less be used.)

5 Maintain the airflow nozzles static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity pressure as measured during the C1 Test.

3.2.3 Tests for a Unit Having a Two-Capacity Compressor. (See Section 1.2 of This Appendix, Definitions)

a. Conduct four steady-state wet coil tests: the A2, B2, B1, and F1 Tests. Use the two optional dry-coil tests, the steady-state C1 Test and the cyclic D1 Test, to determine the cooling-mode cyclic-degradation coefficient, CD c. If the two optional tests are conducted but yield a tested CD c that exceeds the default CD c or if the two optional tests are not conducted, assign CD c the default value of 0.2. Table 7 specifies test conditions for these six tests.

b. For units having a variable-speed indoor blower that is modulated to adjust the sensible to total (S/T) cooling capacity ratio, use cooling full-load and cooling minimum air volume rates that represent a normal installation. Additionally, if conducting the dry-coil tests, operate the unit in the same S/T capacity control mode as used for the B1 Test.

c. Test two-capacity, northern heat pumps (see section 1.2 of this appendix, Definitions) in the same way as a single speed heat pump with the unit operating exclusively at low compressor capacity (see section 3.2.1 of this appendix and Table 5).

d. If a two-capacity air conditioner or heat pump locks out low-capacity operation at higher outdoor temperatures, then use the two dry-coil tests, the steady-state C2 Test and the cyclic D2 Test, to determine the cooling-mode cyclic-degradation coefficient that only applies to on/off cycling from high capacity, CD c(k=2). If the two optional tests are conducted but yield a tested CD c(k = 2) that exceeds the default CD c(k = 2) or if the two optional tests are not conducted, assign CD c(k = 2) the default value. The default CD c(k=2) is the same value as determined or assigned for the low-capacity cyclic-degradation coefficient, CD c [or equivalently, CD c(k=1)].

Table 7—Cooling Mode Test Conditions for Units Having a Two-Capacity Compressor

Test description Air entering indoor
unit temperature
( °F)
Air entering outdoor
unit temperature
( °F)
Compressor capacity Cooling air volume rate Dry bulb Wet bulb Dry bulb Wet bulb A2 Test—required (steady, wet coil)8067951 75HighCooling Full-Load. 2B2 Test—required (steady, wet coil)8067821 65HighCooling Full-Load. 2B1 Test—required (steady, wet coil)8067821 65LowCooling Minimum. 3C2 Test—optional (steady, dry-coil)80( 4)82HighCooling Full-Load. 2D2 Test—optional (cyclic, dry-coil)80( 4)82High( 5). C1 Test—optional (steady, dry-coil)80( 4)82LowCooling Minimum. 3D1 Test—optional (cyclic, dry-coil)80( 4)82Low( 6). F1 Test—required (steady, wet coil)8067671 53.5LowCooling Minimum. 3

1 The specified test condition only applies if the unit rejects condensate to the outdoor coil.

2 Defined in section 3.1.4.1 of this appendix.

3 Defined in section 3.1.4.2 of this appendix.

4 The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air wet-bulb temperature of 57 °F or less.

5 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the C2 Test.

6 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the C1 Test.

3.2.4 Tests for a Unit Having a Variable-Speed Compressor

a. Conduct five steady-state wet coil tests: the A2, EV, B2, B1, and F1 Tests (the EV test is not applicable for variable speed non-communicating coil-only air conditioners and heat pumps). Use the two optional dry-coil tests, the steady-state G1 Test and the cyclic I1 Test, to determine the cooling mode cyclic degradation coefficient, CD c. If the two optional tests are conducted and yield a tested CD c that exceeds the default CD c or if the two optional tests are not conducted, assign CD c the default value of 0.25. Table 8 specifies test conditions for these seven tests. The compressor shall operate at the same cooling full speed, measured by RPM or power input frequency (Hz), for both the A2 and B2 tests. The compressor shall operate at the same cooling minimum speed, measured by RPM or power input frequency (Hz), for the B1, F1, G1, and I1 tests. Determine the cooling intermediate compressor speed cited in Table 8 to this appendix, as required, using:

Where a tolerance of plus 5 percent or the next higher inverter frequency step from that calculated is allowed.

b. For units that modulate the indoor blower speed to adjust the sensible to total (S/T) cooling capacity ratio, use cooling full-load, cooling intermediate, and cooling minimum air volume rates that represent a normal installation. Additionally, if conducting the dry-coil tests, operate the unit in the same S/T capacity control mode as used for the F1 Test.

c. For multiple-split air conditioners and heat pumps (except where noted), the following procedures supersede the above requirements: For all Table 8 tests specified for a minimum compressor speed, turn off at least one indoor unit. The manufacturer shall designate the particular indoor unit(s) that is turned off. The manufacturer must also specify the compressor speed used for the Table 8 EV Test, a cooling-mode intermediate compressor speed that falls within 1/4 and 3/4 of the difference between the full and minimum cooling-mode speeds. The manufacturer should prescribe an intermediate speed that is expected to yield the highest EER for the given EV Test conditions and bracketed compressor speed range. The manufacturer can designate that one or more indoor units are turned off for the EV Test.

d. For variable-speed non-communicating coil-only air conditioners and heat pumps, the manufacturer-provided equipment overrides for full and minimum compressor speed described in section 3.1.2 of this appendix shall be limited to two stages of digital on/off control.

Table 8—Cooling Mode Test Condition for Units Having a Variable-Speed Compressor

Test description Air entering indoor unit
temperature ( °F)
Air entering outdoor unit
temperature ( °F)
Compressor speed Cooling air volume rate Dry bulb Wet bulb Dry bulb Wet bulb A2 Test—required (steady, wet coil)806795175Cooling FullCooling Full-Load. 2B2 Test—required (steady, wet coil)806782165Cooling FullCooling Full-Load. 2EV Test—required 7 (steady, wet coil)806787169Cooling IntermediateCooling Intermediate. 3B1 Test—required (steady, wet coil)806782165Cooling MinimumCooling Minimum. 4F1 Test—required (steady, wet coil)806767153.5Cooling MinimumCooling Minimum. 4G1 Test 5—optional (steady, dry-coil)80( 6)67Cooling MinimumCooling Minimum. 4I1 Test 5—optional (cyclic, dry-coil)80( 6)67Cooling Minimum( 6)

1 The specified test condition only applies if the unit rejects condensate to the outdoor coil.

2 Defined in section 3.1.4.1 of this appendix.

3 Defined in section 3.1.4.3 of this appendix.

4 Defined in section 3.1.4.2 of this appendix.

5 The entering air must have a low enough moisture content so no condensate forms on the indoor coil. DOE recommends using an indoor air wet bulb temperature of 57 °F or less.

6 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure difference or velocity pressure as measured during the G1 Test.

7 The EV test is not applicable for variable-speed non-communicating coil-only air conditioners and heat pumps.

3.2.5 Cooling Mode Tests for Northern Heat Pumps With Triple-Capacity Compressors

Test triple-capacity, northern heat pumps for the cooling mode in the same way as specified in section 3.2.3 of this appendix for units having a two-capacity compressor.

3.2.6 Tests for an Air Conditioner or Heat Pump Having a Single Indoor Unit Having Multiple Indoor Blowers and Offering Two Stages of Compressor Modulation

Conduct the cooling mode tests specified in section 3.2.3 of this appendix.

3.3 Test Procedures for Steady-State Wet Coil Cooling Mode Tests (the A, A2, A1, B, B2, B1, EV, and F1 Tests)

a. For the pretest interval, operate the test room reconditioning apparatus and the unit to be tested until maintaining equilibrium conditions for at least 30 minutes at the specified section 3.2 test conditions. Use the exhaust fan of the airflow measuring apparatus and, if installed, the indoor blower of the test unit to obtain and then maintain the indoor air volume rate and/or external static pressure specified for the particular test. Continuously record (see section 1.2 of this appendix, Definitions):

(1) The dry-bulb temperature of the air entering the indoor coil,

(2) The water vapor content of the air entering the indoor coil,

(3) The dry-bulb temperature of the air entering the outdoor coil, and

(4) For the section 2.2.4 of this appendix cases where its control is required, the water vapor content of the air entering the outdoor coil.

Refer to section 3.11 of this appendix for additional requirements that depend on the selected secondary test method.

b. After satisfying the pretest equilibrium requirements, make the measurements specified in Table 3 of ANSI/ASHRAE 37-2009 for the indoor air enthalpy method and the user-selected secondary method. Make said Table 3 measurements at equal intervals that span 5 minutes or less. Continue data sampling until reaching a 30-minute period (e.g., seven consecutive 5-minute samples) where the test tolerances specified in Table 9 are satisfied. For those continuously recorded parameters, use the entire data set from the 30-minute interval to evaluate Table 9 compliance. Determine the average electrical power consumption of the air conditioner or heat pump over the same 30-minute interval.

c. Calculate indoor-side total cooling capacity and sensible cooling capacity as specified in sections 7.3.3.1 and 7.3.3.3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3). To calculate capacity, use the averages of the measurements (e.g. inlet and outlet dry bulb and wet bulb temperatures measured at the psychrometers) that are continuously recorded for the same 30-minute interval used as described above to evaluate compliance with test tolerances. Do not adjust the parameters used in calculating capacity for the permitted variations in test conditions. Evaluate air enthalpies based on the measured barometric pressure. Use the values of the specific heat of air given in section 7.3.3.1 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3) for calculation of the sensible cooling capacities. Assign the average total space cooling capacity, average sensible cooling capacity, and electrical power consumption over the 30-minute data collection interval to the variables Q c k(T), Q sc k(T) and E c k(T), respectively. For these three variables, replace the “T” with the nominal outdoor temperature at which the test was conducted. The superscript k is used only when testing multi-capacity units. Use the superscript k=2 to denote a test with the unit operating at high capacity or full speed, k=1 to denote low capacity or minimum speed, and k=v to denote the intermediate speed.

d. For mobile home and space-constrained ducted coil-only system tests,

(1) For two-stage or variable-speed systems, for all steady-state wet coil tests (i.e., the A1, A2, B1, B2, EV, and F1 tests), decrease by the quantity calculated in Equation 3.3-1 to this appendix and increase by the quantity calculated in Equation 3.3-2 to this appendix.

Where: DFPCMHSC is the default fan power coefficient (watts) for mobile-home and space-constrained systems, And %FLAVR is the air volume rate used for the test, expressed as a percentage of the cooling full load air volume rate. For all tests specifying the full-load air volume rate (e.g., the A2 and B2 tests), set %FLAVR to 100%. For tests that specify the cooling minimum air volume rate or cooling intermediate air volume rate (i.e., the A1, B1, EV, and F1 tests) and for which the specified minimum or intermediate air volume rate is greater than or equal to 75 percent of the cooling full-load air volume rate and less than the cooling full-load air volume rate, set %FLAVR to the ratio of the specified air volume rate and the cooling full-load air volume rate, expressed as a percentage.

(2) For single-stage systems, for all steady-state wet coil tests (i.e., the A and B tests), decrease Qc k(T) by the quantity calculated in Equation 3.3-3 to this appendix and increase E c k(T) by the quantity calculated in Equation 3.3-4 to this appendix.

Where V S is the average measured indoor air volume rate expressed in units of cubic feet per minute of standard air (scfm).

e. For non-mobile, non-space-constrained home ducted coil-only system tests,

(1) For two-stage or variable-speed systems, for all steady-state wet coil tests (i.e., the A1, A2, B1, B2, EV, and F1 tests), decrease Qc k(T) by the quantity calculated in Equation 3.3-5 to this appendix and increase E c k(T) by the quantity calculated in Equation 3.3-6 to this appendix.

Where: DFPCC is the default fan power coefficient (watts) for non-mobile-home and non-space-constrained systems,

And %FLAVR is the air volume rate used for the test, expressed as a percentage of the cooling full load air volume rate. For all tests specifying the full-load air volume rate (e.g., the A2 and B2 tests), set %FLAVR to 100%. For tests that specify the cooling minimum air volume rate or cooling intermediate air volume rate (i.e., the A1, B1, EV, and F1 tests) and for which the specified minimum or intermediate air volume rate is greater than or equal to 75 percent of the cooling full-load air volume rate and less than the cooling full-load air volume rate, set %FLAVR to the ratio of the specified air volume rate and the cooling full-load air volume rate, expressed as a percentage.

(2) For single-stage systems, for all steady-state wet coil tests (i.e., the A and B tests), decrease Qc k(T) by the quantity calculated in Equation 3.3-7 to this appendix and increase E c k(T) by the quantity calculated in Equation 3.3-8 to this appendix.

Where is the average measured indoor air volume rate expressed in units of cubic feet per minute of standard air (scfm).

Table 9—Test Operating and Test Condition Tolerances for Section 3.3 Steady-State Wet Coil Cooling Mode Tests and Section 3.4 Dry Coil Cooling Mode Tests

Test operating
tolerance 1
Test condition
tolerance 1
Indoor dry-bulb, °F Entering temperature2.00.5 Leaving temperature2.0 Indoor wet-bulb, °F Entering temperature1.02 0.3 Leaving temperature2 1.0 Outdoor dry-bulb, °F Entering temperature2.00.5 Leaving temperature3 2.0 Outdoor wet-bulb, °F Entering temperature1.04 0.3 Leaving temperature3 1.0 External resistance to airflow, inches of water0.055 0.02 Electrical voltage, % of reading2.01.5 Nozzle pressure drop, % of reading2.0

1 See section 1.2 of this appendix, Definitions.

2 Only applies during wet coil tests; does not apply during steady-state, dry coil cooling mode tests.

3 Only applies when using the outdoor air enthalpy method.

4 Only applies during wet coil cooling mode tests where the unit rejects condensate to the outdoor coil.

5 Only applies when testing non-ducted units.

f. For air conditioners and heat pumps having a constant-air-volume-rate indoor blower, the five additional steps listed below are required if the average of the measured external static pressures exceeds the applicable sections 3.1.4 minimum (or target) external static pressure (ΔPmin) by 0.03 inches of water or more.

(1) Measure the average power consumption of the indoor blower motor (E fan,1) and record the corresponding external static pressure (ΔP1) during or immediately following the 30-minute interval used for determining capacity.

(2) After completing the 30-minute interval and while maintaining the same test conditions, adjust the exhaust fan of the airflow measuring apparatus until the external static pressure increases to approximately ΔP1 + (ΔP1 − ΔPmin).

(3) After re-establishing steady readings of the fan motor power and external static pressure, determine average values for the indoor blower power (E fan,2) and the external static pressure (ΔP2) by making measurements over a 5-minute interval.

(4) Approximate the average power consumption of the indoor blower motor at ΔPmin using linear extrapolation:

(5) Increase the total space cooling capacity, Q c k(T), by the quantity (E fan,1 − E fan,min), when expressed on a Btu/h basis. Decrease the total electrical power, E c k(T), by the same fan power difference, now expressed in watts.

3.4 Test Procedures for the Steady-State Dry-Coil Cooling-Mode Tests (the C, C1, C2, and G1 Tests)

a. Except for the modifications noted in this section, conduct the steady-state dry coil cooling mode tests as specified in section 3.3 of this appendix for wet coil tests. Prior to recording data during the steady-state dry coil test, operate the unit at least one hour after achieving dry coil conditions. Drain the drain pan and plug the drain opening. Thereafter, the drain pan should remain completely dry.

b. Denote the resulting total space cooling capacity and electrical power derived from the test as Q ss,dry and E ss,dry. With regard to a section 3.3 deviation, do not adjust Q ss,dry for duct losses (i.e., do not apply section 7.3.3.3 of ANSI/ASHRAE 37-2009). In preparing for the section 3.5 cyclic tests of this appendix, record the average indoor-side air volume rate, V , specific heat of the air, Cp,a (expressed on dry air basis), specific volume of the air at the nozzles, v′n, humidity ratio at the nozzles, Wn, and either pressure difference or velocity pressure for the flow nozzles. For units having a variable-speed indoor blower (that provides either a constant or variable air volume rate) that will or may be tested during the cyclic dry coil cooling mode test with the indoor blower turned off (see section 3.5 of this appendix), include the electrical power used by the indoor blower motor among the recorded parameters from the 30-minute test.

c. If the temperature sensors used to provide the primary measurement of the indoor-side dry bulb temperature difference during the steady-state dry-coil test and the subsequent cyclic dry-coil test are different, include measurements of the latter sensors among the regularly sampled data. Beginning at the start of the 30-minute data collection period, measure and compute the indoor-side air dry-bulb temperature difference using both sets of instrumentation, ΔT (Set SS) and ΔT (Set CYC), for each equally spaced data sample. If using a consistent data sampling rate that is less than 1 minute, calculate and record minutely averages for the two temperature differences. If using a consistent sampling rate of one minute or more, calculate and record the two temperature differences from each data sample. After having recorded the seventh (i=7) set of temperature differences, calculate the following ratio using the first seven sets of values:

Each time a subsequent set of temperature differences is recorded (if sampling more frequently than every 5 minutes), calculate FCD using the most recent seven sets of values. Continue these calculations until the 30-minute period is completed or until a value for FCD is calculated that falls outside the allowable range of 0.94-1.06. If the latter occurs, immediately suspend the test and identify the cause for the disparity in the two temperature difference measurements. Recalibration of one or both sets of instrumentation may be required. If all the values for FCD are within the allowable range, save the final value of the ratio from the 30-minute test as FCD*. If the temperature sensors used to provide the primary measurement of the indoor-side dry bulb temperature difference during the steady-state dry-coil test and the subsequent cyclic dry-coil test are the same, set FCD*= 1. 3.5 Test Procedures for the Cyclic Dry-Coil Cooling-Mode Tests (the D, D1, D2, and I1 Tests)

After completing the steady-state dry-coil test, remove the outdoor air enthalpy method test apparatus, if connected, and begin manual OFF/ON cycling of the unit's compressor. The test set-up should otherwise be identical to the set-up used during the steady-state dry coil test. When testing heat pumps, leave the reversing valve during the compressor OFF cycles in the same position as used for the compressor ON cycles, unless automatically changed by the controls of the unit. For units having a variable-speed indoor blower, the manufacturer has the option of electing at the outset whether to conduct the cyclic test with the indoor blower enabled or disabled. Always revert to testing with the indoor blower disabled if cyclic testing with the fan enabled is unsuccessful.

a. For all cyclic tests, the measured capacity must be adjusted for the thermal mass stored in devices and connections located between measured points. Follow the procedure outlined in section 7.4.3.4.5 of ASHRAE 116-2010 (incorporated by reference, see § 430.3) to ensure any required measurements are taken.

b. For units having a single-speed or two-capacity compressor, cycle the compressor OFF for 24 minutes and then ON for 6 minutes (Δτcyc,dry = 0.5 hours). For units having a variable-speed compressor, cycle the compressor OFF for 48 minutes and then ON for 12 minutes (Δτcyc,dry = 1.0 hours). Repeat the OFF/ON compressor cycling pattern until the test is completed. Allow the controls of the unit to regulate cycling of the outdoor fan. If an upturned duct is used, measure the dry-bulb temperature at the inlet of the device at least once every minute and ensure that its test operating tolerance is within 1.0 °F for each compressor OFF period.

c. Sections 3.5.1 and 3.5.2 of this appendix specify airflow requirements through the indoor coil of ducted and non-ducted indoor units, respectively. In all cases, use the exhaust fan of the airflow measuring apparatus (covered under section 2.6 of this appendix) along with the indoor blower of the unit, if installed and operating, to approximate a step response in the indoor coil airflow. Regulate the exhaust fan to quickly obtain and then maintain the flow nozzle static pressure difference or velocity pressure at the same value as was measured during the steady-state dry coil test. The pressure difference or velocity pressure should be within 2 percent of the value from the steady-state dry coil test within 15 seconds after airflow initiation. For units having a variable-speed indoor blower that ramps when cycling on and/or off, use the exhaust fan of the airflow measuring apparatus to impose a step response that begins at the initiation of ramp up and ends at the termination of ramp down.

d. For units having a variable-speed indoor blower, conduct the cyclic dry coil test using the pull-thru approach described below if any of the following occur when testing with the fan operating:

(1) The test unit automatically cycles off;

(2) Its blower motor reverses; or

(3) The unit operates for more than 30 seconds at an external static pressure that is 0.1 inches of water or more higher than the value measured during the prior steady-state test.

For the pull-thru approach, disable the indoor blower and use the exhaust fan of the airflow measuring apparatus to generate the specified flow nozzles static pressure difference or velocity pressure. If the exhaust fan cannot deliver the required pressure difference because of resistance created by the unpowered indoor blower, temporarily remove the indoor blower.

e. Conduct three complete compressor OFF/ON cycles with the test tolerances given in Table 10 satisfied. Calculate the degradation coefficient CD for each complete cycle. If all three CD values are within 0.02 of the average CD then stability has been achieved, use the highest CD value of these three. If stability has not been achieved, conduct additional cycles, up to a maximum of eight cycles, until stability has been achieved between three consecutive cycles. Once stability has been achieved, use the highest CD value of the three consecutive cycles that establish stability. If stability has not been achieved after eight cycles, use the highest CD from cycle one through cycle eight, or the default CD, whichever is lower.

f. With regard to the Table 10 parameters, continuously record the dry-bulb temperature of the air entering the indoor and outdoor coils during periods when air flows through the respective coils. Sample the water vapor content of the indoor coil inlet air at least every 2 minutes during periods when air flows through the coil. Record external static pressure and the air volume rate indicator (either nozzle pressure difference or velocity pressure) at least every minute during the interval that air flows through the indoor coil. (These regular measurements of the airflow rate indicator are in addition to the required measurement at 15 seconds after flow initiation.) Sample the electrical voltage at least every 2 minutes beginning 30 seconds after compressor start-up. Continue until the compressor, the outdoor fan, and the indoor blower (if it is installed and operating) cycle off.

g. For ducted units, continuously record the dry-bulb temperature of the air entering (as noted above) and leaving the indoor coil. Or if using a thermopile, continuously record the difference between these two temperatures during the interval that air flows through the indoor coil. For non-ducted units, make the same dry-bulb temperature measurements beginning when the compressor cycles on and ending when indoor coil airflow ceases.

h. Integrate the electrical power over complete cycles of length Δτcyc,dry. For ducted blower coil systems tested with the unit's indoor blower operating for the cycling test, integrate electrical power from indoor blower OFF to indoor blower OFF. For all other ducted units and for non-ducted units, integrate electrical power from compressor OFF to compressor OFF. (Some cyclic tests will use the same data collection intervals to determine the electrical energy and the total space cooling. For other units, terminate data collection used to determine the electrical energy before terminating data collection used to determine total space cooling.)

Table 10—Test Operating and Test Condition Tolerances for Cyclic Dry Coil Cooling Mode Tests

Test operating tolerance 1Test condition tolerance 1Indoor entering dry-bulb temperature, 2 °F2.00.5 Indoor entering wet-bulb temperature, °F( 3) Outdoor entering dry-bulb temperature, 2 °F2.00.5 External resistance to airflow, 2 inches of water0.05Airflow nozzle pressure difference or velocity pressure, 2% of reading2.04 2.0 Electrical voltage, 5 % of reading2.01.5

1 See section 1.2 of this appendix, Definitions.

2 Applies during the interval that air flows through the indoor (outdoor) coil except for the first 30 seconds after flow initiation. For units having a variable-speed indoor blower that ramps, the tolerances listed for the external resistance to airflow apply from 30 seconds after achieving full speed until ramp down begins.

3 Shall at no time exceed a wet-bulb temperature that results in condensate forming on the indoor coil.

4 The test condition must be the average nozzle pressure difference or velocity pressure measured during the steady-state dry coil test.

5 Applies during the interval when at least one of the following—the compressor, the outdoor fan, or, if applicable, the indoor blower—are operating except for the first 30 seconds after compressor start-up.

If the Table 10 tolerances are satisfied over the complete cycle, record the measured electrical energy consumption as ecyc,dry and express it in units of watt-hours. Calculate the total space cooling delivered, qcyc,dry, in units of Btu using,

Where, V , Cp,a, vn′ (or vn), Wn, and FCD* are the values recorded during the section 3.4 dry coil steady-state test and Tal(τ) = dry bulb temperature of the air entering the indoor coil at time τ, °F. Ta2(τ) = dry bulb temperature of the air leaving the indoor coil at time τ, °F. τ1 = for ducted units, the elapsed time when airflow is initiated through the indoor coil; for non-ducted units, the elapsed time when the compressor is cycled on, hr. τ2 = the elapsed time when indoor coil airflow ceases, hr.

Adjust the total space cooling delivered, qcyc,dry, according to calculation method outlined in section 7.4.3.4.5 of ASHRAE 116-2010 (incorporated by reference, see § 430.3).

3.5.1 Procedures When Testing Ducted Systems

The automatic controls that are installed in the test unit must govern the OFF/ON cycling of the air moving equipment on the indoor side (i.e., the exhaust fan of the airflow measuring apparatus and the indoor blower of the test unit). For ducted coil-only systems rated based on using a fan time-delay relay, control the indoor coil airflow according to the OFF delay listed by the manufacturer in the certification report. For ducted units having a variable-speed indoor blower that has been disabled (and possibly removed), start and stop the indoor airflow at the same instances as if the fan were enabled. For all other ducted coil-only systems, cycle the indoor coil airflow in unison with the cycling of the compressor. If air damper boxes are used, close them on the inlet and outlet side during the OFF period. Airflow through the indoor coil should stop within 3 seconds after the automatic controls of the test unit de-energize (or if the airflow system has been disabled (and possibly removed), within 3 seconds after the automatic controls of the test unit would have de-energized) the indoor blower.

a. For mobile home and space-constrained ducted coil-only systems,

(1) For two-stage or variable-speed systems, for all cyclic dry-coil tests (i.e., the D1, D2, and I1 tests) decrease qcyc,dry by the quantity calculated in Equation 3.5-2 to this appendix and increase ecyc,dry by the quantity calculated in Equation 3.5-3 to this appendix.

Where: V S is the average indoor air volume rate from the section 3.4 dry coil steady-state test and is expressed in units of cubic feet per minute of standard air (scfm), DFPCMHSC is the default fan power coefficient (watts) for mobile-home and space-constrained systems, And %FLAVR is the air volume rate used for the test, expressed as a percentage of the cooling full load air volume rate. For all tests specifying the full-load air volume rate (e.g., the D2 test), set %FLAVR to 100%. For tests that specify the cooling minimum air volume rate or cooling intermediate air volume rate (i.e., the D1 and I1 tests) and for which the specified minimum or intermediate air volume rate is greater than or equal to 75 percent of the cooling full-load air volume rate and less than the cooling full-load air volume rate, set %FLAVR to the ratio of the specified air volume rate and the cooling full-load air volume rate, expressed as a percentage.

(2) For single-stage systems, for all cyclic dry-coil tests (i.e., the D test), decrease qcyc,dry by the quantity calculated in Equation 3.5-4 to this appendix and increase ecyc,dry by the quantity calculated in Equation 3.5-5 to this appendix.

b. For ducted, non-mobile, non-space-constrained home coil-only units,

(1) For two-stage or variable-speed systems, for all cyclic dry-coil tests (i.e., the D1, D2, and I1 tests) decrease qcyc,dry by the quantity calculated in Equation 3.5-6 to this appendix and increase ecyc,dry by the quantity calculated in Equation 3.5-7 to this appendix.

Where: V S is the average indoor air volume rate from the section 3.4 dry coil steady-state test and is expressed in units of cubic feet per minute of standard air (scfm), DFPCC is the default fan power coefficient (watts) for non-mobile-home and non-space-constrained systems, And %FLAVR is the air volume rate used for the test, expressed as a percentage of the cooling full load air volume rate. For all tests specifying the full-load air volume rate (e.g., the D2 test), set %FLAVR to 100%. For tests that specify the cooling minimum air volume rate or cooling intermediate air volume rate (i.e., the D1, and I1 tests) and for which the specified minimum or intermediate air volume rate is greater than or equal to 75 percent of the cooling full-load air volume rate and less than the cooling full-load air volume rate, set %FLAVR to the ratio of the specified air volume rate and the cooling full-load air volume rate, expressed as a percentage.

(2) For single-stage systems, for all cyclic dry-coil tests (i.e., the D test) decrease qcyc,dry by the quantity calculated in Equation 3.5-8 to this appendix and increase ecyc,dry by the quantity calculated in Equation 3.5-9 to this appendix.

c. For units having a variable-speed indoor blower that is disabled during the cyclic test, decrease qcyc,dry and increase ecyc,dry based on: The product of [τ2 − τ1] and the indoor blower power (in W) measured during or following the dry coil steady-state test; or,

d. The following algorithm if the indoor blower ramps its speed when cycling.

(1) Measure the electrical power consumed by the variable-speed indoor blower at a minimum of three operating conditions: at the speed/air volume rate/external static pressure that was measured during the steady-state test, at operating conditions associated with the midpoint of the ramp-up interval, and at conditions associated with the midpoint of the ramp-down interval. For these measurements, the tolerances on the airflow volume or the external static pressure are the same as required for the section 3.4 steady-state test.

(2) For each case, determine the fan power from measurements made over a minimum of 5 minutes.

(3) Approximate the electrical energy consumption of the indoor blower if it had operated during the cyclic test using all three power measurements. Assume a linear profile during the ramp intervals. The manufacturer must provide the durations of the ramp-up and ramp-down intervals. If the test setup instructions included with the unit by the manufacturer specifies a ramp interval that exceeds 45 seconds, use a 45-second ramp interval nonetheless when estimating the fan energy.

3.5.2 Procedures When Testing Non-Ducted Indoor Units

Do not use airflow prevention devices when conducting cyclic tests on non-ducted indoor units. Until the last OFF/ON compressor cycle, airflow through the indoor coil must cycle off and on in unison with the compressor. For the last OFF/ON compressor cycle—the one used to determine ecyc,dry and qcyc,dry—use the exhaust fan of the airflow measuring apparatus and the indoor blower of the test unit to have indoor airflow start 3 minutes prior to compressor cut-on and end three minutes after compressor cutoff. Subtract the electrical energy used by the indoor blower during the 3 minutes prior to compressor cut-on from the integrated electrical energy, ecyc,dry. Add the electrical energy used by the indoor blower during the 3 minutes after compressor cutoff to the integrated cooling capacity, qcyc,dry. For the case where the non-ducted indoor unit uses a variable-speed indoor blower which is disabled during the cyclic test, correct ecyc,dry and qcyc,dry using the same approach as prescribed in section 3.5.1 of this appendix for ducted units having a disabled variable-speed indoor blower.

3.5.3 Cooling-Mode Cyclic-Degradation Coefficient Calculation

Use the two dry-coil tests to determine the cooling-mode cyclic-degradation coefficient, CD c. Append “(k=2)” to the coefficient if it corresponds to a two-capacity unit cycling at high capacity. If the two optional tests are conducted but yield a tested CD c that exceeds the default CD c or if the two optional tests are not conducted, assign CD c the default value of 0.25 for variable-speed compressor systems and outdoor units with no match, and 0.20 for all other systems. The default value for two-capacity units cycling at high capacity, however, is the low-capacity coefficient, i.e., CD c(k=2) = CD c. Evaluate CD c using the above results and those from the section 3.4 dry-coil steady-state test.

Where: the average energy efficiency ratio during the cyclic dry coil cooling mode test, Btu/W·h the average energy efficiency ratio during the steady-state dry coil cooling mode test, Btu/W·h the cooling load factor dimensionless

Round the calculated value for CD c to the nearest 0.01. If CD c is negative, then set it equal to zero.

3.6 Heating Mode Tests for Different Types of Heat Pumps, Including Heating-Only Heat Pumps 3.6.1 Tests for a Heat Pump Having a Single-Speed Compressor and Fixed Heating Air Volume Rate

This set of tests is for single-speed-compressor heat pumps that do not have a heating minimum air volume rate or a heating intermediate air volume rate that is different than the heating full load air volume rate. Conducting a very low temperature test (H4) is optional. Conduct the optional high temperature cyclic (H1C) test to determine the heating mode cyclic-degradation coefficient, CD h. If this optional test is conducted but yields a tested CD h that exceeds the default CD h or if the optional test is not conducted, assign CD h the default value of 0.25. Test conditions for the five tests are specified in Table 11 of this section.

Table 11—Heating Mode Test Conditions for Units Having a Single-Speed Compressor and a Fixed-Speed Indoor Blower, a Constant Air Volume Rate Indoor Blower, or Coil-Only

Test description Air entering indoor unit
temperature ( °F)
Air entering outdoor unit
temperature ( °F)
Heating air volume rate Dry bulb Wet bulb Dry bulb Wet bulb H1 test (required, steady)7060 (max)4743Heating Full-Load. 1H1C test (optional, cyclic)7060 (max)4743( 2) H2 test (required)7060 (max)3533Heating Full-Load. 1H3 test (required, steady)7060 (max)1715Heating Full-Load. 1H4 test (optional, steady)7060 (max)54 (max)Heating Full-Load. 1

1 Defined in section 3.1.4.4 of this appendix.

2 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during an ON period at the same pressure or velocity as measured during the H1 test.

3.6.2 Tests for a Heat Pump Having a Single-Speed Compressor and a Single Indoor Unit Having Either (1) a Variable-Speed, Variable-Air-Rate Indoor Blower Whose Capacity Modulation Correlates With Outdoor Dry Bulb Temperature or (2) Multiple Indoor Blowers

Conduct five tests: Two high temperature tests (H12 and H11), one frost accumulation test (H22), and two low temperature tests (H32 and H31). Conducting an additional frost accumulation test (H21) and a very low temperature test (H42) is optional. Conduct the optional high temperature cyclic (H1C1) test to determine the heating mode cyclic-degradation coefficient, CD h. If this optional test is conducted but yields a tested CD h that exceeds the default CD h or if the optional test is not conducted, assign CD h the default value of 0.25. Test conditions for the seven tests are specified in Table 12. If the optional H21 test is not performed, use the following equations to approximate the capacity and electrical power of the heat pump at the H21 test conditions:

where, The quantities Q hk=2(47), E hk=2(47), Q hk=1(47), and E hk=1(47) are determined from the H12 and H11 tests and evaluated as specified in section 3.7 of this appendix; the quantities Q hk=2(35) and E hk=2(35) are determined from the H22 test and evaluated as specified in section 3.9 of this appendix; and the quantities Q hk=2(17), E hk=2(17), Q hk=1(17), and E hk=1(17), are determined from the H32 and H31 tests and evaluated as specified in section 3.10 of this appendix.

Table 12—Heating Mode Test Conditions for Units With a Single-Speed Compressor That Meet the Section 3.6.2 Indoor Unit Requirements

Test description Air entering indoor unit
temperature ( °F)
Air entering outdoor unit
temperature ( °F)
Heating air volume rate Dry bulb Wet bulb Dry bulb Wet bulb H12 test (required, steady)7060 (max)4743Heating Full-Load. 1H11 test (required, steady)7060 (max)4743Heating Minimum. 2H1C1 test (optional, cyclic)7060 (max)4743( 3) H22 test (required)7060 (max)3533Heating Full-Load. 1H21 test (optional)7060 (max)3533Heating Minimum. 2H32 test (required, steady)7060 (max)1715Heating Full-Load. 1H31 test (required, steady)7060 (max)1715Heating Minimum. 2H42 test (optional, steady)7060 (max)54 (max)Heating Full-Load. 1

1 Defined in section 3.1.4.4 of this appendix.

2 Defined in section 3.1.4.5 of this appendix.

3 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during an ON period at the same pressure or velocity as measured during the H11 test.

3.6.3 Tests for a Heat Pump Having a Two-Capacity Compressor (see Section 1.2 of This Appendix, Definitions), Including Two-Capacity, Northern Heat Pumps (see Section 1.2 of This Appendix, Definitions)

a. Conduct one maximum temperature test (H01), two high temperature tests (H12 and H11), one frost accumulation test (H22), and one low temperature test (H32). Conducting a very low temperature test (H42) is optional. Conduct an additional frost accumulation test (H21) and low temperature test (H31) if both of the following conditions exist:

(1) Knowledge of the heat pump's capacity and electrical power at low compressor capacity for outdoor temperatures of 37 °F and less is needed to complete the section 4.2.3 of this appendix seasonal performance calculations; and

(2) The heat pump's controls allow low-capacity operation at outdoor temperatures of 37 °F and less.

If the two conditions in a.(1) and a.(2) of this section are met, an alternative to conducting the H21 frost accumulation is to use the following equations to approximate the capacity and electrical power:

Determine the quantities Q hk=1 (47) and E hk=1 (47) from the H11 test and evaluate them according to section 3.7 of this appendix. Determine the quantities Q hk=1 (17) and E hk=1 (17) from the H31 test and evaluate them according to section 3.10 of this appendix.

b. Conduct the optional high temperature cyclic test (H1C1) to determine the heating mode cyclic-degradation coefficient, CD h. If this optional test is conducted but yields a tested CD h that exceeds the default CD h or if the optional test is not conducted, assign CD h the default value of 0.25. If a two-capacity heat pump locks out low capacity operation at lower outdoor temperatures, conduct the high temperature cyclic test (H1C2) to determine the high-capacity heating mode cyclic-degradation coefficient, CD h (k=2). If this optional test at high capacity is conducted but yields a tested CD h (k = 2) that exceeds the default CD h (k = 2) or if the optional test is not conducted, assign CD h the default value. The default CD h (k=2) is the same value as determined or assigned for the low-capacity cyclic-degradation coefficient, CD h [or equivalently, CD h (k=1)]. Table 13 specifies test conditions for these nine tests.

Table 13—Heating Mode Test Conditions for Units Having a Two-Capacity Compressor

Test description Air entering indoor unit
temperature ( °F)
Air entering outdoor unit
temperature ( °F)
Compressor capacity Heating air volume rate Dry bulb Wet bulb Dry bulb Wet bulb H01 test (required, steady)7060 (max)6256.5LowHeating Minimum. 1H12 test (required, steady)7060 (max)4743HighHeating Full-Load. 2H1C2 test (optional, 7 cyclic)7060 (max)4743High( 3) H11 test (required, steady)7060 (max)4743LowHeating Minimum. 1H1C1 test (optional, cyclic)7060 (max)4743Low( 4) H22 test (required)7060 (max)3533HighHeating Full-Load. 2H21 test 5 6 (required)7060 (max)3533LowHeating Minimum. 1H32 test (required, steady)7060 (max)1715HighHeating Full-Load. 2H31 test 5 (required, steady)7060 (max)1715LowHeating Minimum. 1H42 test (optional, steady)7060 (max)54 (max)HighHeating Full-Load. 2

1 Defined in section 3.1.4.5 of this appendix.

2 Defined in section 3.1.4.4 of this appendix.

3 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during an ON period at the same pressure or velocity as measured during the H12 test.

4 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during an ON period at the same pressure or velocity as measured during the H11 test.

5 Required only if the heat pump's performance when operating at low compressor capacity and outdoor temperatures less than 37 °F is needed to complete HSPF2 calculations in section 4.2.3 of this appendix.

6 If note #5 to this table applies, the equations for Q h k=1 (35) and E h k=1 (17) in section 3.6.3 of this appendix may be used in lieu of conducting the H21 test.

7 Required only if the heat pump locks out low-capacity operation at lower outdoor temperatures.

3.6.4 Tests for a Heat Pump Having a Variable-Speed Compressor 3.6.4.1 Variable-Speed Compressor Other Than Non-Communicating Coil-Only Heat Pumps

a. Conduct one maximum temperature test (H01), two high temperature tests (H1N and H11), one frost accumulation test (H2V), and one low temperature test (H32). Conducting one or more of the following tests is optional: an additional high temperature test (H12), an additional frost accumulation test (H22), and a very low temperature test (H42). Conduct the optional high temperature cyclic (H1C1) test to determine the heating mode cyclic-degradation coefficient, CD h. If this optional test is conducted and yields a tested CD h that exceeds the default CD h or if the optional test is not conducted, assign CD h the default value of 0.25. Test conditions for the nine tests are specified in Table 14A to this appendix. The compressor shall operate for the H12, H22 and H32 Tests at the same heating full speed, measured by RPM or power input frequency (Hz), as the maximum speed at which the system controls would operate the compressor in normal operation in 17 °F ambient temperature. The compressor shall operate for the H1N test at the maximum speed at which the system controls would operate the compressor in normal operation in 47 °F ambient temperature. Additionally, for a cooling/heating heat pump, the compressor shall operate for the H1N test at a speed, measured by RPM or power input frequency (Hz), no lower than the speed used in the A2 test if the tested H1N heating capacity is less than the tested A2 cooling capacity. The compressor shall operate at the same heating minimum speed, measured by RPM or power input frequency (Hz), for the H01, H1C1, and H11 Tests. Determine the heating intermediate compressor speed cited in Table 14A using the heating mode full and minimum compressors speeds and:

Where a tolerance of plus 5 percent or the next higher inverter frequency step from that calculated is allowed.

b. If one of the high temperature tests (H12 or H1N) is conducted using the same compressor speed (RPM or power input frequency) as the H32 test, set the 47 °F capacity and power input values used for calculation of HSPF2 equal to the measured values for that test:

Q k=2hcalc(47) = Q k=2h(47); E k=2hcalc(47) = E k=2h(47) Where: Q k=2hcalc(47) and E k=2hcalc(47) are the capacity and power input, respectively, representing full-speed operation at 47 °F for the HSPF2 calculations, Q k=2h(47) is the capacity measured in the high temperature test (H12 or H1N) that used the same compressor speed as the H32 test, and E k=2h(47) is the power input measured in the high temperature test (H12 or H1N) which used the same compressor speed as the H32 test.

Evaluate the quantities Q hk=2(47) and E hk=2(47) according to section 3.7 of this appendix.

Otherwise (if no high temperature test is conducted using the same speed (RPM or power input frequency) as the H32 test), calculate the 47 °F capacity and power input values used for calculation of HSPF2 as follows:

Q k=2hcalc(47) = Q k=2h(17) * (1 + 30 °F * CSF); E k=2hcalc(47) = E k=2h(17) * (1 + 30 °F * PSF); Where: Q k=2hcalc(47) and E k=2hcalc(47) are the capacity and power input, respectively, representing full-speed operation at 47 °F for the HSPF2 calculations, Q k=2h(17) is the capacity measured in the H32 test, E k=2h(17) is the power input measured in the H32 test, CSF is the capacity slope factor, equal to 0.0204/ °F for split systems and 0.0262/ °F for single-package systems, and PSF is the Power Slope Factor, equal to 0.00455/ °F.

c. If the H22 test is not done, use the following equations to approximate the capacity and electrical power at the H22 test conditions:

Q k=2h(35) = 0.90*{Q k=2h(17) + 0.6*[Q k=2hcalc(47) − Q k=2h(17)]} E k=2h(35) = 0.985*{E k=2h(17) + 0.6*[E k=2hcalc(47) − E k=2h(17)]} Where: Q k=2hcalc(47) and E k=2hcalc(47) are the capacity and power input, respectively, representing full-speed operation at 47 °F for the HSPF2 calculations, calculated as described in paragraph b. of this section, and Q k=2h(17) and E k=2h(17) are the capacity and power input measured in the H32 test.

d. Determine the quantities Q h k=2(17) and E h k=2(17) from the H32 test, determine the quantities Q h k=2(5) and E h k=2(5) from the H42 test, and evaluate all four according to section 3.10 of this appendix.

e. For multiple-split heat pumps (only), the following procedures supersede the above requirements. For all Table 14A of this appendix tests specified for a minimum compressor speed, turn off at least one indoor unit. The manufacturer shall designate the particular indoor unit(s) to be turned off. The manufacturer must also specify the compressor speed used for the Table 14A H2V test, a heating mode intermediate compressor speed that falls within 1/4 and 3/4 of the difference between the full and minimum heating mode speeds. The manufacturer should prescribe an intermediate speed that is expected to yield the highest COP for the given H2V test conditions and bracketed compressor speed range. The manufacturer can designate that one or more specific indoor units are turned off for the H2V test.

Table 14A—Heating Mode Test Conditions for Units Having a Variable-Speed Compressor Other Than Variable-Speed Non-Communicating Coil-Only Heat Pumps

Test description Air entering indoor unit
temperature ( °F)
Air entering outdoor unit
temperature ( °F)
Compressor speed Heating air volume rate Dry bulb Wet bulb Dry bulb Wet bulb H01 test (required, steady)7060 (max)6256.5Heating MinimumHeating Minimum. 1H12 test (optional, steady)7060 (max)4743Heating Full 4Heating Full-Load. 3H11 test (required, steady)7060 (max)4743Heating MinimumHeating Minimum. 1H1N test (required, steady)7060 (max)4743Heating Full 5Heating Nominal. 7H1C1 test (optional, cyclic)7060 (max)4743Heating Minimum( 2) H22 test (optional)7060 (max)3533Heating Full 4Heating Full-Load. 3H2V test (required)7060 (max)3533Heating IntermediateHeating Intermediate. 6H32 test (required, steady)7060 (max)1715Heating Full 4Heating Full-Load. 3H42 test (optional, steady)7060 (max)54 (max)Heating Full 8Heating Full-Load. 3

1 Defined in section 3.1.4.5 of this appendix.

2 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during an ON period at the same pressure or velocity as measured during the H11 test.

3 Defined in section 3.1.4.4 of this appendix.

4 Maximum speed that the system controls would operate the compressor in normal operation in 17 °F ambient temperature. The H12 test is not needed if the H1N test uses this same compressor speed.

5 Maximum speed that the system controls would operate the compressor in normal operation in 47 °F ambient temperature.

6 Defined in section 3.1.4.6 of this appendix.

7 Defined in section 3.1.4.7 of this appendix.

8 Maximum speed that the system controls would operate the compressor in normal operation at 5 °F ambient temperature.

3.6.4.2 Variable-Speed Compressor With Non-Communicating Coil-Only Heat Pumps

a. Conduct one maximum temperature test (H01), two high temperature tests (H1N and H11), two frost accumulation test (H22 and H21), and two low temperature tests (H32 and H31). Conducting one or both of the following tests is optional: an additional high temperature test (H12) and a very low temperature test (H42). Conduct the optional high temperature cyclic (H1C1) test to determine the heating mode cyclic-degradation coefficient, CD h. If this optional test is conducted and yields a tested CD h that exceeds the default CD h or if the optional test is not conducted, assign CD h the default value of 0.25. Test conditions for the ten tests are specified in Table 14B to this appendix. The compressor shall operate for the H12 and H32 tests at the same heating full speed, measured by RPM or power input frequency (Hz), as the maximum speed at which the system controls would operate the compressor in normal operation in 17 °F ambient temperature. The compressor shall operate for the H1N test at the maximum speed at which the system controls would operate the compressor in normal operation in 47 °F ambient temperature. Additionally, for a cooling/heating heat pump, the compressor shall operate for the H1N test at a speed, measured by RPM or power input frequency (Hz), no lower than the speed used in the A2 test if the tested H1N heating capacity is less than the tested A2 cooling capacity. The compressor shall operate at the same heating minimum speed, measured by RPM or power input frequency (Hz), for the H01, H1C1, and H11 tests.

b. If one of the high temperature tests (H12 or H1N) is conducted using the same compressor speed (RPM or power input frequency) as the H32 test, set the 47 °F capacity and power input values used for calculation of HSPF2 equal to the measured values for that test:

Q k=2hcalc(47) = Q k=2h(47) = E k= 2hcalc(47) = E k=2h(47) Where: Q k= 2hcalc(47) and E k= 2hcalc(47) are the capacity and power input, respectively, representing full-speed operation at 47 °F for the HSPF2 calculations, Q k=2h(47) is the capacity measured in the high temperature test (H12 or H1N) which used the same compressor speed as the H32 test, and E k=2h(47) is the power input measured in the high temperature test (H12 or H1N) which used the same compressor speed as the H32 test.

Evaluate the quantities Q h= 2(47) and E k= 2(47) according to section 3.7 of this appendix.

Otherwise (if no high temperature test is conducted using the same speed (RPM or power input frequency) as the H32 test), calculate the 47 °F capacity and power input values used for calculation of HSPF2 as follows:

Q k=2hcalc(47) = Q k=2h(17) * (1 + 30 °F CSF); and E k=2hcalc(47) = E k=2h(17) * (1 + 30 °F PSF); and Where: Q k=2hcalc and E k=2hcalc(47) are the capacity and power input, respectively, representing full-speed operation at 47 °F for the HSPF2 calculations, Q k=2h is the capacity measured in the H32 test, E k=2h(47) is the power input measured in the H32 test,

CSF is the capacity slope factor, equal to 0.0204/ °F for split systems, and

PSF is the Power Slope Factor, equal to 0.00455/ °F.

c. Determine the quantities Q k= 2h(17) and E k= 2h(5) from the H32 test, determine the quantities Q k= 2h(5) and E k= 2h(5) from the H42 test, and evaluate all four according to section 3.10 of this appendix.

Table 14B—Heating Mode Test Conditions for Variable-Speed Non-Communicating Coil-Only Heat Pumps

Test description Air entering indoor unit
temperature ( °F)
Air entering outdoor unit
temperature ( °F)
Compressor speed Heating air volume rate Dry bulb Wet bulb Dry bulb Wet bulb H01 test (required, steady)7060 (max)6256.5Heating MinimumHeating Minimum. 1H12 test (optional, steady)7060 (max)4743Heating Full 4Heating Full-Load. 3H11 test (required, steady)7060 (max)4743Heating MinimumHeating Minimum. 1H1N test (required, steady)7060 (max)4743Heating Full 5Heating Full-Load. 3H1C1 test (optional, cyclic)7060 (max)4743Heating Minimum( 2) H22 test (required)7060 (max)3533Heating Full 6Heating Full-Load. 3H21 test (required)7060 (max)3533Heating Minimum 7Heating Minimum. 1H32 test (required, steady)7060 (max)1715Heating Full 4Heating Full-Load. 3H31 test (required, steady)7060 (max)1715Heating Minimum 8Heating Minimum. 1H42 test (optional, steady)7060 (max)54 (max)Heating Full 9Heating Full-Load. 3

1 Defined in section 3.1.4.5 of this appendix.

2 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during an ON period at the same pressure or velocity as measured during the H11 test.

3 Defined in section 3.1.4.4 of this appendix.

4 Maximum speed that the system controls would operate the compressor in normal operation in 17 °F ambient temperature. The H12 test is not needed if the H1N test uses this same compressor speed.

5 Maximum speed that the system controls would operate the compressor in normal operation in 47 °F ambient temperature.

6 Maximum speed that the system controls would operate the compressor in normal operation in 35 °F ambient temperature.

7 Minimum speed that the system controls would operate the compressor in normal operation in 35 °F ambient temperature.

8 Minimum speed that the system controls would operate the compressor in normal operation in 17 °F ambient temperature.

9 Maximum speed that the system controls would operate the compressor in normal operation in 5 °F ambient temperature.

3.6.5 Additional Test for a Heat Pump Having a Heat Comfort Controller

Test any heat pump that has a heat comfort controller (see section 1.2 of this appendix, Definitions) according to section 3.6.1, 3.6.2, or 3.6.3, whichever applies, with the heat comfort controller disabled. Additionally, conduct the abbreviated test described in section 3.1.9 of this appendix with the heat comfort controller active to determine the system's maximum supply air temperature. ( Note: heat pumps having a variable-speed compressor and a heat comfort controller are not covered in the test procedure at this time.)

3.6.6 Heating Mode Tests for Northern Heat Pumps with Triple-Capacity Compressors

Test triple-capacity, northern heat pumps for the heating mode as follows:

a. Conduct one maximum temperature test (H01), two high temperature tests (H12 and H11), one frost accumulation test (H22), two low temperature tests (H32, H33), and one very low temperature test (H43). Conduct an additional frost accumulation test (H21) and low temperature test (H31) if both of the following conditions exist: (1) Knowledge of the heat pump's capacity and electrical power at low compressor capacity for outdoor temperatures of 37 °F and less is needed to complete the section 4.2.6 seasonal performance calculations; and (2) the heat pump's controls allow low capacity operation at outdoor temperatures of 37 °F and less. If the above two conditions are met, an alternative to conducting the H21 frost accumulation test to determine Q hk=1(35) and Ehk=1(35) is to use the following equations to approximate this capacity and electrical power:

In evaluating the above equations, determine the quantities Qhk=1(47) from the H11 test and evaluate them according to section 3.7 of this appendix. Determine the quantities Q hk=1(17) and E hk=1(17) from the H31 test and evaluate them according to section 3.10 of this appendix. Use the paired values of Q hk=1(35) and E hk=1(35) derived from conducting the H21 frost accumulation test and evaluated as specified in section 3.9.1 of this appendix or use the paired values calculated using the above default equations, whichever contribute to a higher Region IV HSPF2 based on the DHRmin.

b. Conducting a frost accumulation test (H23) with the heat pump operating at its booster capacity is optional. If this optional test is not conducted, determine Q hk=3(35) and E hk=3(35) using the following equations to approximate this capacity and electrical power:

Where:

Determine the quantities Q hk=2(47) and E hk=2(47) from the H12 test and evaluate them according to section 3.7 of this appendix. Determine the quantities Q hk=2(35) and E hk=2(35) from the H22 test and evaluate them according to section 3.9.1 of this appendix. Determine the quantities Q hk=2(17) and E hk=2(17) from the H32 test, determine the quantities Q hk=3(17) and E hk=3(17) from the H33 test, and determine the quantities Q hk=3(5) and E hk=3(5) from the H43 test. Evaluate all six quantities according to section 3.10 of this appendix. Use the paired values of Q hk=3(35) and E hk=3(35) derived from conducting the H23 frost accumulation test and calculated as specified in section 3.9.1 of this appendix or use the paired values calculated using the above default equations, whichever contribute to a higher Region IV HSPF2 based on the DHRmin.

c. Conduct the optional high temperature cyclic test (H1C1) to determine the heating mode cyclic-degradation coefficient, CD h. A default value for CD h of 0.25 may be used in lieu of conducting the cyclic. If a triple-capacity heat pump locks out low capacity operation at lower outdoor temperatures, conduct the high temperature cyclic test (H1C2) to determine the high capacity heating mode cyclic-degradation coefficient, CD h (k=2). The default CD h (k=2) is the same value as determined or assigned for the low-capacity cyclic-degradation coefficient, CD h [or equivalently, CD h (k=1)]. Finally, if a triple-capacity heat pump locks out both low and high capacity operation at the lowest outdoor temperatures, conduct the low temperature cyclic test (H3C3) to determine the booster-capacity heating mode cyclic-degradation coefficient, CD h (k=3). The default CD h (k=3) is the same value as determined or assigned for the high capacity cyclic-degradation coefficient, CD h [or equivalently, CD h (k=2)]. Table 15 specifies test conditions for all 13 tests.

Table 15—Heating Mode Test Conditions for Units With a Triple-Capacity Compressor

Test description Air entering indoor unit ( °F) Air entering outdoor unit ( °F) Compressor capacity Heating air volume rate Dry bulb Wet bulb Dry bulb Wet bulb H01 Test (required, steady)7060 (max)6256.5LowHeating Minimum. 1H12 (required, steady)7060 (max)4743HighHeating Full-Load. 2H1C2 Test (optional, 8 cyclic7060 (max)4743High( 3) H11 Test (required, steady)7060 (max)4743LowHeating Minimum. 1H1C1 Test (optional, cyclic)7060 (max)4743Low( 4) H23 Test (optional, steady)7060 (max)3533BoosterHeating Full-Load. 2H22 Test (required)7060 (max)3533HighHeating Full-Load. 2H21 Test (required7060 (max)3533LowHeating Minimum. 1H33 Test (required, steady)7060 (max)1715BoosterHeating Full-Load. 2H3C3 Test 5 6 (optional, cyclic)7060 (max)1715Booster( 7) H32 Test (required, steady)7060 (max)1715HighHeating Full-Load. 2H31 Test 5 (required, steady)7060 (max)1715LowHeating Minimum. 1H43 Test (required, steady)7060 (max)54 (max)BoosterHeating Full-Load. 2

1 Defined in section 3.1.4.5 of this appendix.

2 Defined in section 3.1.4.4 of this appendix.

3 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the H12 test.

4 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the H11 test.

5 Required only if the heat pump's performance when operating at low compressor capacity and outdoor temperatures less than 37 °F is needed to complete the HSPF2 calculations in section 4.2.6 of this appendix.

6 If note #5 to this table applies, the equations for Q k=1h(35) and E k=1h (17) in section 3.6.6 of this appendix may be used in lieu of conducting the H21 test.

7 Maintain the airflow nozzle(s) static pressure difference or velocity pressure during the ON period at the same pressure or velocity as measured during the H33 test.

8 Required only if the heat pump locks out low-capacity operation at lower outdoor temperatures

3.6.7 Tests for a Heat Pump Having a Single Indoor Unit Having Multiple Indoor Blowers and Offering Two Stages of Compressor Modulation. Conduct the Heating Mode Tests Specified in Section 3.6.3 of this Appendix 3.7 Test Procedures for Steady-State Maximum Temperature and High Temperature Heating Mode Tests (the H01, H1, H12, H11, and H1N tests)

a. For the pretest interval, operate the test room reconditioning apparatus and the heat pump until equilibrium conditions are maintained for at least 30 minutes at the specified section 3.6 test conditions. Use the exhaust fan of the airflow measuring apparatus and, if installed, the indoor blower of the heat pump to obtain and then maintain the indoor air volume rate and/or the external static pressure specified for the particular test. Continuously record the dry-bulb temperature of the air entering the indoor coil, and the dry-bulb temperature and water vapor content of the air entering the outdoor coil. Refer to section 3.11 of this appendix for additional requirements that depend on the selected secondary test method. After satisfying the pretest equilibrium requirements, make the measurements specified in Table 3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3) for the indoor air enthalpy method and the user-selected secondary method. Make said Table 3 measurements at equal intervals that span 5 minutes or less. Continue data sampling until a 30-minute period (e.g., seven consecutive 5-minute samples) is reached where the test tolerances specified in Table 16 are satisfied. For those continuously recorded parameters, use the entire data set for the 30-minute interval when evaluating Table 16 compliance. Determine the average electrical power consumption of the heat pump over the same 30-minute interval.

Table 16—Test Operating and Test Condition Tolerances for Section 3.7 and Section 3.10 Steady-State Heating Mode Tests

Test operating tolerance 1Test condition tolerance 1Indoor dry-bulb, °F: Entering temperature2.00.5 Leaving temperature2.0 Indoor wet-bulb, °F: Entering temperature1.0 Leaving temperature1.0 Outdoor dry-bulb, °F: Entering temperature2.00.5 Leaving temperature22.0 Outdoor wet-bulb, °F: Entering temperature1.00.3 Leaving temperature2 1.0 External resistance to airflow, inches of water0.053 0.02 Electrical voltage, % of reading2.01.5 Nozzle pressure drop, % of reading2.0

1 See section 1.2 of this appendix, Definitions.

2 Only applies when the Outdoor Air Enthalpy Method is used.

3 Only applies when testing non-ducted units.

b. Calculate indoor-side total heating capacity as specified in sections 7.3.4.1 and 7.3.4.3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3). To calculate capacity, use the averages of the measurements (e.g. inlet and outlet dry bulb temperatures measured at the psychrometers) that are continuously recorded for the same 30-minute interval used as described above to evaluate compliance with test tolerances. Do not adjust the parameters used in calculating capacity for the permitted variations in test conditions. Assign the average space heating capacity and electrical power over the 30-minute data collection interval to the variables Q h k and E h k(T) respectively. The “T” and superscripted “k” are the same as described in section 3.3 of this appendix. Additionally, for the heating mode, use the superscript to denote results from the optional H1N test, if conducted.

c. For mobile home and space-constrained ducted coil-only system tests,

(1) For two-stage or variable-speed systems, for all steady-state maximum temperature and high temperature tests (i.e., the H01, H11, H12, and H1N tests), increase Qck(T) by the quantity calculated in Equation 3.7-1 to this appendix and increase E ck(T) by the quantity calculated in Equation 3.7-2 to this appendix.

Where: DFPCMHSC is the default fan power coefficient (watts) for mobile-home and space-constrained systems, And %FLAVR is the air volume rate used for the test, expressed as a percentage of the cooling full load air volume rate. For all tests specifying the full-load air volume rate (e.g., the H12 and H1N tests), set %FLAVR to 100%. For tests that specify the heating minimum air volume rate or heating intermediate air volume rate (i.e., the H01 and H11 tests) and for which the specified minimum or intermediate air volume rate is greater than or equal to 75 percent of the cooling full-load air volume rate and less than the cooling full-load air volume rate, set %FLAVR to the ratio of the specified air volume rate and the cooling full-load air volume rate, expressed as a percentage.

(2) For single-stage systems, for all steady-state maximum temperature and high temperature tests (i.e., the H1 test), increase Qck(T) by the quantity calculated in Equation 3.7-3 to this appendix and increase Eck(T) by the quantity calculated in Equation 3.7-4 to this appendix.

Where V S is the average measured indoor air volume rate expressed in units of cubic feet per minute of standard air (scfm).

d. For non-mobile, non-space-constrained home ducted coil-only system tests,

(1) For two-stage or variable-speed systems, for all steady-state maximum temperature and high temperature tests (i.e., the H01, H11, H12, and H1N tests), increase Qck(T) by the quantity calculated in Equation 3.7-5 to this appendix and increase Eck(T) by the quantity calculated in Equation 3.7-6 to this appendix.

Where:

DFPCC is the default fan power coefficient (watts) for non-mobile-home and non-space-constrained systems,

And %FLAVR is the air volume rate used for the test, expressed as a percentage of the cooling full load air volume rate. For all tests specifying the full-load air volume rate (e.g., the H12 and H1N tests), set %FLAVR to 100%. For tests that specify the heating minimum air volume rate or heating intermediate air volume rate (i.e., the H01 and H11 tests) and for which the specified minimum or intermediate air volume rate is greater than or equal to 75 percent of the cooling full-load air volume rate and less than the cooling full-load air volume rate, set %FLAVR to the ratio of the specified air volume rate and the cooling full-load air volume rate, expressed as a percentage.

(2) For single-stage systems, for all steady-state maximum temperature and high temperature tests (i.e., the H1 test), increase Qck(T) by the quantity calculated in Equation 3.7-7 to this appendix and increase Eck(T) by the quantity calculated in Equation 3.7-8 to this appendix.

Where V S is the average measured indoor air volume rate expressed in units of cubic feet per minute of standard air (scfm).

e. If conducting the cyclic heating mode test, which is described in section 3.8 of this appendix, record the average indoor-side air volume rate, V , specific heat of the air, Cp,a (expressed on dry air basis), specific volume of the air at the nozzles, vn′ (or vn), humidity ratio at the nozzles, Wn, and either pressure difference or velocity pressure for the flow nozzles. If either or both of the below criteria apply, determine the average, steady-state, electrical power consumption of the indoor blower motor (E fan,1):

(1) The section 3.8 cyclic test will be conducted and the heat pump has a variable-speed indoor blower that is expected to be disabled during the cyclic test; or

(2) The heat pump has a (variable-speed) constant-air volume-rate indoor blower and during the steady-state test the average external static pressure (ΔP1) exceeds the applicable section 3.1.4.4 minimum (or targeted) external static pressure (ΔPmin) by 0.03 inches of water or more.

Determine E fan,1 by making measurements during the 30-minute data collection interval, or immediately following the test and prior to changing the test conditions. When the above “2” criteria applies, conduct the following four steps after determining E fan,1 (which corresponds to ΔP1):

(i) While maintaining the same test conditions, adjust the exhaust fan of the airflow measuring apparatus until the external static pressure increases to approximately ΔP1 + (ΔP1 − ΔPmin).

(ii) After re-establishing steady readings for fan motor power and external static pressure, determine average values for the indoor blower power (E fan,2) and the external static pressure (ΔP2) by making measurements over a 5-minute interval.

(iii) Approximate the average power consumption of the indoor blower motor if the 30-minute test had been conducted at ΔPmin using linear extrapolation:

(iv) Decrease the total space heating capacity, Q h k(T), by the quantity (E fan,1 − E fan,min), when expressed on a Btu/h basis. Decrease the total electrical power, E h k(T) by the same fan power difference, now expressed in watts.

f. If the temperature sensors used to provide the primary measurement of the indoor-side dry bulb temperature difference during the steady-state dry-coil test and the subsequent cyclic dry-coil test are different, include measurements of the latter sensors among the regularly sampled data. Beginning at the start of the 30-minute data collection period, measure and compute the indoor-side air dry-bulb temperature difference using both sets of instrumentation, ΔT (Set SS) and ΔT (Set CYC), for each equally spaced data sample. If using a consistent data sampling rate that is less than 1 minute, calculate and record minutely averages for the two temperature differences. If using a consistent sampling rate of one minute or more, calculate and record the two temperature differences from each data sample. After having recorded the seventh (i=7) set of temperature differences, calculate the following ratio using the first seven sets of values:

Each time a subsequent set of temperature differences is recorded (if sampling more frequently than every 5 minutes), calculate FCD using the most recent seven sets of values. Continue these calculations until the 30-minute period is completed or until a value for FCD is calculated that falls outside the allowable range of 0.94-1.06. If the latter occurs, immediately suspend the test and identify the cause for the disparity in the two temperature difference measurements. Recalibration of one or both sets of instrumentation may be required. If all the values for FCD are within the allowable range, save the final value of the ratio from the 30-minute test as FCD*. If the temperature sensors used to provide the primary measurement of the indoor-side dry bulb temperature difference during the steady-state dry-coil test and the subsequent cyclic dry-coil test are the same, set FCD*= 1. 3.8 Test Procedures for the Cyclic Heating Mode Tests (the H0C1, H1C, H1C1 and H1C2 Tests).

a. Except as noted below, conduct the cyclic heating mode test as specified in section 3.5 of this appendix. As adapted to the heating mode, replace section 3.5 references to “the steady-state dry coil test” with “the heating mode steady-state test conducted at the same test conditions as the cyclic heating mode test.” Use the test tolerances in Table 17 rather than Table 10. Record the outdoor coil entering wet-bulb temperature according to the requirements given in section 3.5 of this appendix for the outdoor coil entering dry-bulb temperature. Drop the subscript “dry” used in variables cited in section 3.5 of this appendix when referring to quantities from the cyclic heating mode test. If available, use electric resistance heaters (see section 2.1 of this appendix) to minimize the variation in the inlet air temperature. Determine the total space heating delivered during the cyclic heating test, qcyc, as specified in section 3.5 of this appendix except for making the following changes:

(1) When evaluating Equation 3.5-1, use the values of V , Cp,a,vn′, (or vn), and Wn that were recorded during the section 3.7 steady-state test conducted at the same test conditions.

(2) Calculate

where FCD* is the value recorded during the section 3.7 steady-state test conducted at the same test condition.

b. For ducted coil-only system heat pumps (excluding the special case where a variable-speed fan is temporarily removed),

(1) For mobile home and space-constrained ducted coil-only systems,

(i) For two-stage or variable-speed systems, for all cyclic heating tests (i.e., the H1C1 and H1C2 tests), increase qcyc by the amount calculated using Equation 3.5-2 to this appendix. Additionally, increase ecyc by the amount calculated using Equation 3.5-3 to this appendix.

(ii) For single-stage systems, for all cyclic heating tests (i.e., the H1C and H1C1 tests), increase qcyc by the amount calculated using Equation 3.5-4 to this appendix. Additionally, increase ecyc by the amount calculated using Equation 3.5-5 to this appendix.

(2) For non-mobile home and non-space-constrained ducted coil-only systems,

(i) For two-stage or variable-speed systems, for all cyclic heating tests (i.e., the H1C1 and H1C2 tests), increase qcyc by the amount calculated using Equation 3.5-6 to this appendix. Additionally, increase ecyc by the amount calculated using Equation 3.5-7 to this appendix.

(ii) For single-stage systems, for all cyclic heating tests (i.e., the H1C and H1C1 tests), increase qcyc by the amount calculated using Equation 3.5-8 to this appendix. Additionally, increase ecyc by the amount calculated using Equation 3.5-9 to this appendix.

In making these calculations, use the average indoor air volume rate (Vs) determined from the section 3.7 of this appendix steady-state heating mode test conducted at the same test conditions.

c. For non-ducted heat pumps, subtract the electrical energy used by the indoor blower during the 3 minutes after compressor cutoff from the non-ducted heat pump's integrated heating capacity, qcyc.

d. If a heat pump defrost cycle is manually or automatically initiated immediately prior to or during the OFF/ON cycling, operate the heat pump continuously until 10 minutes after defrost termination. After that, begin cycling the heat pump immediately or delay until the specified test conditions have been re-established. Pay attention to preventing defrosts after beginning the cycling process. For heat pumps that cycle off the indoor blower during a defrost cycle, make no effort here to restrict the air movement through the indoor coil while the fan is off. Resume the OFF/ON cycling while conducting a minimum of two complete compressor OFF/ON cycles before determining qcyc and ecyc.

3.8.1 Heating Mode Cyclic-Degradation Coefficient Calculation

Use the results from the required cyclic test and the required steady-state test that were conducted at the same test conditions to determine the heating mode cyclic-degradation coefficient CDh. Add “(k=2)” to the coefficient if it corresponds to a two-capacity unit cycling at high capacity. For the below calculation of the heating mode cyclic degradation coefficient, do not include the duct loss correction from section 7.3.3.3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3) in determining Q h k(Tcyc) (or qcyc). If the optional cyclic test is conducted but yields a tested CDh that exceeds the default CDh or if the optional test is not conducted, assign CDh the default value of 0.25. The default value for two-capacity units cycling at high capacity, however, is the low-capacity coefficient, i.e., CDh (k=2) = CDh. The tested CDh is calculated as follows:

Where: the average coefficient of performance during the cyclic heating mode test, dimensionless. the average coefficient of performance during the steady-state heating mode test conducted at the same test conditions—i.e., same outdoor dry bulb temperature, Tcyc, and speed/capacity, k, if applicable—as specified for the cyclic heating mode test, dimensionless. the heating load factor, dimensionless. Tcyc = the nominal outdoor temperature at which the cyclic heating mode test is conducted, 62 or 47 °F. Δτcyc = the duration of the OFF/ON intervals; 0.5 hours when testing a heat pump having a single-speed or two-capacity compressor and 1.0 hour when testing a heat pump having a variable-speed compressor.

Round the calculated value for CDh to the nearest 0.01. If CDh is negative, then set it equal to zero.

Table 17—Test Operating and Test Condition Tolerances for Cyclic Heating Mode Tests

Test operating tolerance 1Test condition tolerance 1Indoor entering dry-bulb temperature, 2 °F2.00.5 Indoor entering wet-bulb temperature, 2 °F1.0 Outdoor entering dry-bulb temperature, 2 °F2.00.5 Outdoor entering wet-bulb temperature, 2 °F2.01.0 External resistance to air-flow, 2 inches of water0.05 Airflow nozzle pressure difference or velocity pressure, 2% of reading2.03 2.0 Electrical voltage, 4% of reading2.01.5

1 See section 1.2 of this appendix, Definitions.

2 Applies during the interval that air flows through the indoor (outdoor) coil except for the first 30 seconds after flow initiation. For units having a variable-speed indoor blower that ramps, the tolerances listed for the external resistance to airflow shall apply from 30 seconds after achieving full speed until ramp down begins.

3 The test condition must be the average nozzle pressure difference or velocity pressure measured during the steady-state test conducted at the same test conditions.

4 Applies during the interval that at least one of the following—the compressor, the outdoor fan, or, if applicable, the indoor blower—are operating, except for the first 30 seconds after compressor start-up.

3.9 Test Procedures for Frost Accumulation Heating Mode Tests (the H2, H22, H2V, and H21 Tests).

a. Confirm that the defrost controls of the heat pump are set as specified in section 2.2.1 of this appendix. Operate the test room reconditioning apparatus and the heat pump for at least 30 minutes at the specified section 3.6 test conditions before starting the “preliminary” test period. The preliminary test period must immediately precede the “official” test period, which is the heating and defrost interval over which data are collected for evaluating average space heating capacity and average electrical power consumption.

b. For heat pumps containing defrost controls which are likely to cause defrosts at intervals less than one hour, the preliminary test period starts at the termination of an automatic defrost cycle and ends at the termination of the next occurring automatic defrost cycle. For heat pumps containing defrost controls which are likely to cause defrosts at intervals exceeding one hour, the preliminary test period must consist of a heating interval lasting at least one hour followed by a defrost cycle that is either manually or automatically initiated. In all cases, the heat pump's own controls must govern when a defrost cycle terminates.

c. The official test period begins when the preliminary test period ends, at defrost termination. The official test period ends at the termination of the next occurring automatic defrost cycle. When testing a heat pump that uses a time-adaptive defrost control system (see section 1.2 of this appendix, Definitions), however, manually initiate the defrost cycle that ends the official test period at the instant indicated by instructions provided by the manufacturer. If the heat pump has not undergone a defrost after 6 hours, immediately conclude the test and use the results from the full 6-hour period to calculate the average space heating capacity and average electrical power consumption.

For heat pumps that turn the indoor blower off during the defrost cycle, take steps to cease forced airflow through the indoor coil and block the outlet duct whenever the heat pump's controls cycle off the indoor blower. If it is installed, use the outlet damper box described in section 2.5.4.1 of this appendix to affect the blocked outlet duct.

d. Defrost termination occurs when the controls of the heat pump actuate the first change in converting from defrost operation to normal heating operation. Defrost initiation occurs when the controls of the heat pump first alter its normal heating operation in order to eliminate possible accumulations of frost on the outdoor coil.

e. To constitute a valid frost accumulation test, satisfy the test tolerances specified in Table 18 during both the preliminary and official test periods. As noted in Table 18, test operating tolerances are specified for two sub-intervals:

(1) When heating, except for the first 10 minutes after the termination of a defrost cycle (sub-interval H, as described in Table 18) and

(2) When defrosting, plus these same first 10 minutes after defrost termination (sub-interval D, as described in Table 18). Evaluate compliance with Table 18 test condition tolerances and the majority of the test operating tolerances using the averages from measurements recorded only during sub-interval H. Continuously record the dry bulb temperature of the air entering the indoor coil, and the dry bulb temperature and water vapor content of the air entering the outdoor coil. Sample the remaining parameters listed in Table 18 at equal intervals that span 5 minutes or less.

f. For the official test period, collect and use the following data to calculate average space heating capacity and electrical power. During heating and defrosting intervals when the controls of the heat pump have the indoor blower on, continuously record the dry-bulb temperature of the air entering (as noted above) and leaving the indoor coil. If using a thermopile, continuously record the difference between the leaving and entering dry-bulb temperatures during the interval(s) that air flows through the indoor coil. For coil-only system heat pumps, determine the corresponding cumulative time (in hours) of indoor coil airflow, Δτa. Sample measurements used in calculating the air volume rate (refer to sections 7.7.2.1 and 7.7.2.2 of ANSI/ASHRAE 37-2009) at equal intervals that span 10 minutes or less. (Note: In the first printing of ANSI/ASHRAE 37-2009, the second IP equation for Qmi should read:) Record the electrical energy consumed, expressed in watt-hours, from defrost termination to defrost termination, eDEF k(35), as well as the corresponding elapsed time in hours, Δτspan.

Table 18—Test Operating and Test Condition Tolerances for Frost Accumulation Heating Mode Tests

Test operating tolerance 1Test condition tolerance 1 Sub-interval H 2Sub-interval H 2Sub-interval D 3Indoor entering dry-bulb temperature, °F2.04 4.00.5 Indoor entering wet-bulb temperature, °F1.0 Outdoor entering dry-bulb temperature, °F2.010.01.0 Outdoor entering wet-bulb temperature, °F1.50.5 External resistance to airflow, inches of water0.055 0.02 Electrical voltage, % of reading2.01.5

1 See section 1.2 of this appendix, Definitions.

2 Applies when the heat pump is in the heating mode, except for the first 10 minutes after termination of a defrost cycle.

3 Applies during a defrost cycle and during the first 10 minutes after the termination of a defrost cycle when the heat pump is operating in the heating mode.

4 For heat pumps that turn off the indoor blower during the defrost cycle, the noted tolerance only applies during the 10 minute interval that follows defrost termination.

5 Only applies when testing non-ducted heat pumps.

3.9.1 Average Space Heating Capacity and Electrical Power Calculations

a. Evaluate average space heating capacity, Q h k(35), when expressed in units of Btu per hour, using:

where, V = the average indoor air volume rate measured during sub-interval H, cfm. Cp,a = 0.24 + 0.444 · Wn, the constant pressure specific heat of the air-water vapor mixture that flows through the indoor coil and is expressed on a dry air basis, Btu/lbmda · °F. vn′ = specific volume of the air-water vapor mixture at the nozzle, ft 3/lbmmx. Wn = humidity ratio of the air-water vapor mixture at the nozzle, lbm of water vapor per lbm of dry air. Δτspan = τ2 − τ1, the elapsed time from defrost termination to defrost termination, hr. Tal(τ) = dry bulb temperature of the air entering the indoor coil at elapsed time τ, °F; only recorded when indoor coil airflow occurs; assigned the value of zero during periods (if any) where the indoor blower cycles off. Ta2(τ) = dry bulb temperature of the air leaving the indoor coil at elapsed time τ, °F; only recorded when indoor coil airflow occurs; assigned the value of zero during periods (if any) where the indoor blower cycles off. τ1 = the elapsed time when the defrost termination occurs that begins the official test period, hr. τ2 = the elapsed time when the next automatically occurring defrost termination occurs, thus ending the official test period, hr. vn = specific volume of the dry air portion of the mixture evaluated at the dry-bulb temperature, vapor content, and barometric pressure existing at the nozzle, ft 3 per lbm of dry air.

To account for the effect of duct losses between the outlet of the indoor unit and the section 2.5.4 dry-bulb temperature grid, adjust Q h k(35) in accordance with section 7.3.4.3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3).

(1) For mobile home and space-constrained ducted coil-only system tests,

(i) For two-stage or variable-speed systems, for all frost accumulation tests (i.e., the H21, H22, and H2V tests), increase Qhk(35) by the quantity calculated in Equation 3.9.1-1 to this appendix and increase Ehk (35) by the quantity calculated in Equation 3.9.1-2 to this appendix.

Where: DFPCMHSC is the default fan power coefficient (watts) for mobile-home and space-constrained systems, And %FLAVR is the air volume rate used for the test, expressed as a percentage of the cooling full load air volume rate. For all tests specifying the full-load air volume rate (e.g., the H22 test), set %FLAVR to 100%. For tests that specify the heating minimum air volume rate or heating intermediate air volume rate (i.e., the H21 and H2v tests) and for which the specified minimum or intermediate air volume rate is greater than or equal to 75 percent of the cooling full-load air volume rate and less than the cooling full-load air volume rate, set %FLAVR to the ratio of the specified air volume rate and the cooling full-load air volume rate, expressed as a percentage.

(ii) For single-stage systems, for all frost accumulation tests (i.e., the H2 test), increase Qhk(35) by the quantity calculated in Equation 3.9.1-3 to this appendix and increase Qhk(35) by the quantity calculated in Equation 3.9.1-4 to this appendix.

Where Vs is the average measured indoor air volume rate expressed in units of cubic feet per minute of standard air (scfm).

(2) For non-mobile home and non-space-constrained ducted coil-only systems,

(i) For two-stage or variable-speed systems, for all frost accumulation tests (i.e., the H21, H22, and H2V tests), increase Qhk(35) by the quantity calculated in Equation 3.9.1-5 to this appendix and increase Ehk(35) by the quantity calculated in Equation 3.9.1-6 to this appendix.

Where: DFPCC is the default fan power coefficient (watts) for non-mobile-home and non-space-constrained systems, And %FLAVR is the air volume rate used for the test, expressed as a percentage of the cooling full load air volume rate. For all tests specifying the full-load air volume rate (e.g., the H22 test), set %FLAVR to 100%. For tests that specify the heating minimum air volume rate or heating intermediate air volume rate (i.e., the H21 and H2v tests) and for which the specified minimum or intermediate air volume rate is greater than or equal to 75 percent of the cooling full-load air volume rate and less than the cooling full-load air volume rate, set %FLAVR to the ratio of the specified air volume rate and the cooling full-load air volume rate, expressed as a percentage.

(ii) For single-stage systems, for all frost accumulation tests (i.e., the H2 test), increase Qhk (35) by the quantity calculated in Equation 3.9.1-7 to this appendix and increase Ehk (35) by the quantity calculated in Equation 3.9.1-8 to this appendix.

Where Vs is the average measured indoor air volume rate expressed in units of cubic feet per minute of standard air (scfm).

c. For heat pumps having a constant-air-volume-rate indoor blower, the five additional steps listed below are required if the average of the external static pressures measured during sub-interval H exceeds the applicable section 3.1.4.4, 3.1.4.5, or 3.1.4.6 minimum (or targeted) external static pressure (ΔPmin) by 0.03 inches of water or more:

(1) Measure the average power consumption of the indoor blower motor (E fan,1) and record the corresponding external static pressure (ΔP1) during or immediately following the frost accumulation heating mode test. Make the measurement at a time when the heat pump is heating, except for the first 10 minutes after the termination of a defrost cycle.

(2) After the frost accumulation heating mode test is completed and while maintaining the same test conditions, adjust the exhaust fan of the airflow measuring apparatus until the external static pressure increases to approximately ΔP1 + (ΔP1 − ΔPmin).

(3) After re-establishing steady readings for the fan motor power and external static pressure, determine average values for the indoor blower power (E fan,2) and the external static pressure (ΔP2) by making measurements over a 5-minute interval.

(4) Approximate the average power consumption of the indoor blower motor had the frost accumulation heating mode test been conducted at ΔPmin using linear extrapolation:

(5) Decrease the total heating capacity, Q h k(35), by the quantity [(E fan,1 − E fan,min)· (Δτ a/Δτ span], when expressed on a Btu/h basis. Decrease the total electrical power, Eh k(35), by the same quantity, now expressed in watts.

3.9.2 Demand Defrost Credit

a. Assign the demand defrost credit, Fdef, that is used in section 4.2 of this appendix to the value of 1 in all cases except for heat pumps having a demand-defrost control system (see section 1.2 of this appendix, Definitions). For such qualifying heat pumps, evaluate Fdef using,

where: Δτdef = the time between defrost terminations (in hours) or 1.5, whichever is greater. Assign a value of 6 to Δτdef if this limit is reached during a frost accumulation test and the heat pump has not completed a defrost cycle. Δτmax = maximum time between defrosts as allowed by the controls (in hours) or 12, whichever is less, as provided in the certification report.

b. For two-capacity heat pumps and for section 3.6.2 units, evaluate the above equation using the Δτdef that applies based on the frost accumulation test conducted at high capacity and/or at the heating full-load air volume rate. For variable-speed heat pumps, evaluate Δτdef based on the required frost accumulation test conducted at the intermediate compressor speed.

3.10 Test Procedures for Steady-State Low Temperature and Very Low Temperature Heating Mode Tests (the H3, H32, H31, H33, H4, H42, and H43 Tests)

Except for the modifications noted in this section, conduct the low temperature and very low temperature heating mode tests using the same approach as specified in section 3.7 of this appendix for the maximum and high temperature tests. After satisfying the section 3.7 requirements for the pretest interval but before beginning to collect data to determine the capacity and power input, conduct a defrost cycle. This defrost cycle may be manually or automatically initiated. Terminate the defrost sequence using the heat pump's defrost controls. Begin the 30-minute data collection interval described in section 3.7 of this appendix, from which the capacity and power input are determined, no sooner than 10 minutes after defrost termination. Defrosts should be prevented over the 30-minute data collection interval.

3.11 Additional Requirements for the Secondary Test Methods 3.11.1 If Using the Outdoor Air Enthalpy Method as the Secondary Test Method.

a. For all cooling mode and heating mode tests, first conduct a test without the outdoor air-side test apparatus described in section 2.10.1 of this appendix connected to the outdoor unit (“free outdoor air” test).

b. For the first section 3.2 steady-state cooling mode test and the first section 3.6 steady-state heating mode test, conduct a second test in which the outdoor-side apparatus is connected (“ducted outdoor air” test). No other cooling mode or heating mode tests require the ducted outdoor air test so long as the unit operates the outdoor fan during all cooling mode steady-state tests at the same speed and all heating mode steady-state tests at the same speed. If using more than one outdoor fan speed for the cooling mode steady-state tests, however, conduct the ducted outdoor air test for each cooling mode test where a different fan speed is first used. This same requirement applies for the heating mode tests.

3.11.1.1 Free Outdoor Air Test

a. For the free outdoor air test, connect the indoor air-side test apparatus to the indoor coil; do not connect the outdoor air-side test apparatus. Allow the test room reconditioning apparatus and the unit being tested to operate for at least one hour. After attaining equilibrium conditions, measure the following quantities at equal intervals that span 5 minutes or less:

(1) The section 2.10.1 evaporator and condenser temperatures or pressures;

(2) Parameters required according to the Indoor Air Enthalpy Method.

Continue these measurements until a 30-minute period (e.g., seven consecutive 5-minute samples) is obtained where the Table 9 or Table 16, whichever applies, test tolerances are satisfied.

b. For cases where a ducted outdoor air test is not required per section 3.11.1.b of this appendix, the free outdoor air test constitutes the “official” test for which validity is not based on comparison with a secondary test.

c. For cases where a ducted outdoor air test is required per section 3.11.1.b of this appendix, the following conditions must be met for the free outdoor air test to constitute a valid “official” test:

(1) The energy balance specified in section 3.1.1 of this appendix is achieved for the ducted outdoor air test (i.e., compare the capacities determined using the indoor air enthalpy method and the outdoor air enthalpy method).

(2) The capacities determined using the indoor air enthalpy method from the ducted outdoor air and free outdoor air tests must agree within 2 percent.

3.11.1.2 Ducted Outdoor Air Test

a. The test conditions and tolerances for the ducted outdoor air test are the same as specified for the official test, where the official test is the free outdoor air test described in section 3.11.1.1 of this appendix.

b. After collecting 30 minutes of steady-state data during the free outdoor air test, connect the outdoor air-side test apparatus to the unit for the ducted outdoor air test. Adjust the exhaust fan of the outdoor airflow measuring apparatus until averages for the evaporator and condenser temperatures, or the saturated temperatures corresponding to the measured pressures, agree within ±0.5 °F of the averages achieved during the free outdoor air test. Collect 30 minutes of steady-state data after re-establishing equilibrium conditions.

c. During the ducted outdoor air test, at intervals of 5 minutes or less, measure the parameters required according to the indoor air enthalpy method and the outdoor air enthalpy method for the prescribed 30 minutes.

d. For cooling mode ducted outdoor air tests, calculate capacity based on outdoor air-enthalpy measurements as specified in sections 7.3.3.2 and 7.3.3.3 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3). For heating mode ducted tests, calculate heating capacity based on outdoor air-enthalpy measurements as specified in sections 7.3.4.2 and 7.3.3.4.3 of the same ANSI/ASHRAE Standard. Adjust the outdoor-side capacity according to section 7.3.3.4 of ANSI/ASHRAE 37-2009 to account for line losses when testing split systems. As described in section 8.6.2 of ANSI/ASHRAE 37-2009, use the outdoor air volume rate as measured during the ducted outdoor air tests to calculate capacity for checking the agreement with the capacity calculated using the indoor air enthalpy method.

3.11.2 If Using the Compressor Calibration Method as the Secondary Test Method

a. Conduct separate calibration tests using a calorimeter to determine the refrigerant flow rate. Or for cases where the superheat of the refrigerant leaving the evaporator is less than 5 °F, use the calorimeter to measure total capacity rather than refrigerant flow rate. Conduct these calibration tests at the same test conditions as specified for the tests in this appendix. Operate the unit for at least one hour or until obtaining equilibrium conditions before collecting data that will be used in determining the average refrigerant flow rate or total capacity. Sample the data at equal intervals that span 5 minutes or less. Determine average flow rate or average capacity from data sampled over a 30-minute period where the Table 9 (cooling) or the Table 16 (heating) tolerances are satisfied. Otherwise, conduct the calibration tests according to sections 5, 6, 7, and 8 of ASHRAE 23.1-2010 (incorporated by reference, see § 430.3); sections 5, 6, 7, 8, 9, and 11 of ASHRAE 41.9-2011 (incorporated by reference, see § 430.3); and section 7.4 of ANSI/ASHRAE 37-2009 (incorporated by reference, see § 430.3).

b. Calculate space cooling and space heating capacities using the compressor calibration method measurements as specified in section 7.4.5 and 7.4.6 respectively, of ANSI/ASHRAE 37-2009.

3.11.3 If Using the Refrigerant-Enthalpy Method as the Secondary Test Method

Conduct this secondary method according to section 7.5 of ANSI/ASHRAE 37-2009. Calculate space cooling and heating capacities using the refrigerant-enthalpy method measurements as specified in sections 7.5.4 and 7.5.5, respectively, of the same ANSI/ASHRAE Standard.

3.12 Rounding of Space Conditioning Capacities for Reporting Purposes

a. When reporting rated capacities, round them off as specified in § 430.23 (for a single unit) and in 10 Cspan 429.16 (for a sample).

b. For the capacities used to perform the calculations in section 4 of this appendix, however, round only to the nearest integer.

3.13 Laboratory Testing To Determine Off Mode Average Power Ratings

Voltage tolerances: As a percentage of reading, test operating tolerance must be 2.0 percent and test condition tolerance must be 1.5 percent (see section 1.2 of this appendix for definitions of these tolerances).

Conduct one of the following tests: If the central air conditioner or heat pump lacks a compressor crankcase heater, perform the test in section 3.13.1 of this appendix; if the central air conditioner or heat pump has a compressor crankcase heater that lacks controls and is not self-regulating, perform the test in section 3.13.1 of this appendix; if the central air conditioner or heat pump has a crankcase heater with a fixed power input controlled with a thermostat that measures ambient temperature and whose sensing element temperature is not affected by the heater, perform the test in section 3.13.1 of this appendix; if the central air conditioner or heat pump has a compressor crankcase heater equipped with self-regulating control or with controls for which the sensing element temperature is affected by the heater, perform the test in section 3.13.2 of this appendix.

3.13.1 This Test Determines the Off Mode Average Power Rating for Central Air Conditioners and Heat Pumps That Lack a Compressor Crankcase Heater, or Have a Compressor Crankcase Heating System That Can Be Tested Without Control of Ambient Temperature During the Test. This Test Has No Ambient Condition Requirements

a. Test Sample Set-up and Power Measurement: For coil-only systems, provide a furnace or modular blower that is compatible with the system to serve as an interface with the thermostat (if used for the test) and to provide low-voltage control circuit power. Make all control circuit connections between the furnace (or modular blower) and the outdoor unit as specified by the manufacturer's installation instructions. Measure power supplied to both the furnace (or modular blower) and power supplied to the outdoor unit. Alternatively, provide a compatible transformer to supply low-voltage control circuit power, as described in section 2.2.d of this appendix. Measure transformer power, either supplied to the primary winding or supplied by the secondary winding of the transformer, and power supplied to the outdoor unit. For blower coil and single-package systems, make all control circuit connections between components as specified by the manufacturer's installation instructions, and provide power and measure power supplied to all system components.

b. Configure Controls: Configure the controls of the central air conditioner or heat pump so that it operates as if connected to a building thermostat that is set to the OFF position. Use a compatible building thermostat if necessary to achieve this configuration. For a thermostat-controlled crankcase heater with a fixed power input, bypass the crankcase heater thermostat if necessary to energize the heater.

c. Measure P2x: If the unit has a crankcase heater time delay, make sure that time-delay function is disabled or wait until delay time has passed. Determine the average power from non-zero value data measured over a 5-minute interval of the non-operating central air conditioner or heat pump and designate the average power as P2x, the heating season total off mode power.

d. Measure Px for coil-only split systems and for blower coil split systems for which a furnace or a modular blower is the designated air mover: Disconnect all low-voltage wiring for the outdoor components and outdoor controls from the low-voltage transformer. Determine the average power from non-zero value data measured over a 5-minute interval of the power supplied to the (remaining) low-voltage components of the central air conditioner or heat pump, or low-voltage power, Px. This power measurement does not include line power supplied to the outdoor unit. It is the line power supplied to the air mover, or, if a compatible transformer is used instead of an air mover, it is the line power supplied to the transformer primary coil. If a compatible transformer is used instead of an air mover and power output of the low-voltage secondary circuit is measured, Px is zero.

e. Calculate P2: Set the number of compressors equal to the unit's number of single-stage compressors plus 1.75 times the unit's number of compressors that are not single-stage.

For single-package systems and blower coil split systems for which the designated air mover is not a furnace or modular blower, divide the heating season total off mode power (P2x) by the number of compressors to calculate P2, the heating season per-compressor off mode power. Round P2 to the nearest watt. The expression for calculating P2 is as follows:

For coil-only split systems and blower coil split systems for which a furnace or a modular blower is the designated air mover, subtract the low-voltage power (Px) from the heating season total off mode power (Px) and divide by the number of compressors to calculate P2, the heating season per-compressor off mode power. Round P2 to the nearest watt. The expression for calculating P2 is as follows:

f. Shoulder-season per-compressor off mode power, P1: If the system does not have a crankcase heater, has a crankcase heater without controls that is not self-regulating, or has a value for the crankcase heater turn-on temperature (as certified to DOE) that is higher than 71 °F, P1 is equal to P2.

Otherwise, de-energize the crankcase heater (by removing the thermostat bypass or otherwise disconnecting only the power supply to the crankcase heater) and repeat the measurement as described in section 3.13.1.c of this appendix. Designate the measured average power as P1x, the shoulder season total off mode power.

Determine the number of compressors as described in section 3.13.1.e of this appendix.

For single-package systems and blower coil systems for which the designated air mover is not a furnace or modular blower, divide the shoulder season total off mode power (P1x) by the number of compressors to calculate P1, the shoulder season per-compressor off mode power. Round P1 to the nearest watt. The expression for calculating P1 is as follows:

For coil-only split systems and blower coil split systems for which a furnace or a modular blower is the designated air mover, subtract the low-voltage power (Px) from the shoulder season total off mode power (P1x) and divide by the number of compressors to calculate P1, the shoulder season per-compressor off mode power. Round P1 to the nearest watt. The expression for calculating P1 is as follows:

3.13.2 This Test Determines the Off Mode Average Power Rating for Central Air Conditioners and Heat Pumps for Which Ambient Temperature Can Affect the Measurement of Crankcase Heater Power

a. Test Sample Set-up and Power Measurement: set up the test and measurement as described in section 3.13.1.a of this appendix.

b. Configure Controls: Position a temperature sensor to measure the outdoor dry-bulb temperature in the air between 2 and 6 inches from the crankcase heater control temperature sensor or, if no such temperature sensor exists, position it in the air between 2 and 6 inches from the crankcase heater. Utilize the temperature measurements from this sensor for this portion of the test procedure. Configure the controls of the central air conditioner or heat pump so that it operates as if connected to a building thermostat that is set to the OFF position. Use a compatible building thermostat if necessary to achieve this configuration.

Conduct the test after completion of the B, B1, or B2 test. Alternatively, start the test when the outdoor dry-bulb temperature is at 82 °F and the temperature of the compressor shell (or temperature of each compressor's shell if there is more than one compressor) is at least 81 °F. Then adjust the outdoor temperature and achieve an outdoor dry-bulb temperature of 72 °F. If the unit's compressor has no sound blanket, wait at least 4 hours after the outdoor temperature reaches 72 °F. Otherwise, wait at least 8 hours after the outdoor temperature reaches 72 °F. Maintain this temperature within ±2 °F while the compressor temperature equilibrates and while making the power measurement, as described in section 3.13.2.c of this appendix.

c. Measure P1x: If the unit has a crankcase heater time delay, make sure that time-delay function is disabled or wait until delay time has passed. Determine the average power from non-zero value data measured over a 5-minute interval of the non-operating central air conditioner or heat pump and designate the average power as P1x, the shoulder season total off mode power. For units with crankcase heaters which operate during this part of the test and whose controls cycle or vary crankcase heater power over time, the test period shall consist of three complete crankcase heater cycles or 18 hours, whichever comes first. Designate the average power over the test period as P1x, the shoulder season total off mode power.

d. Reduce outdoor temperature: Approach the target outdoor dry-bulb temperature by adjusting the outdoor temperature. This target temperature is five degrees Fahrenheit less than the temperature certified by the manufacturer as the temperature at which the crankcase heater turns on. If the unit's compressor has no sound blanket, wait at least 4 hours after the outdoor temperature reaches the target temperature. Otherwise, wait at least 8 hours after the outdoor temperature reaches the target temperature. Maintain the target temperature within ±2 °F while the compressor temperature equilibrates and while making the power measurement, as described in section 3.13.2.e of this appendix.

e. Measure P2x: If the unit has a crankcase heater time delay, make sure that time-delay function is disabled or wait until delay time has passed. Determine the average non-zero power of the non-operating central air conditioner or heat pump over a 5-minute interval and designate it as P2x, the heating season total off mode power. For units with crankcase heaters whose controls cycle or vary crankcase heater power over time, the test period shall consist of three complete crankcase heater cycles or 18 hours, whichever comes first. Designate the average power over the test period as P2x, the heating season total off mode power.

f. Measure Px for coil-only split systems and for blower coil split systems for which a furnace or modular blower is the designated air mover: Disconnect all low-voltage wiring for the outdoor components and outdoor controls from the low-voltage transformer. Determine the average power from non-zero value data measured over a 5-minute interval of the power supplied to the (remaining) low-voltage components of the central air conditioner or heat pump, or low-voltage power, Px. This power measurement does not include line power supplied to the outdoor unit. It is the line power supplied to the air mover, or, if a compatible transformer is used instead of an air mover, it is the line power supplied to the transformer primary coil. If a compatible transformer is used instead of an air mover and power output of the low-voltage secondary circuit is measured, Px is zero.

g. Calculate P1:

Set the number of compressors equal to the unit's number of single-stage compressors plus 1.75 times the unit's number of compressors that are not single-stage.

For single-package systems and blower coil split systems for which the air mover is not a furnace or modular blower, divide the shoulder season total off mode power (P1x) by the number of compressors to calculate P1, the shoulder season per-compressor off mode power. Round to the nearest watt. The expression for calculating P1 is as follows:

For coil-only split systems and blower coil split systems for which a furnace or a modular blower is the designated air mover, subtract the low-voltage power (Px) from the shoulder season total off mode power (P1x) and divide by the number of compressors to calculate P1, the shoulder season per-compressor off mode power. Round to the nearest watt. The expression for calculating P1 is as follows:

h. Calculate P2:

Determine the number of compressors as described in section 3.13.2.g of this appendix.

For, single-package systems and blower coil split systems for which the air mover is not a furnace, divide the heating season total off mode power (P2x) by the number of compressors to calculate P2, the heating season per-compressor off mode power. Round to the nearest watt. The expression for calculating P2 is as follows:

For coil-only split systems and blower coil split systems for which a furnace or a modular blower is the designated air mover, subtract the low-voltage power (Px) from the heating season total off mode power (P2x) and divide by the number of compressors to calculate P2, the heating season per-compressor off mode power. Round to the nearest watt. The expression for calculating P2 is as follows:

4 Calculations of Seasonal Performance Descriptors 4.1 Seasonal Energy Efficiency Ratio (SEER2) Calculations

Calculate SEER2 as follows: For equipment covered under sections 4.1.2, 4.1.3, and 4.1.4 of this appendix, evaluate the seasonal energy efficiency ratio,

where, Tj = the outdoor bin temperature, °F. Outdoor temperatures are grouped or “binned.” Use bins of 5 °F with the 8 cooling season bin temperatures being 67, 72, 77, 82, 87, 92, 97, and 102 °F. j = the bin number. For cooling season calculations, j ranges from 1 to 8.

Additionally, for sections 4.1.2, 4.1.3, and 4.1.4 of this appendix, use a building cooling load, BL(Tj). When referenced, evaluate BL(Tj) for cooling using,

where: Q ck=2(95) = the space cooling capacity determined from the A2 test and calculated as specified in section 3.3 of this appendix, Btu/h. 1.1 = sizing factor, dimensionless. The temperatures 95 °F and 65 °F in the building load equation represent the selected outdoor design temperature and the zero-load base temperature, respectively. V is a factor equal to 0.93 for variable-speed heat pumps and otherwise equal to 1.0. 4.1.1 SEER2 Calculations for a Blower Coil System Having a Single-Speed Compressor and Either a Fixed-Speed Indoor Blower or a Constant-Air-Volume-Rate Indoor Blower, or a Single-Speed Coil-Only System Air Conditioner or Heat Pump

a. Evaluate the seasonal energy efficiency ratio, expressed in units of Btu/watt-hour, using:

SEER2 = PLF(0.5) * EERB

where: PLF(0.5) = 1 − 0.5 · CD c, the part-load performance factor evaluated at a cooling load factor of 0.5, dimensionless.

b. Refer to section 3.3 of this appendix regarding the definition and calculation of Q c(82) and E c(82). Evaluate the cooling mode cyclic degradation factor CD c as specified in section 3.5.3 of this appendix.

4.1.2 SEER2 Calculations for an Air Conditioner or Heat Pump Having a Single-Speed Compressor and a Variable-Speed Variable-Air-Volume-Rate Indoor Blower 4.1.2.1 Units Covered by Section 3.2.2.1 of This Appendix Where Indoor Blower Capacity Modulation Correlates With the Outdoor Dry Bulb Temperature

The manufacturer must provide information on how the indoor air volume rate or the indoor blower speed varies over the outdoor temperature range of 67 °F to 102 °F. Calculate SEER2 using Equation 4.1-1. Evaluate the quantity qc(Tj)/N in Equation 4.1-1 using,

where: Q c(Tj) = the space cooling capacity of the test unit when operating at outdoor temperature, Tj, Btu/h. nj/N = fractional bin hours for the cooling season; the ratio of the number of hours during the cooling season when the outdoor temperature fell within the range represented by bin temperature Tj to the total number of hours in the cooling season, dimensionless.

a. For the space cooling season, assign nj/N as specified in Table 19. Use Equation 4.1-2 to calculate the building load, BL(Tj). Evaluate Q c(Tj) using,

where: the space cooling capacity of the test unit at outdoor temperature Tj if operated at the cooling minimum air volume rate, Btu/h. the space cooling capacity of the test unit at outdoor temperature Tj if operated at the Cooling full-load air volume rate, Btu/h.

b. For units where indoor blower speed is the primary control variable, spanck=1 denotes the fan speed used during the required A1 and B1 tests (see section 3.2.2.1 of this appendix), spanck=2 denotes the fan speed used during the required A2 and B2 tests, and spanc(Tj) denotes the fan speed used by the unit when the outdoor temperature equals Tj. For units where indoor air volume rate is the primary control variable, the three spanc's are similarly defined only now being expressed in terms of air volume rates rather than fan speeds. Refer to sections 3.2.2.1, 3.1.4 to 3.1.4.2, and 3.3 of this appendix regarding the definitions and calculations of Q ck=1(82), Q ck=1(95),Q c k=2(82), and Q ck=2(95).

Calculate ec(Tj)/N in Equation 4.1-1 using, Equation 4.1.2-3

where: PLFj = 1 − CD c · [1 − X(Tj)], the part load factor, dimensionless. E c(Tj) = the electrical power consumption of the test unit when operating at outdoor temperature Tj, W.

c. The quantities X(Tj) and nj/N are the same quantities as used in Equation 4.1.2-1. Evaluate the cooling mode cyclic degradation factor CD c as specified in section 3.5.3 of this appendix.

d. Evaluate E c(Tj) using,

the electrical power consumption of the test unit at outdoor temperature Tj if operated at the cooling minimum air volume rate, W.

e. The parameters spanck=1, and spanck=2, and spanc(Tj) are the same quantities that are used when evaluating Equation 4.1.2-2. Refer to sections 3.2.2.1, 3.1.4 to 3.1.4.2, and 3.3 of this appendix regarding the definitions and calculations of E ck=1(82), E ck=1(95), E ck=2(82), and E ck=2(95).

4.1.2.2 Units Covered by Section 3.2.2.2 of This Appendix Where Indoor Blower Capacity Modulation is Used to Adjust the Sensible to Total Cooling Capacity Ratio

Calculate SEER2 as specified in section 4.1.1 of this appendix.

4.1.3 SEER2 Calculations for an Air Conditioner or Heat Pump Having a Two-Capacity Compressor

Calculate SEER2 using Equation 4.1-1. Evaluate the space cooling capacity, Q ck=1 (Tj), and electrical power consumption, E ck=1 (Tj), of the test unit when operating at low compressor capacity and outdoor temperature Tj using,

where Q ck=1 (82) and E ck=1 (82) are determined from the B1 test, Q ck=1 (67) and E ck=1 (67) are determined from the F1 test, and all four quantities are calculated as specified in section 3.3 of this appendix. Evaluate the space cooling capacity, Q ck=2 (Tj), and electrical power consumption, E ck=2 (Tj), of the test unit when operating at high compressor capacity and outdoor temperature Tj using, where Q ck=2(95) and E ck=2(95) are determined from the A2 test, Q ck=2(82), and E ck=2(82), are determined from the B2 test, and all are calculated as specified in section 3.3 of this appendix.

The calculation of Equation 4.1-1 quantities qc(Tj)/N and ec(Tj)/N differs depending on whether the test unit would operate at low capacity (section 4.1.3.1 of this appendix), cycle between low and high capacity (section 4.1.3.2 of this appendix), or operate at high capacity (sections 4.1.3.3 and 4.1.3.4 of this appendix) in responding to the building load. For units that lock out low capacity operation at higher outdoor temperatures, the outdoor temperature at which the unit locks out must be that specified by the manufacturer in the certification report so that the appropriate equations are used. Use Equation 4.1-2 to calculate the building load, BL(Tj), for each temperature bin.

4.1.3.1 Steady-state Space Cooling Capacity at Low Compressor Capacity Is Greater Than or Equal to the Building Cooling Load at Temperature Tj, Q ck=1(Tj) ≥BL(Tj) Where: Xk=1(Tj) = BL(Tj)/Q ck=1(Tj), the cooling mode low capacity load factor for temperature bin j, dimensionless. PLFj = 1 − CD c · [1 − Xk=1(Tj)], the part load factor, dimensionless. nj/N = fractional bin hours for the cooling season; the ratio of the number of hours during the cooling season when the outdoor temperature fell within the range represented by bin temperature Tj to the total number of hours in the cooling season, dimensionless.

Obtain the fractional bin hours for the cooling season, nj/N, from Table 19. Use Equations 4.1.3-1 and 4.1.3-2, respectively, to evaluate Q ck=1(Tj) and E ck=1(Tj). Evaluate the cooling mode cyclic degradation factor CD c as specified in section 3.5.3 of this appendix.

Table 19—Distribution of Fractional Hours Within Cooling Season Temperature Bins

Bin number, j Bin temperature range °F Representative temperature for bin °F Fraction of total temperature bin hours, nj/N 165-69670.214 270-74720.231 375-79770.216 480-84820.161 585-89870.104 690-94920.052 795-99970.018 8100-1041020.004
4.1.3.2 Unit Alternates Between High (k=2) and Low (k=1) Compressor Capacity to Satisfy the Building Cooling Load at Temperature Tj, Q ck=1(Tj) < BL(Tj) < Q ck=2(Tj) Where:

Xk=2(Tj) = 1 − Xk=1(Tj), the cooling mode, high capacity load factor for temperature bin j, dimensionless.

Obtain the fractional bin hours for the cooling season, nj/N, from Table 19. Use Equations 4.1.3-1 and 4.1.3-2, respectively, to evaluate Q ck=1(Tj) and E ck=1(Tj). Use Equations 4.1.3-3 and 4.1.3-4, respectively, to evaluate Q ck=2(Tj) and E ck=2(Tj).

4.1.3.3 Unit Only Operates at High (k=2) Compressor Capacity at Temperature Tj and Its Capacity Is Greater Than the Building Cooling Load, BL(Tj) <Q ck=2(Tj). This section applies to units that lock out low compressor capacity operation at higher outdoor temperatures. Where,

Xk=2(Tj) = BL(Tj)/Q ck=2(Tj), the cooling mode high capacity load factor for temperature bin j, dimensionless.

PLFj = 1−CDc(k = 2) * [1−Xk=2(Tj)], the part load factor, dimensionless.

Obtain the fractional bin hours for the cooling season, nj/N, from Table 19. Use Equations 4.1.3-3 and 4.1.3-4, respectively, to evaluate Q ck=2 (Tj) and E ck=2 (Tj). If the C2 and D2 tests described in section 3.2.3 and Table 7 of this appendix are not conducted, set CD c (k=2) equal to the default value specified in section 3.5.3 of this appendix.

4.1.3.4 Unit Must Operate Continuously at High (k=2) Compressor Capacity at Temperature Tj, BL(Tj) ≥Q ck=2(Tj) Obtain the fractional bin hours for the cooling season, nj/N, from Table 19. Use Equations 4.1.3-3 and 4.1.3-4, respectively, to evaluate Q ck=2(Tj) and E ck=2(Tj). 4.1.4 SEER2 Calculations for an Air Conditioner or Heat Pump Having a Variable-Speed Compressor

Calculate SEER2 using Equation 4.1-1 to this appendix. Evaluate the space cooling capacity, Qc k=1(Tj), and electrical power consumption, Ec k=1(Tj), of the test unit when operating at minimum compressor speed and outdoor temperature Tj.. Use:

Where Q c k=1(82) and Ėc k=1(82) are determined from the B1 test, Q c k=1(67) and Ec k=1(67) are determined from the F1 test, and all four quantities are calculated as specified in section 3.3 of this appendix. Evaluate the space cooling capacity, Q c k=2(Tj), and electrical power consumption, Ėc k=2(Tj), of the test unit when operating at full compressor speed and outdoor temperature Tj. Use Equations 4.1.3-3 and 4.1.3-4 to this appendix, respectively, where Q c k=2(95) and Ėck=2(95) are determined from the A2 test, Q c k=2(82) and Ėc k=2(82) are determined from the B2 test, and all four quantities are calculated as specified in section 3.3 of this appendix. For units other than variable-speed non-communicating coil-only air-conditioners or heat pumps, calculate the space cooling capacity, Q c k=v(Tj), and electrical power consumption, Ėc k=v(Tj), of the test unit when operating at outdoor temperature Tj and the intermediate compressor speed used during the section 3.2.4 (and Table 8) EV test of this appendix using: Where Q c k=v(87) are determined from the EV test and calculated as specified in section 3.3 of this appendix. Approximate the slopes of the k=v intermediate speed cooling capacity and electrical power input curves, MQ and ME, as follows: Where:

Use Equations 4.1.4-1 and 4.1.4-2 to this appendix, respectively, to calculate Q c k=1(87) and Ėc k=1(87).

4.1.4.1 Steady-state space cooling capacity when operating at minimum compressor speed is greater than or equal to the building cooling load at temperature Tj, Q ck=1(Tj) ≥BL(Tj).

Where: Xk=1(Tj) = BL(Tj)/Q ck=1(Tj), the cooling mode minimum speed load factor for temperature bin j, dimensionless. PLFj = 1 − CD c · [1 − Xk=1(Tj)], the part load factor, dimensionless. nj/N = fractional bin hours for the cooling season; the ratio of the number of hours during the cooling season when the outdoor temperature fell within the range represented by bin temperature Tj to the total number of hours in the cooling season, dimensionless.

Obtain the fractional bin hours for the cooling season, nj/N, from Table 19. Use Equations 4.1.3-1 and 4.1.3-2, respectively, to evaluate Q c k=l (Tj) and E c k=l (Tj). Evaluate the cooling mode cyclic degradation factor CD c as specified in section 3.5.3 of this appendix.

4.1.4.2 Unit operates at an intermediate compressor speed (k=i) in order to match the building cooling load at temperature Tj, Q ck=1(Tj) <BL(Tj) <Q ck=2(Tj).

Where: Q ck=i(Tj) = BL(Tj), the space cooling capacity delivered by the unit in matching the building load at temperature Tj, Btu/h. The matching occurs with the unit operating at compressor speed k = i. EERk=i(Tj) = the steady-state energy efficiency ratio of the test unit when operating at a compressor speed of k = i and temperature Tj, Btu/h per W.

Obtain the fractional bin hours for the cooling season, nj/N, from Table 19 of this section. For each temperature bin where the unit operates at an intermediate compressor speed, determine the energy efficiency ratio EERk=i(Tj) using the following equations,

For each temperature bin where Q ck=1(Tj) <BL(Tj) <Q ck=v(Tj),

For each temperature bin where Q ck=v(Tj) ≤BL(Tj) <Q ck=2(Tj),

Where:

EERk=1(Tj) is the steady-state energy efficiency ratio of the test unit when operating at minimum compressor speed and temperature Tj, Btu/h per W, calculated using capacity Q ck=1(Tj) calculated using Equation 4.1.4-1 and electrical power consumption E ck=1(Tj) calculated using Equation 4.1.4-2;

EERk=v(Tj) is the steady-state energy efficiency ratio of the test unit when operating at intermediate compressor speed and temperature Tj, Btu/h per W, calculated using capacity Q ck=v(Tj) calculated using Equation 4.1.4-3 and electrical power consumption E ck=v(Tj) calculated using Equation 4.1.4-4;

EERk=2(Tj) is the steady-state energy efficiency ratio of the test unit when operating at full compressor speed and temperature Tj, Btu/h per W, calculated using capacity Q ck=2(Tj) and electrical power consumption E ck=2(Tj), both calculated as described in section 4.1.4; and

BL(Tj) is the building cooling load at temperature Tj, Btu/h.

4.1.4.2.1 Units That Are Not Variable-Speed Non-Communicating Coil-Only Air Conditioners or Heat Pumps

If the unit operates at an intermediate compressor speed (k=i) in order to match the building cooling load at temperature Tj, Q c k=1(Tj) < BL(Tj) < Q c k=2(Tj).

Where: Q c k=i(Tj) = BL(Tj), the space cooling capacity delivered by the unit in matching the building load at temperature Tj, in Btu/h. The matching occurs with the unit operating at compressor speed k = i. EER k=i(Tj) = the steady-state energy efficiency ratio of the test unit when operating at a compressor speed of k = i and temperature Tj, Btu/h per W.

Obtain the fractional bin hours for the cooling season, nj/N, from Table 19 of this section. For each temperature bin where the unit operates at an intermediate compressor speed, determine the energy efficiency ratio EER k=i(Tj) using the following equations:

For each temperature bin where Q c k=1(Tj) < BL(Tj) < Q c k=v(Tj),

For each temperature bin where Q c k=v(Tj) < BL(Tj) < Q c k=2(Tj),

Where: EER k=1(Tj) is the steady-state energy efficiency ratio of the test unit when operating at minimum compressor speed and temperature Tj, in Btu/h per W, calculated using capacity Q c k=1(Tj) calculated using Equation 4.1.4-1 to this appendix and electrical power consumption Ėc k=1(Tj) calculated using Equation 4.1.4-2 to this appendix; EER k=v(Tj) is the steady-state energy efficiency ratio of the test unit when operating at intermediate compressor speed and temperature Tj, in Btu/h per W, calculated using capacity Q c k=v(Tj) calculated using Equation 4.1.4-3 to this appendix and electrical power consumption Ėc k=v(Tj) calculated using Equation 4.1.4-4 to this appendix; EER k=2(Tj) is the steady-state energy efficiency ratio of the test unit when operating at full compressor speed and temperature Tj, Btu/h per W, calculated using capacity Q c k=2(Tj) and electrical power consumption Ėc k=2(Tj), both calculated as described in section 4.1.4 of this appendix; and BL(Tj) is the building cooling load at temperature Tj, Btu/h. 4.1.4.2.2 Variable-Speed Non-Communicating Coil-Only Air Conditioners or Heat Pumps

If the unit alternates between high (k=2) and low (k=1) compressor capacity to satisfy the building cooling load at temperature Tj, Q c k=1(Tj) < BL(Tj) < Q c k=2(Tj).

Where: the cooling mode, low capacity load factor for temperature bin j (dimensionless); and X k=2 (Tj)= 1 − X k=1 (Tj), the cooling mode, high capacity load factor for temperature bin j (demensionless). Obtain the fractional bin hours for the cooling season, nj/N, from Table 19 to this appendix. Obtain Q c k=1(Tj), Ėc k=1(Tj), Q c k=2(Tj), and Ėc k=2(Tj) as described in section 4.1.4 of this appendix.

4.1.4.3 Unit must operate continuously at full (k=2) compressor speed at temperature Tj, BL(Tj) ≥ Q ck=2(Tj). Evaluate the Equation 4.1-1 quantities

as specified in section 4.1.3.4 of this appendix with the understanding that Q ck=2(Tj) and E ck=2(Tj) correspond to full compressor speed operation and are derived from the results of the tests specified in section 3.2.4 of this appendix. 4.1.5 SEER2 Calculations for an Air Conditioner or Heat Pump Having a Single Indoor Unit With Multiple Indoor Blowers

Calculate SEER2 using Eq. 4.1-1, where qc(Tj)/N and ec(Tj)/N are evaluated as specified in the applicable subsection.

4.1.5.1 For Multiple Indoor Blower Systems That Are Connected to a Single, Single-Speed Outdoor Unit

a. Calculate the space cooling capacity, Q ck=1(Tj), and electrical power consumption, E ck=1(Tj), of the test unit when operating at the cooling minimum air volume rate and outdoor temperature Tj using the equations given in section 4.1.2.1 of this appendix. Calculate the space cooling capacity, Q ck=2(Tj), and electrical power consumption, E ck=2(Tj), of the test unit when operating at the cooling full-load air volume rate and outdoor temperature Tj using the equations given in section 4.1.2.1 of this appendix. In evaluating the section 4.1.2.1 equations, determine the quantities Q ck=1(82) and E ck=1(82) from the B1 test, Q ck=1(95) and E ck=1(95) from the Al test, Q ck=2(82) and E ck=2(82) from the B2 test, and Q ck=2(95) and E ck=2(95) from the A2 test. Evaluate all eight quantities as specified in section 3.3. Refer to section 3.2.2.1 and Table 6 for additional information on the four referenced laboratory tests.

b. Determine the cooling mode cyclic degradation coefficient, CD c, as per sections 3.2.2.1 and 3.5 to 3.5.3 of this appendix. Assign this same value to CD c(K=2).

c. Except for using the above values of Q ck=1(Tj), E ck=1(Tj), E ck=2(Tj), Q ck=2(Tj), CD c, and CD c (K=2), calculate the quantities qc(Tj)/N and ec(Tj)/N as specified in section 4.1.3.1 of this appendix for cases where Q ck=1(Tj) ≥ BL(Tj). For all other outdoor bin temperatures, Tj, calculate qc(Tj)/N and ec(Tj)/N as specified in section 4.1.3.3 of this appendix if Q ck=2(Tj) > BL (Tj) or as specified in section 4.1.3.4 of this appendix if Q ck=2(Tj) ≤ BL(Tj).

4.1.5.2 For Multiple Indoor Blower Systems That Are Connected to Either a Lone Outdoor Unit Having a Two-Capacity Compressor or Two Separate But Identical Model Single-Speed Outdoor Units. Calculate the Quantities qc(Tj)/N and ec(Tj)/N as Specified in Section 4.1.3 of This Appendix 4.2 Heating Seasonal Performance Factor 2 (HSPF2) Calculations

Unless an approved alternative efficiency determination method is used, as set forth in 10 Cspan 429.70(e). Calculate HSPF2 as follows: Six generalized climatic regions are depicted in Figure 1 and otherwise defined in Table 20. For each of these regions and for each applicable standardized design heating requirement, evaluate the heating seasonal performance factor using,

Where: eh(Tj)/N = The ratio of the electrical energy consumed by the heat pump during periods of the heating season when the outdoor temperature fell within the range represented by bin temperature Tj to the total number of hours in the heating season (N), W. For heat pumps having a heat comfort controller, this ratio may also include electrical energy used by resistive elements to maintain a minimum air delivery temperature (see 4.2.5). RH(Tj)/N = The ratio of the electrical energy used for resistive space heating during periods when the outdoor temperature fell within the range represented by bin temperature Tj to the total number of hours in the heating season (N), W. Except as noted in section 4.2.5 of this appendix, resistive space heating is modeled as being used to meet that portion of the building load that the heat pump does not meet because of insufficient capacity or because the heat pump automatically turns off at the lowest outdoor temperatures. For heat pumps having a heat comfort controller, all or part of the electrical energy used by resistive heaters at a particular bin temperature may be reflected in eh(Tj)/N (see section 4.2.5 of this appendix). Tj = the outdoor bin temperature, °F. Outdoor temperatures are “binned” such that calculations are only performed based one temperature within the bin. Bins of 5 °F are used. nj/N = Fractional bin hours for the heating season; the ratio of the number of hours during the heating season when the outdoor temperature fell within the range represented by bin temperature Tj to the total number of hours in the heating season, dimensionless. Obtain nj/N values from Table 20. j = the bin number, dimensionless. J = for each generalized climatic region, the total number of temperature bins, dimensionless. Referring to Table 20, J is the highest bin number (j) having a nonzero entry for the fractional bin hours for the generalized climatic region of interest. Fdef = the demand defrost credit described in section 3.9.2 of this appendix, dimensionless. BL(Tj) = the building space conditioning load corresponding to an outdoor temperature of Tj; the heating season building load also depends on the generalized climatic region's outdoor design temperature and the design heating requirement, Btu/h.

Table 20—Generalized Climatic Region Information

Region Number I II III IV V * VI Heating Load Hours, HLH4938571247170122021842 Outdoor Design Temperature, TOD3727175−1030 Heating Load Line Equation Slope Factor, C1.101.061.301.151.161.11 Variable-speed Slope Factor, CVS1.030.991.211.071.081.03 Zero-Load Temperature, Tzl585756555557 j Tj ( °F)Fractional Bin Hours, nj/N 1 62000000 2 57.23900000 3 52.194.163.138.103.086.215 4 47.129.143.137.093.076.204 5 42.081.112.135.100.078.141 6 37.041.088.118.109.087.076 7 32.019.056.092.126.102.034 8 27.005.024.047.087.094.008 9 22.001.008.021.055.074.003 10 170.002.009.036.0550 11 1200.005.026.0470 12 700.002.013.0380 13 200.001.006.0290 14 −3000.002.0180 15 −8000.001.0100 16 −130000.0050 17 −180000.0020 18 −230000.0010

* Pacific Coast Region.

Evaluate the building heating load using:

Where: Tj = the outdoor bin temperature, °F; Tzl = the zero-load temperature, °F, which varies by climate region according to Table 20 to this appendix; C = slope (adjustment) factor, which varies by climate region according to Table 20 to this appendix. When calculating building load for a variable-speed compressor system, substitute CVS for C; Qc(95 °F) = the cooling capacity at 95 °F determined from the A or A2 test, Btu/h. For heating-only heat pump units, replace Qc(95 °F) in Equation 4.2-2 with Qh(47 °F); Qh(47 °F) = the heating capacity at 47 °F determined from the H1 test for units having a single-speed compressor, H12 for units having a two-capacity compressor, and H1N test for units having a variable-speed compressor, Btu/h.

a. For all heat pumps, HSPF2 accounts for the heating delivered and the energy consumed by auxiliary resistive elements when operating below the balance point. This condition occurs when the building load exceeds the space heating capacity of the heat pump condenser. For HSPF2 calculations for all heat pumps, see either section 4.2.1, 4.2.2, 4.2.3, or 4.2.4 of this appendix, whichever applies.

b. For heat pumps with heat comfort controllers (see section 1.2 of this appendix, Definitions), HSPF2 also accounts for resistive heating contributed when operating above the heat-pump-plus-comfort-controller balance point as a result of maintaining a minimum supply temperature. For heat pumps having a heat comfort controller, see section 4.2.5 of this appendix for the additional steps required for calculating the HSPF2.

4.2.1 Additional Steps for Calculating the HSPF2 of a Blower Coil System Heat Pump Having a Single-Speed Compressor and Either a Fixed-Speed Indoor Blower or a Constant-Air-Volume-Rate Indoor Blower, or a Single-Speed Coil-Only System Heat Pump Where: whichever is less; the heating mode load factor for temperature bin j, dimensionless. Q h(Tj) = the space heating capacity of the heat pump when operating at outdoor temperature Tj, Btu/h. E h(Tj) = the electrical power consumption of the heat pump when operating at outdoor temperature Tj, W. δ(Tj) = the heat pump low temperature cut-out factor, dimensionless. PLFj = 1 − C Dh · [1 −X(Tj)] the part load factor, dimensionless.

Use Equation 4.2-2 to determine BL(Tj). Obtain fractional bin hours for the heating season, nj/N, from Table 20. Evaluate the heating mode cyclic degradation factor CDh as specified in section 3.8.1 of this appendix.

Determine the low temperature cut-out factor using

Where: Toff = the outdoor temperature when the compressor is automatically shut off, °F. (If no such temperature exists, Tj is always greater than Toff and Ton).

Ton = the outdoor temperature when the compressor is automatically turned back on, if applicable, following an automatic shut-off, °F.

If the H4 test is not conducted, calculate Qh(Tj) and Eh(Tj) using

where Q h(47) and E h(47) are determined from the H1 test and calculated as specified in section 3.7 of this appendix; Q h(35) and E h(35) are determined from the H2 test and calculated as specified in section 3.9.1 of this appendix; and Q h(17) and E h(17) are determined from the H3 test and calculated as specified in section 3.10 of this appendix.

If the H4 test is conducted, calculate Q h(Tj) and E h(Tj) using

where Q h(47) and E h(47) are determined from the H1 test and calculated as specified in section 3.7 of this appendix; Q h(35) and E h(35) are determined from the H2 test and calculated as specified in section 3.9.1 of this appendix; Q h(17) and E h(17) are determined from the H3 test and calculated as specified in section 3.10 of this appendix; Q h(5) and E h(5) are determined from the H4 test and calculated as specified in section 3.10 of this appendix. 4.2.2 Additional Steps for Calculating the HSPF2 of a Heat Pump Having a Single-Speed Compressor and a Variable-Speed, Variable-Air-Volume-Rate Indoor Blower

The manufacturer must provide information about how the indoor air volume rate or the indoor blower speed varies over the outdoor temperature range of 65 °F to −23 °F. Calculate the quantities

in Equation 4.2-1 as specified in section 4.2.1 of this appendix with the exception of replacing references to the H1C test and section 3.6.1 of this appendix with the H1C1 test and section 3.6.2 of this appendix. In addition, evaluate the space heating capacity and electrical power consumption of the heat pump Q h(Tj) and E h(Tj) using where the space heating capacity and electrical power consumption at low capacity (k=1) at outdoor temperature Tj are determined using

If the H42 test is not conducted, calculate the space heating capacity and electrical power consumption at high capacity (k=2) at outdoor temperature Tj using Equations 4.2.2-3 and 4.2.2-4 for k=2.

If the H42 test is conducted, calculate the space heating capacity and electrical power consumption at high capacity (k=2) at outdoor temperature Tj using Equations 4.2.2-5 and 4.2.2-6.

For units where indoor blower speed is the primary control variable, spanhk=1 denotes the fan speed used during the required H11 and H31 tests (see Table 12), spanhk=2 denotes the fan speed used during the required H12, H22, and H32 tests, and spanh(Tj) denotes the fan speed used by the unit when the outdoor temperature equals Tj. For units where indoor air volume rate is the primary control variable, the three spanh's are similarly defined only now being expressed in terms of air volume rates rather than fan speeds. Determine Q hk=1(47) and E hk=1(47) from the H11 test, and Q hk=2(47) and E hk=2(47) from the H12 test. Calculate all four quantities as specified in section 3.7 of this appendix. Determine Q hk=1(35) and E hk=1(35) as specified in section 3.6.2 of this appendix; determine Q hk=2(35) and E hk=2(35) and from the H22 test and the calculation specified in section 3.9 of this appendix. Determine Q hk=1(17) and E hk=1(17 from the H31 test, and Q hk=2(17) and E hk=2(17) from the H32 test. Calculate all four quantities as specified in section 3.10 of this appendix. Determine Q hk=2(5) and E hk=2(5) from the H42 test and the calculation specified in section 3.10 of this appendix.

4.2.3 Additional Steps for Calculating the HSPF2 of a Heat Pump Having a Two-Capacity Compressor

The calculation of the Equation 4.2-1 to this appendix quantities differ depending upon whether the heat pump would operate at low capacity (section 4.2.3.1 of this appendix), cycle between low and high capacity (section 4.2.3.2 of this appendix), or operate at high capacity (sections 4.2.3.3 and 4.2.3.4 of this appendix) in responding to the building load. For heat pumps that lock out low capacity operation at low outdoor temperatures, the outdoor temperature at which the unit locks out must be that specified by the manufacturer in the certification report so that the appropriate equations can be selected.

a. Evaluate the space heating capacity and electrical power consumption of the heat pump when operating at low compressor capacity and outdoor temperature Tj using

b. If the H42 test is not conducted, evaluate the space heating capacity and electrical power consumption (Q hk=2(Tj) and E hk=2 (Tj)) of the heat pump when operating at high compressor capacity and outdoor temperature Tj by solving Equations 4.2.2-3 and 4.2.2-4, respectively, for k=2. If the H42 test is conducted, evaluate the space heating capacity and electrical power consumption (Q hk=2(Tj) and E hk=2 (Tj)) of the heat pump when operating at high compressor capacity and outdoor temperature Tj using Equations 4.2.2-5 and 4.2.2-6, respectively.

Determine Q hk=1(62) and E hk=1(62) from the H01 test, Q hk=1(47) and E hk=1(47) from the H11 test, and Q hk=2(47) and E hk=2(47) from the H12 test. Calculate all six quantities as specified in section 3.7 of this appendix. Determine Q hk=2(35) and E hk=2(35) from the H22 test and, if required as described in section 3.6.3 of this appendix, determine Q hk=1(35) and E hk=1(35) from the H21 test. Calculate the required 35 °F quantities as specified in section 3.9 in this appendix. Determine Q hk=2(17) and E hk=2(17) from the H32 test and, if required as described in section 3.6.3 of this appendix, determine Q hk=1(17) and E hk=1(17) from the H31 test. Calculate the required 17 °F quantities as specified in section 3.10 of this appendix. Determine Q hk=2(5) and E hk=2(5) from the H42 test and the calculation specified in section 3.10 of this appendix.

4.2.3.1 Steady-State Space Heating Capacity When Operating at Low Compressor Capacity Is Greater Than or Equal to the Building Heating Load at Temperature Tj, Q hk=1(Tj) ≥BL(Tj) Where: Xk=1(Tj) = BL(Tj)/Q hk=1(Tj), the heating mode low capacity load factor for temperature bin j, dimensionless. PLFj = 1 − CDh · [ 1 − Xk=1(Tj) ], the part load factor, dimensionless. δ′(Tj) = the low temperature cutoff factor, dimensionless.

Evaluate the heating mode cyclic degradation factor CDh as specified in section 3.8.1 of this appendix.

Determine the low temperature cut-out factor using

where Toff and Ton are defined in section 4.2.1 of this appendix. Use the calculations given in section 4.2.3.3 of this appendix, and not the above, if:

a. The heat pump locks out low capacity operation at low outdoor temperatures and

b. Tj is below this lockout threshold temperature.

4.2.3.2 Heat Pump Alternates Between High (k=2) and Low (k=1) Compressor Capacity To Satisfy the Building Heating Load at a Temperature Tj, Q hk=1(Tj) BL(Tj) Q hk=2(Tj) Xk=2(Tj) = 1 − Xk=1(Tj) the heating mode, high capacity load factor for temperature bin j, dimensionless.

Determine the low temperature cut-out factor, δ′(Tj), using Equation 4.2.3-3.

4.2.3.3 Heat Pump Only Operates at High (k=2) Compressor Capacity at Temperature Tj and its Capacity Is Greater Than the Building Heating Load, BL(Tj) < Q hk=2(Tj). This Section Applies to Units That Lock Out Low Compressor Capacity Operation at Low Outdoor Temperatures where:

Xk=2(Tj)= BL(Tj)/Q hk=2(Tj). PLFj = 1 − C hD(k = 2) * [1 − Xk=2(Tj)]

If the H1C2 test described in section 3.6.3 and Table 13 of this appendix is not conducted, set CDh (k=2) equal to the default value specified in section 3.8.1 of this appendix.

Determine the low temperature cut-out factor, δ(Tj), using Equation 4.2.3-3.

4.2.3.4 Heat Pump Must Operate Continuously at High (k=2) Compressor Capacity at Temperature Tj, BL(Tj) ≥ Q h k=2(Tj) Where: 4.2.4 Additional Steps for Calculating the HSPF2 of a Heat Pump Having a Variable-Speed Compressor. Calculate HSPF2 Using Equation 4.2-1

a. Minimum Compressor Speed. For units other than variable-speed non-communicating coil-only heat pumps, evaluate the space heating capacity, Qh k=1(Tj), and electrical power consumption, Eh k=1(Tj), of the heat pump when operating at minimum compressor speed and outdoor temperature Tj using:

Where Qh k=1(62) and Eh k=1(62) are determined from the H01 test, Qh k=1(47) and Eh k=1(47) are determined from the H11 test, and all four quantities are calculated as specified in section 3.7 of this appendix.

For variable-speed non-communicating coil-only heat pumps, when Tj is greater than or equal to 47 °F, evaluate the space heating capacity, Q h k=1(Tj), and electrical power consumption, Ėh k=1(Tj), of the heat pump when operating at minimum compressor speed as described in Equations 4.2.4-1 and 4.2.4-2 to this appendix, respectively. When Tj is less than 47 °F, evaluate the space heating capacity, Q h k=1(Tj), and electrical power consumption, Ėh k=1(Tj) using:

And Where Q h k=1(47) and Ėh k=1(47) are determined from the H11 test, and both quantities are calculated as specified in section 3.7 of this appendix; Q h k=1(35) and Ėh k=1(35) are determined from the H21 test, and are calculated as specified in section 3.9 of this appendix; Q h k=1(17) and Ėh k=1(17) are determined from the H31 test, and are calculated as specified in section 3.10 of this appendix; and Q h k=2(Tj) and Ėh k=2(Tj) are calculated as described in section 4.2.4.c or 4.2.4.d of this appendix, as appropriate.

b. Minimum Compressor Speed for Minimum-speed-limiting Variable-speed Heat Pumps. For units other than variable-speed non-communicating coil-only heat pumps, evaluate the space heating capacity, Q h k=1(Tj), and electrical power consumption, Ėh k=1(Tj), of the heat pump when operating at minimum compressor speed and outdoor temperature Tj using:

And Where Q h k=1(62) and Ėh k=1(62) are determined from the H01 test, Q h k=1(47) and Ėh k=1(47) are determined from the H11 test, and all four quantities are calculated as specified in section 3.7 of this appendix; Q h k=v(35) and Ėh k=v(35) are determined from the H2v test and are calculated as specified in section 3.9 of this appendix; and Q h k=v(Tj) and Ėh k=v(Tj) are calculated using Equations 4.2.4-7 and 4.2.4-8 to this appendix, respectively.

For variable-speed non-communicating coil-only heat pumps, evaluate the space heating capacity, Q h k=1(Tj), and electrical power consumption, Ėh k=1(Tj), of the heat pump as described in section 4.2.4.a of this appendix, using Equations 4.2.4-1, 4.2.4-2, 4.2.4-3, and 4.2.4-4 to this appendix, as appropriate.

c. Full Compressor Speed for Heat Pumps for which the H42 test is not conducted. Evaluate the space heating capacity, Q h k=2(Tj), and electrical power consumption, Ėh k=2(Tj), of the heat pump when operating at full compressor speed and outdoor temperature Tj using:

And

Determine Q h k=N(47) and Ėh k=N(47) from the H1N test and the calculations specified in section 3.7 of this appendix. See section 3.6.4.b of this appendix regarding determination of the capacity Q hcalc k=2(47) and power input Ėhcacl k=2(47) used in the HSPF2 calculations to represent the H12 Test. Determine Q h k=2(35) and Ėh k=2(35) from the H22 test and the calculations specified in section 3.9 of this appendix or, if the H22 test is not conducted, by conducting the calculations specified in section 3.6.4 of this appendix. Determine Q h k=2(17) and Ėh k=2(17) from the H32 test and the methods specified in section 3.10 of this appendix.

d. Full Compressor Speed for Heat Pumps for which the H42 test is Conducted. For Tj above 17 °F, evaluate the space heating capacity, Q hk=2(Tj), and electrical power consumption, E hk=2(Tj), of the heat pump when operating at full compressor speed as described above for heat pumps for which the H42 is not conducted. For Tj between 5 °F and 17 °F, evaluate the space heating capacity, Q hk=2(Tj), and electrical power consumption, E hk=2(Tj), of the heat pump when operating at full compressor speed using the following equations:

Determine Q hk=2(17) and E hk=2(17) from the H32 test, and Q hk=2(5) and E hk=2(5) from the H42 test, using the methods specified in section 3.10 of this appendix for all four values. For Tj below 5 °F, evaluate the space heating capacity, Q hk=2(Tj), and electrical power consumption, E hk=2(Tj), of the heat pump when operating at full compressor speed using the following equations: Determine Q hcalck=2(47) and E hcalck=2(47) as described in section 3.6.4.b of this appendix. Determine Q hk=2(17) and E hk=2(17) from the H32 test, using the methods specified in section 3.10 of this appendix.

e. Intermediate Compressor Speed. For units other than variable-speed non-communicating coil-only heat pumps, calculate the space heating capacity, Q h k=v(Tj), and electrical power consumption, Ėh k=v(Tj), of the heat pump when operating at outdoor temperature Tj and the intermediate compressor speed used during the H2V test in section 3.6.4 of this appendix using:

Where Q h k=v(35) and Ėh k=v(35) are determined from the H2V test and calculated as specified in section 3.9 of this appendix. Approximate the slopes of the k=v intermediate speed heating capacity and electrical power input curves, MQ and ME, as follows:

Where:

Use Equations 4.2.4-1 and 4.2.4-2 to this appendix, respectively, to calculate Q h k=1(35) and Ėh k=1(35), whether or not the heat pump is a minimum-speed-limiting variable-speed heat pump.

For variable-speed non-communicating coil-only heat pumps, there is no intermediate speed.

4.2.4.1 Steady-State Space Heating Capacity When Operating at Minimum Compressor Speed is Greater Than or Equal to the Building Heating Load at Temperature Tj, Q h k=1(Tj ≥BL(Tj).

Evaluate the Equation 4.2-1 to this appendix quantities:

As specified in section 4.2.3.1 of this appendix. Except now use Equations 4.2.4-1 and 4.2.4-2 (for heat pumps that are not minimum-speed-limiting and are not variable-speed non-communicating coil-only heat pumps), Equations 4.2.4-1, 4.2.4-2, 4.2.4-3, and 4.2.4-4 as appropriate (for variable-speed non-communicating coil-only heat pumps), or Equations 4.2.4-5 and 4.2.4.-6 (for minimum-speed-limiting variable-speed heat pumps that are not variable-speed non-communicating coil-only heat pumps) to this appendix to evaluate Q h k=1(Tj) and Ėh k=1(Tj), respectively, and replace section 4.2.3.1 references to “low capacity” and section 3.6.3 of this appendix with “minimum speed” and section 3.6.4 of this appendix.

4.2.4.2 Heat Pump Operates at an Intermediate Compressor Speed (k = i) or, for a Variable-Speed Non-Communicating Coil-Only Heat Pump, Cycles Between High and Low Speeds, in Order to Match the Building Heating Load at a Temperature Tj, Q h k=1(Tj) < Q BL(Tj) < Q h k=2(Tj).

For units that are not variable-speed non-communicating coil-only heat pumps, calculate:

Where: And δ(Tj) is evaluated using Equation 4.2.3-3, while:

Q h k=i(Tj) = BL(Tj), the space heating capacity delivered by the unit in matching the building load at temperature (Tj), in Btu/h. The matching occurs with the heat pump operating at compressor speed k=i, and

COP k=i(Tj) = the steady-state coefficient of performance of the heat pump when operating at compressor speed k=i and temperature Tj (dimensionless). For each temperature bin where the heat pump operates at an intermediate compressor speed, determine COP k=i(Tj) using the following equations,

For each temperature bin where Q h k=1(Tj) < BL(Tj) < Q h k=v(Tj),

For each temperature bin where Q h k=v(Tj) ≤ BL(Tj) < Q h k=2(Tj),

Where: COPh k=1(Tj) is the steady-state coefficient of performance of the heat pump when operating at minimum compressor speed and temperature Tj, dimensionless, calculated using capacity Q h k=1(Tj) calculated using Equation 4.2.4-1 or 4.2.4-3 to this appendix and electrical power consumption Ėh k=1(Tj) calculated using Equation 4.2.4-2 or 4.2.4-4 to this appendix; COPh k=v(Tj) is the steady-state coefficient of performance of the heat pump when operating at intermediate compressor speed and temperature Tj, dimensionless, calculated using capacity Q h k=v(Tj) calculated using Equation 4.2.4-7 to this appendix and electrical power consumption Ėh k=v(Tj) calculated using Equation 4.2.4-8 to this appendix; COPh k=2(Tj) is the steady-state coefficient of performance of the heat pump when operating at full compressor speed and temperature Tj (dimensionless), calculated using capacity Q h k=2(Tj) and electrical power consumption Ėh k=2(Tj), both calculated as described in section 4.2.4 of this appendix; and BL(Tj) is the building heating load at temperature Tj, in Btu/h. 4.2.4.3 Heat Pump Must Operate Continuously at Full (k=2) Compressor Speed at Temperature Tj, BL(Tj) ≥Q hk=2(Tj). Evaluate the Equation 4.2-1 Quantities as specified in section 4.2.3.4 of this appendix with the understanding that Q hk=2(Tj) and E hk=2(Tj) correspond to full compressor speed operation and are derived from the results of the specified section 3.6.4 tests of this appendix. 4.2.5 Heat Pumps Having a Heat Comfort Controller

Heat pumps having heat comfort controllers, when set to maintain a typical minimum air delivery temperature, will cause the heat pump condenser to operate less because of a greater contribution from the resistive elements. With a conventional heat pump, resistive heating is only initiated if the heat pump condenser cannot meet the building load (i.e., is delayed until a second stage call from the indoor thermostat). With a heat comfort controller, resistive heating can occur even though the heat pump condenser has adequate capacity to meet the building load (i.e., both on during a first stage call from the indoor thermostat). As a result, the outdoor temperature where the heat pump compressor no longer cycles (i.e., starts to run continuously), will be lower than if the heat pump did not have the heat comfort controller.

4.2.5.1 Blower Coil System Heat Pump Having a Heat Comfort Controller: Additional Steps for Calculating the HSPF2 of a Heat Pump Having a Single-Speed Compressor and Either a Fixed-Speed Indoor Blower or a Constant-Air-Volume-Rate Indoor Blower Installed, or a Single-Speed Coil-Only System Heat Pump

Calculate the space heating capacity and electrical power of the heat pump without the heat comfort controller being active as specified in section 4.2.1 of this appendix (Equations 4.2.1-4 and 4.2.1-5) for each outdoor bin temperature, Tj, that is listed in Table 20. Denote these capacities and electrical powers by using the subscript “hp” instead of “h.” Calculate the mass flow rate (expressed in pounds-mass of dry air per hour) and the specific heat of the indoor air (expressed in Btu/lbmda · °F) from the results of the H1 test using:

where V s, V mx, v′n (or vn), and Wn are defined following Equation 3-1. For each outdoor bin temperature listed in Table 20, calculate the nominal temperature of the air leaving the heat pump condenser coil using,

Evaluate eh(Tj/N), RH(Tj)/N, X(Tj), PLFj, and δ(Tj) as specified in section 4.2.1 of this appendix. For each bin calculation, use the space heating capacity and electrical power from Case 1 or Case 2, whichever applies.

Case 1. For outdoor bin temperatures where To(Tj) is equal to or greater than TCC (the maximum supply temperature determined according to section 3.1.10 of this appendix), determine Q h(Tj) and E h(Tj) as specified in section 4.2.1 of this appendix (i.e., Q h(Tj) = Q hp(Tj) and E h(Tj) = E hp(Tj)).

Note:

Even though To(Tj) ≥Tcc, resistive heating may be required; evaluate Equation 4.2.1-2 for all bins.

Case 2. For outdoor bin temperatures where To(Tj) <TCC, determine Q h(Tj) and E h(Tj) using, Note:

Even though To(Tj) <Tcc, additional resistive heating may be required; evaluate Equation 4.2.1-2 for all bins.

4.2.5.2 Heat Pump Having a Heat Comfort Controller: Additional Steps for Calculating the HSPF2 of a Heat Pump Having a Single-Speed Compressor and a Variable-Speed, Variable-Air-Volume-Rate Indoor Blower

Calculate the space heating capacity and electrical power of the heat pump without the heat comfort controller being active as specified in section 4.2.2 of this appendix (Equations 4.2.2-1 and 4.2.2-2) for each outdoor bin temperature, Tj, that is listed in Table 20. Denote these capacities and electrical powers by using the subscript “hp” instead of “h.” Calculate the mass flow rate (expressed in pounds-mass of dry air per hour) and the specific heat of the indoor air (expressed in Btu/lbmda · °F) from the results of the H12 test using:

where V S, V mx, v′n (or vn), and Wn are defined following Equation 3-1. For each outdoor bin temperature listed in Table 20, calculate the nominal temperature of the air leaving the heat pump condenser coil using,

Evaluate eh(Tj)/N, RH(Tj)/N, X(Tj), PLFj, and δ(Tj) as specified in section 4.2.1 of this appendix with the exception of replacing references to the H1C test and section 3.6.1 of this appendix with the H1C1 test and section 3.6.2 of this appendix. For each bin calculation, use the space heating capacity and electrical power from Case 1 or Case 2, whichever applies.

Case 1. For outdoor bin temperatures where To(Tj) is equal to or greater than TCC (the maximum supply temperature determined according to section 3.1.10 of this appendix), determine Q h(Tj) and E h(Tj) as specified in section 4.2.2 of this appendix (i.e. Q h(Tj) = Q hp(Tj) and E h(Tj) = E hp(Tj)). Note: Even though To(Tj) ≥TCC, resistive heating may be required; evaluate Equation 4.2.1-2 for all bins.

Case 2. For outdoor bin temperatures where To(Tj) <TCC, determine Q h(Tj) and E h(Tj) using,

Note:

Even though To(Tj) <Tcc, additional resistive heating may be required; evaluate Equation 4.2.1-2 for all bins.

4.2.5.3 Heat Pumps Having a Heat Comfort Controller: Additional Steps for Calculating the HSPF2 of a Heat Pump Having a Two-Capacity Compressor

Calculate the space heating capacity and electrical power of the heat pump without the heat comfort controller being active as specified in section 4.2.3 of this appendix for both high and low capacity and at each outdoor bin temperature, Tj, that is listed in Table 20. Denote these capacities and electrical powers by using the subscript “hp” instead of “h.” For the low capacity case, calculate the mass flow rate (expressed in pounds-mass of dry air per hour) and the specific heat of the indoor air (expressed in Btu/lbmda · °F) from the results of the H11 test using:

where V s, V mx, v′n (or vn), and Wn are defined following Equation 3-1. For each outdoor bin temperature listed in Table 20, calculate the nominal temperature of the air leaving the heat pump condenser coil when operating at low capacity using,

Repeat the above calculations to determine the mass flow rate (m dak=2) and the specific heat of the indoor air (Cp,dak=2) when operating at high capacity by using the results of the H12 test. For each outdoor bin temperature listed in Table 20, calculate the nominal temperature of the air leaving the heat pump condenser coil when operating at high capacity using,

Evaluate eh(Tj)/N, RH(Tj)/N, Xk=1(Tj), and/or Xk=2(Tj), PLFj, and δ′(Tj) or δ″(Tj) as specified in section 4.2.3.1. 4.2.3.2, 4.2.3.3, or 4.2.3.4 of this appendix, whichever applies, for each temperature bin. To evaluate these quantities, use the low-capacity space heating capacity and the low-capacity electrical power from Case 1 or Case 2, whichever applies; use the high-capacity space heating capacity and the high-capacity electrical power from Case 3 or Case 4, whichever applies.

Case 1. For outdoor bin temperatures where Tok=1(Tj) is equal to or greater than TCC (the maximum supply temperature determined according to section 3.1.10 of this appendix), determine Q hk=1(Tj) and E hk=1(Tj) as specified in section 4.2.3 of this appendix (i.e., Q hk=1(Tj) = Q hpk=1(Tj) and E hk=1(Tj) = E hpk=1(Tj).

Note:

Even though Tok=1(Tj) ≥TCC, resistive heating may be required; evaluate RH(Tj)/N for all bins.

Case 2. For outdoor bin temperatures where To k=1(Tj) < TCC, determine Q h k=1(Tj) and E h k=1(Tj) using,

Q hk= 1(Tj) = Q hpk= 1(Tj) + Q CCk= 1(Tj) E hk= 1(Tj) = E hpk= 1(Tj) + E CCk= 1(Tj)

where,

Note:

Even though Tok=1(Tj) ≥Tcc, additional resistive heating may be required; evaluate RH(Tj)/N for all bins.

Case 3. For outdoor bin temperatures where Tok=2(Tj) is equal to or greater than TCC, determine Q hk=2(Tj) and E hk=2(Tj) as specified in section 4.2.3 of this appendix (i.e., Q hk=2(Tj) = Q hpk=2(Tj) and E hk=2(Tj) = E hpk=2(Tj)).

Note:

Even though Tok=2(Tj) <TCC, resistive heating may be required; evaluate RH(Tj)/N for all bins.

Case 4. For outdoor bin temperatures where Tok=2(Tj) <TCC, determine Q hk=2(Tj) and E hk=2(Tj) using,

Q hk= 2(Tj) = Q hpk= 2(Tj) + Q CCk= 2(Tj) E hk= 2(Tj) = E hpk= 2(Tj) + E CCk= 2(Tj)

where,

Note:

Even though Tok=2(Tj) Tcc, additional resistive heating may be required; evaluate RH(Tj)/N for all bins.

4.2.5.4 Heat Pumps Having a Heat Comfort Controller: Additional Steps for Calculating the HSPF2 of a Heat Pump Having a Variable-Speed Compressor [Reserved]

4.2.6 Additional Steps for Calculating the HSPF2 of a Heat Pump Having a Triple-Capacity Compressor

The only triple-capacity heat pumps covered are triple-capacity, northern heat pumps. For such heat pumps, the calculation of the Eq. 4.2-1 quantities

differ depending on whether the heat pump would cycle on and off at low capacity (section 4.2.6.1 of this appendix), cycle on and off at high capacity (section 4.2.6.2 of this appendix), cycle on and off at booster capacity (section 4.2.6.3 of this appendix), cycle between low and high capacity (section 4.2.6.4 of this appendix), cycle between high and booster capacity (section 4.2.6.5 of this appendix), operate continuously at low capacity (section 4.2.6.6 of this appendix), operate continuously at high capacity (section 4.2.6.7 of this appendix), operate continuously at booster capacity (section 4.2.6.8 of this appendix), or heat solely using resistive heating (also section 4.2.6.8 of this appendix) in responding to the building load. As applicable, the manufacturer must supply information regarding the outdoor temperature range at which each stage of compressor capacity is active. As an informative example, data may be submitted in this manner: At the low (k=1) compressor capacity, the outdoor temperature range of operation is 40 °F ≤ T ≤ 65 °F; At the high (k=2) compressor capacity, the outdoor temperature range of operation is 20 °F ≤ T ≤ 50 °F; At the booster (k=3) compressor capacity, the outdoor temperature range of operation is −20 °F ≤ T ≤ 30 °F.

a. Evaluate the space heating capacity and electrical power consumption of the heat pump when operating at low compressor capacity and outdoor temperature Tj using the equations given in section 4.2.3 of this appendix for Q hk=1(Tj) and E hk=1 (Tj)) In evaluating the section 4.2.3 equations, Determine Q hk=1(62) and E hk=1(62) from the H01 test, Q hk=1(47) and E hk=1(47) from the H11 test, and Q hk=2(47) and E hk=2(47) from the H12 test. Calculate all four quantities as specified in section 3.7 of this appendix. If, in accordance with section 3.6.6 of this appendix, the H31 test is conducted, calculate Q hk=1(17) and E hk=1(17) as specified in section 3.10 of this appendix and determine Q hk=1(35) and E hk=1(35) as specified in section 3.6.6 of this appendix.

b. Evaluate the space heating capacity and electrical power consumption (Q hk=2(Tj) and E hk=2 (Tj)) of the heat pump when operating at high compressor capacity and outdoor temperature Tj by solving Equations 4.2.2-3 and 4.2.2-4, respectively, for k=2. Determine Q hk=1(62) and E hk=1(62) from the H01 test, Q hk=1(47) and E hk=1(47) from the H11 test, and Q hk=2(47) and E hk=2(47) from the H12 test, evaluated as specified in section 3.7 of this appendix. Determine the equation input for Q hk=2(35) and E hk=2(35) from the H22,test evaluated as specified in section 3.9.1 of this appendix. Also, determine Q hk=2(17) and E hk=2(17) from the H32 test, evaluated as specified in section 3.10 of this appendix.

c. Evaluate the space heating capacity and electrical power consumption of the heat pump when operating at booster compressor capacity and outdoor temperature Tj using

Determine Q hk=3(17) and E hk=3(17) from the H33 test and determine Q hk=3(5) and E hk=3(5) from the H43 test. Calculate all four quantities as specified in section 3.10 of this appendix. Determine the equation input for Q hk=3(35) and E hk=3(35) as specified in section 3.6.6 of this appendix.

4.2.6.1 Steady-State Space Heating Capacity When Operating at Low Compressor Capacity Is Greater Than or Equal to the Building Heating Load at Temperature Tj, Q hk=1(Tj) ≥BL(Tj)., and the Heat Pump Permits Low Compressor Capacity at Tj. Evaluate the Quantities using Eqs. 4.2.3-1 and 4.2.3-2, respectively. Determine the equation inputs Xk=1(Tj), PLFj, and δ′(Tj) as specified in section 4.2.3.1. In calculating the part load factor, PLFj, use the low-capacity cyclic-degradation coefficient CDh, [or equivalently, CDh(k=1)] determined in accordance with section 3.6.6 of this appendix. 4.2.6.2 Heat Pump Only Operates at High (k=2) Compressor Capacity at Temperature Tj and Its Capacity Is Greater Than or Equal to the Building Heating Load, BL(Tj) ≤ Q hk=2(Tj)

Evaluate the quantities

as specified in section 4.2.3.3 of this appendix. Determine the equation inputs Xk=2(Tj), PLFj, and δ′(Tj) as specified in section 4.2.3.3 of this appendix. In calculating the part load factor, PLFj, use the high-capacity cyclic-degradation coefficient, CDh(k=2) determined in accordance with section 3.6.6 of this appendix. 4.2.6.3 Heat Pump Only Operates at Booster (k=3) Compressor Capacity at Temperature Tj and its Capacity Is Greater Than or Equal to the Building Heating Load, BL(Tj) ≤Q hk=3(Tj) Determine the low temperature cut-out factor, δ′(Tj), using Eq. 4.2.3-3. Use the booster-capacity cyclic-degradation coefficient, CDh(k=3) determined in accordance with section 3.6.6 of this appendix.

4.2.6.4 Heat Pump Alternates Between High (k=2) and Low (k=1) Compressor Capacity To Satisfy the Building Heating Load at a Temperature Tj, Q hk=1(Tj) <BL(Tj) <Q hk=2(Tj)

Evaluate the quantities

as specified in section 4.2.3.2 of this appendix. Determine the equation inputs Xk=1(Tj), Xk=2(Tj), and δ′(Tj) as specified in section 4.2.3.2 of this appendix.

4.2.6.5 Heat Pump Alternates Between High (k=2) and Booster (k=3) Compressor Capacity To Satisfy the Building Heating Load at a Temperature Tj, Q hk=2(Tj) <BL(Tj) <Q hk=3(Tj) and X k=3(Tj) = 1−X k=2(Tj) = the heating mode, booster capacity load factor for temperature bin j, dimensionless. Determine the low temperature cut-out factor, δ′(Tj), using Eq. 4.2.3-3. 4.2.6.6 Heat Pump Only Operates at Low (k=1) Capacity at Temperature Tj and Its Capacity Is Less Than the Building Heating Load, BL(Tj) > Q hk=1(Tj) where the low temperature cut-out factor, δ′(Tj), is calculated using Eq. 4.2.3-3.

4.2.6.7 Heat Pump Only Operates at High (k=2) Capacity at Temperature Tj and Its Capacity Is Less Than the Building Heating Load, BL(Tj) > Q hk=2(Tj)

Evaluate the quantities

as specified in section 4.2.3.4 of this appendix. Calculate δ″(Tj) using the equation given in section 4.2.3.4 of this appendix. 4.2.6.8 Heat Pump Only Operates at Booster (k=3) Capacity at Temperature Tj and Its Capacity Is Less Than the Building Heating Load, BL(Tj) > Q hk=3(Tj) or the System Converts To Using Only Resistive Heating

where δ″(Tj) is calculated as specified in section 4.2.3.4 of this appendix if the heat pump is operating at its booster compressor capacity. If the heat pump system converts to using only resistive heating at outdoor temperature Tj, set δ′(Tj) equal to zero.

4.2.7 Additional Steps for Calculating the HSPF2 of a Heat Pump Having a Single Indoor Unit With Multiple Indoor Blowers. The Calculation of the Eq. 4.2-1 Quantities eh(Tj)/N and RH(Tj)/N Are Evaluated as Specified in the Applicable Subsection

4.2.7.1 For Multiple Indoor Blower Heat Pumps That Are Connected to a Singular, Single-Speed Outdoor Unit

a. Calculate the space heating capacity, Q hk=1 (Tj), and electrical power consumption, E hk=1 (Tj), of the heat pump when operating at the heating minimum air volume rate and outdoor temperature Tj using Eqs. 4.2.2-3 and 4.2.2-4, respectively. Use these same equations to calculate the space heating capacity, Q hk=2 (Tj) and electrical power consumption, E hk=2 (Tj), of the test unit when operating at the heating full-load air volume rate and outdoor temperature Tj. In evaluating Eqs. 4.2.2-3 and 4.2.2- 4, determine the quantities Q hk=1(47) and E hk=1(47) from the H11 test; determine Q hk=2(47) and E hk=2(47) from the H12 test. Evaluate all four quantities according to section 3.7 of this appendix. Determine the quantities Q hk=1(35) and E hk=1(35) as specified in section 3.6.2 of this appendix. Determine Q hk=2(35) and E hk=2(35) from the H22 frost accumulation test as calculated according to section 3.9.1 of this appendix. Determine the quantities Q hk=1(17) and E hk=1(17) from the H31 test, and Q hk=2(17) and E hk=2(17) from the H32 test. Evaluate all four quantities according to section 3.10 of this appendix. Refer to section 3.6.2 and Table 12 of this appendix for additional information on the referenced laboratory tests.

b. Determine the heating mode cyclic degradation coefficient, CDh, as per sections 3.6.2 and 3.8 to 3.8.1 of this appendix. Assign this same value to CDh(k = 2).

c. Except for using the above values of Q hk=1(Tj), E hk=1(Tj), Q hk=2(Tj), E hk=2(Tj), CDh, and CDh(k = 2), calculate the quantities eh(Tj)/N as specified in section 4.2.3.1 of this appendix for cases where Q hk=1(Tj) ≥ BL(Tj). For all other outdoor bin temperatures, Tj, calculate eh(Tj)/N and RHh(Tj)/N as specified in section 4.2.3.3 of this appendix if Q hk=2(Tj) > BL(Tj) or as specified in section 4.2.3.4 of this appendix if Q hk=2(Tj) ≤ BL(Tj).

4.2.7.2 For Multiple Indoor Blower Heat Pumps Connected to Either a Single Outdoor Unit With a Two-Capacity Compressor or to Two Separate but Identical Model Single-Speed Outdoor Units. Calculate the Quantities eh(Tj)/N and RH(Tj)/N as Specified in Section 4.2.3 of This Appendix

4.3 Calculations of Off-Mode Power Consumption

For central air conditioners and heat pumps with a cooling capacity of: Less than 36,000 Btu/h, determine the off mode represented value, PW,OFF, with the following equation:

greater than or equal to 36,000 Btu/h, calculate the capacity scaling factor according to:

where, Q C(95) is the total cooling capacity at the A or A2 test condition, and determine the off mode represented value, PW,OFF, with the following equation:

4.4 Rounding of SEER2 and HSPF2 for Reporting Purposes

After calculating SEER2 according to section 4.1 of this appendix and HSPF2 according to section 4.2 of this appendix round the values off as specified per § 430.23(m) of title 10 of the Code of Federal Regulations.

Table 21—Representative Cooling and Heating Load Hours for Each Generalized Climatic Region

Climatic
region
Cooling
load hours
CLHR
Heating
load hours
HLHR
I2,400493 II1,800857 III1,2001,247 IV8001,701 Rating Values1,0001,572 V4002,202 VI2001,842
4.5 Calculations of the SHR, Which Should Be Computed for Different Equipment Configurations and Test Conditions Specified in Table 22.

Table 22—Applicable Test Conditions for Calculation of the Sensible Heat Ratio

Equipment configuration Reference
table number of
Appendix M
SHR computation with results from Computed values Units Having a Single-Speed Compressor and a Fixed-Speed Indoor Blower, a Constant Air Volume Rate Indoor Blower, or Single-Speed Coil-Only4B TestSHR(B). Units Having a Single-Speed Compressor That Meet the section 3.2.2.1 Indoor Unit Requirements5B2 and B1 TestsSHR(B1), SHR(B2). Units Having a Two-Capacity Compressor6B2 and B1 TestsSHR(B1), SHR(B2). Units Having a Variable-Speed Compressor7B2 and B1 TestsSHR(B1), SHR(B2).

The SHR is defined and calculated as follows:

Where both the total and sensible cooling capacities are determined from the same cooling mode test and calculated from data collected over the same 30-minute data collection interval.

4.6 Calculations of the Energy Efficiency Ratio (EER)

Calculate the energy efficiency ratio using,

where Q ck(T) and E ck(T) are the space cooling capacity and electrical power consumption determined from the 30-minute data collection interval of the same steady-state wet coil cooling mode test and calculated as specified in section 3.3 of this appendix. Add the letter identification for each steady-state test as a subscript (e.g., EERA2) to differentiate among the resulting EER values. The represented value of EER is determined from the A or A2 test, whichever is applicable. The represented value of EER determined in accordance with this appendix is called EER2. [82 span 1533, Jan. 5, 2017, as amended at 86 span 68394, Dec. 2, 2021; 87 span 64588, Oct. 25, 2022; 87 span 66935, Nov. 7, 2022]

Appendix N - Appendix N to Subpart B of Part 430—Uniform Test Method for Measuring the Energy Consumption of Consumer Furnaces Other Than Boilers

0. Incorporation by Reference

DOE incorporated by reference in § 430.3, the entire standards for ASTM D2156R13 and IEC 62301. DOE also incorporated selected provisions of ASHRAE 103-1993.

1. Scope. The scope of this appendix is as specified in section 2 of ASHRAE 103-1993 as it pertains to furnaces other than low pressure steam or hot water boilers or to electric boilers. Low pressure steam or hot water boilers and electric boilers are addressed in appendix EE of this subpart.

2. Definitions. Definitions include those specified in section 3 of ASHRAE 103-1993 and the following additional and modified definitions.

Active mode means the condition in which the furnace is connected to the power source, and at least one of the burner, electric resistance elements, or any electrical auxiliaries such as blowers, are activated.

Control means a device used to regulate the operation of a piece of equipment and the supply of fuel, electricity, air, or water.

Draft inducer means a fan incorporated in the furnace that either draws or forces air into the combustion chamber.

Gas valve means an automatic or semi-automatic device consisting essentially of a valve and operator that controls the gas supply to the burner(s) during normal operation of an appliance. The operator may be actuated by application of gas pressure on a flexible diaphragm, by electrical means, by mechanical means or by other means.

Installation and operation (I&O) manual means instructions for installing, commissioning, and operating the furnace, which are supplied with the product when shipped by the manufacturer.

Isolated combustion system means a system where a unit is installed within the structure, but isolated from the heated space. A portion of the jacket heat from the unit is lost, and air for ventilation, combustion and draft control comes from outside the heated space.

Multi-position furnace means a furnace that can be installed in more than one airflow configuration (i.e., upflow or horizontal; downflow or horizontal; upflow or downflow; and upflow, or downflow, or horizontal).

Off mode means a mode in which the furnace is connected to a mains power source and is not providing any active mode or standby mode function, and where the mode may persist for an indefinite time. The existence of an off switch in off position (a disconnected circuit) is included within the classification of off mode.

Off switch means the switch on the furnace that, when activated, results in a measurable change in energy consumption between the standby and off modes.

Oil control valve means an automatically or manually operated device consisting of an oil valve for controlling the fuel supply to a burner to regulate burner input.

Standby mode means any mode in which the furnace is connected to a mains power source and offers one or more of the following space heating functions that may persist:

(a) Activation of other modes (including activation or deactivation of active mode) by remote switch (including thermostat or remote control), internal or external sensors, and/or timer; and

(b) Continuous functions, including information or status displays or sensor-based functions.

Thermal stack damper means a type of stack damper that relies exclusively upon the changes in temperature in the stack gases to open or close the damper.

3. Classifications. Classifications are as specified in section 4 of ASHRAE 103-1993 for furnaces.

4. Requirements. Requirements are as specified in section 5 of ASHRAE 103-1993 for furnaces.

5. Instruments. Instruments must be as specified in section 6 of ASHRAE 103-1993.

6. Apparatus. The apparatus used in conjunction with the furnace during the testing must be as specified in section 7 of ASHRAE 103-1993 (except for the excluded sub-sections as enumerated at § 430.3(g)(15)); and as specified in sections 6.1 through 6.5 of this appendix.

6.1 General.

(a) Install the furnace in the test room in accordance with the I&O manual, as defined in section 2.6 of this appendix, except that if provisions within this appendix are specified, then the provisions herein drafted and prescribed by DOE govern. If the I&O manual and any additional provisions of this appendix are not sufficient for testing a furnace, the manufacturer must request a waiver from the test procedure pursuant to § 430.27.

(b) If the I&O manual indicates the unit should not be installed with a return duct, then the return (inlet) duct specified in section 7.2.1 of ASHRAE 103-1993 is not required.

(c) Test multi-position furnaces in the least efficient configuration. Testing of multi-position furnaces in other configurations is permitted if energy use or efficiency is represented pursuant to the requirements in 10 CFR part 429.

(d) The apparatuses described in section 6 of this appendix are used in conjunction with the furnace during testing. Each piece of apparatus shall conform to material and construction specifications listed in this appendix and in ASHRAE 103-1993, and the reference standards cited in this appendix and in ASHRAE 103-1993.

(e) Test rooms containing equipment must have suitable facilities for providing the utilities (including but not limited to environmental controls, applicable measurement equipment, and any other technology or tools) necessary for performance of the test and must be able to maintain conditions within the limits specified in section 6 of this appendix.

6.2 Forced-air central furnaces (direct vent and direct exhaust).

(a) Units not equipped with a draft hood or draft diverter must be provided with the minimum-length vent configuration recommended in the I&O manual or a 5-ft flue pipe if there is no recommendation provided in the I&O manual (see Figure 4 of ASHRAE 103-1993). For a direct exhaust system, insulate the minimum-length vent configuration or the 5-ft flue pipe with insulation having an R-value not less than 7 and an outer layer of aluminum foil. For a direct vent system, see section 7.5 of ASHRAE 103-1993 for insulation requirements.

(b) For units with power burners, cover the flue collection box with insulation having an R-value of not less than 7 and an outer layer of aluminum foil before the cool-down and heat-up tests described in sections 9.5 and 9.6 of ASHRAE 103-1993, respectively. However, do not apply the insulation for the jacket loss test (if conducted) described in section 8.6 of ASHRAE 103-1993 or the steady-state test described in section 9.1 of ASHRAE 103-1993.

(c) For power-vented units, insulate the shroud surrounding the blower impeller with insulation having an R-value of not less than 7 and an outer layer of aluminum foil before the cool-down and heat-up tests described in sections 9.5 and 9.6, respectively, of ASHRAE 103-1993. However, do not apply the insulation for the jacket loss test (if conducted) described in section 8.6 of ASHRAE 103-1993 or the steady-state test described in section 9.1 of ASHRAE 103-1993. Do not insulate the blower motor or block the airflow openings that facilitate the cooling of the combustion blower motor or bearings.

6.3 Downflow furnaces. Install an internal section of vent pipe the same size as the flue collar for connecting the flue collar to the top of the unit, if not supplied by the manufacturer. However, do not insulate the internal vent pipe during the jacket loss test (if conducted) described in section 8.6 of ASHRAE 103-1993 or the steady-state test described in section 9.1 of ASHRAE 103-1993. Do not insulate the internal vent pipe before the cool-down and heat-up tests described in sections 9.5 and 9.6, respectively, of ASHRAE 103-1993. If the vent pipe is surrounded by a metal jacket, do not insulate the metal jacket. Install a 5-ft test stack of the same cross-sectional area or perimeter as the vent pipe above the top of the furnace. Tape or seal around the junction connecting the vent pipe and the 5-ft test stack. Insulate the 5-ft test stack with insulation having an R-value not less than 7 and an outer layer of aluminum foil. (See Figure 3-E of ASHRAE 103-1993.)

6.4 Units with draft hoods or draft diverters. Install the stack damper in accordance with the I&O manual. Install 5 feet of stack above the damper.

(a) For units with an integral draft diverter, cover the 5-ft stack with insulation having an R-value of not less than 7 and an outer layer of aluminum foil.

(b) For units with draft hoods, insulate the flue pipe between the outlet of the furnace and the draft hood with insulation having an R-value of not less than 7 and an outer layer of aluminum foil.

(c) For units with integral draft diverters that are mounted in an exposed position (not inside the overall unit cabinet), cover the diverter boxes (excluding any openings through which draft relief air flows) before the beginning of any test (including jacket loss test) with insulation having an R-value of not less than 7 and an outer layer of aluminum foil.

(d) For units equipped with integral draft diverters that are enclosed within the overall unit cabinet, insulate the draft diverter box with insulation as described in section 6.4.c before the cool-down and heat-up tests described in sections 9.5 and 9.6, respectively, of ASHRAE 103-1993. However, do not apply the insulation for the jacket loss test (if conducted) described in section 8.6 of ASHRAE 103-1993 or the steady-state test described in section 9.1 of ASHRAE 103-1993.

6.5 Condensate collection. Attach condensate drain lines to the unit as specified in the I&O manual. Maintain a continuous downward slope of drain lines from the unit. Additional precautions (such as eliminating any line configuration or position that would otherwise restrict or block the flow of condensate or checking to ensure a proper connection with condensate drain spout that allows for unobstructed flow) must be taken to facilitate uninterrupted flow of condensate during the test. Collection containers must be glass or polished stainless steel to facilitate removal of interior deposits. The collection container must have a vent opening to the atmosphere.

7. Testing conditions. The testing conditions must be as specified in section 8 of ASHRAE 103-1993 (except for the excluded sub-sections as enumerated at § 430.3(g)(15)); and as specified in sections 7.1 to 7.9 of this appendix, respectively.

7.1 Fuel supply, gas. In conducting the tests specified herein, gases with characteristics as shown in Table 1 of ASHRAE 103-1993 shall be used. Maintain the gas supply, ahead of all controls for a furnace, at a test pressure between the normal and increased values shown in Table 1 of ASHRAE 103-1993. Maintain the regulator outlet pressure at a level approximating that recommended in the I&O manual, as defined in section 2.6 of this appendix, or, in the absence of such recommendation, to the nominal regulator settings used when the product is shipped by the manufacturer. Use a gas having a specific gravity as shown in Table 1 of ASHRAE 103-1993 and with a higher heating value within ±5% of the higher heating value shown in Table 1 of ASHRAE 103-1993. Determine the actual higher heating value in Btu per standard cubic foot for the gas to be used in the test within an error no greater than 1%.

7.2 Gas burner. Adjust the burners of gas-fired furnaces to their maximum Btu input ratings at the normal test pressure specified by section 7.1 of this appendix. Correct the burner input rate to reflect gas characteristics at a temperature of 60 °F and atmospheric pressure of 30 in of Hg and adjust down to within ±2 percent of the hourly Btu nameplate input rating specified by the manufacturer as measured during the steady-state performance test in section 8 of this appendix. Set the primary air shutters in accordance with the I&O manual to give a good flame at this condition. If, however, the setting results in the deposit of carbon on the burners during any test specified herein, the tester shall adjust the shutters and burners until no more carbon is deposited and shall perform the tests again with the new settings (see Figure 9 of ASHRAE 103-1993). After the steady-state performance test has been started, do not make additional adjustments to the burners during the required series of performance tests specified in section 9 of ASHRAE 103-1993. If a vent-limiting means is provided on a gas pressure regulator, keep it in place during all tests.

7.3 Modulating gas burner adjustment at reduced input rate. For gas-fired furnaces equipped with modulating-type controls, adjust the controls to operate the unit at the nameplate minimum input rate. If the modulating control is of a non-automatic type, adjust the control to the setting recommended in the I&O manual. In the absence of such recommendation, the midpoint setting of the non-automatic control shall be used as the setting for determining the reduced fuel input rate. Start the furnace by turning the safety control valve to the “ON” position.

7.4 Oil burner. Adjust the burners of oil-fired furnaces to give a CO2 reading specified in the I&O manual and an hourly Btu input during the steady-state performance test described in section 8 of this appendix. Ensure the hourly BTU input is within ±2% of the normal hourly Btu input rating as specified in the I&O manual. Smoke in the flue may not exceed a No. 1 smoke during the steady-state performance test as measured by the procedure in ASTM D2156R13). Maintain the average draft over the fire and in the flue during the steady-state performance test at the value specified in the I&O manual. Do not allow draft fluctuations exceeding 0.005 in. water. Do not make additional adjustments to the burner during the required series of performance tests. The instruments and measuring apparatus for this test are described in section 6 of this appendix and shown in Figure 8 of ASHRAE 103-1993.

7.5 Temperature Rise Targets. Adjust air throughputs to achieve a temperature rise that is the higher of a and b, below, unless c applies. A tolerance of ±2 °F is permitted.

(a) 15 °F less than the nameplate maximum temperature rise or

(b) 15 °F higher than the minimum temperature rise specified in the I&O manual.

(c) A furnace with a non-adjustable air temperature rise range and an automatically controlled airflow that does not permit a temperature rise range of 30 °F or more must be tested at the midpoint of the rise range.

7.6 Temperature Rise Adjustments. Establish the temperature rise specified in section 7.5 of this appendix by adjusting the circulating airflow. This adjustment must be accomplished by symmetrically restricting the outlet air duct and varying blower speed selection to obtain the desired temperature rise and minimum external static pressure, as specified in Table 4 of ASHRAE 103-1993. If the required temperature rise cannot be obtained at the minimum specified external static pressure by adjusting blower speed selection and duct outlet restriction, then the following applies.

(a) If the resultant temperature rise is less than the required temperature rise, vary the blower speed by gradually adjusting the blower voltage so as to maintain the minimum external static pressure listed in Table 4 of ASHRAE 103-1993. The airflow restrictions shall then remain unchanged. If static pressure must be varied to prevent unstable blower operation, then increase the static pressure until blower operation is stabilized, except that the static pressure must not exceed the maximum external static pressure as specified by the manufacturer in the I&O manual.

(b) If the resultant temperature rise is greater than the required temperature rise, then the unit can be tested at a higher temperature rise value, but one not greater than nameplate maximum temperature rise. In order not to exceed the maximum temperature rise, the speed of a direct-driven blower may be increased by increasing the circulating air blower motor voltage.

7.7 Measurement of jacket surface temperature. Divide the jacket of the furnace into 6-inch squares when practical, and otherwise into 36-square-inch regions comprising 4-inch by 9-inch or 3-inch by 12-inch sections, and determine the surface temperature at the center of each square or section with a surface thermocouple. Record the surface temperature of the 36-square-inch areas in groups where the temperature differential of the 36-square-inch areas is less than 10 °F for temperature up to 100 °F above room temperature, and less than 20 °F for temperatures more than 100 °F above room temperature. For forced-air central furnaces, the circulating air blower compartment is considered as part of the duct system, and no surface temperature measurement of the blower compartment needs to be recorded for the purpose of this test. For downflow furnaces, measure all cabinet surface temperatures of the heat exchanger and combustion section, including the bottom around the outlet duct and the burner door, using the 36-square-inch thermocouple grid. The cabinet surface temperatures around the blower section do not need to be measured (See Figure 3-E of ASHRAE 103-1993).

7.8 Installation of vent system. Keep the vent or air intake system supplied by the manufacturer in place during all tests. Test units intended for installation with a variety of vent pipe lengths with the minimum vent length as specified in the I&O manual, or a 5-ft. flue pipe if there are no recommendations in the I&O manual. Do not connect a furnace employing a direct vent system to a chimney or induced-draft source. Vent combustion products solely by using the venting incorporated in the furnace and the vent or air intake system supplied by the manufacturer. For units that are not designed to significantly preheat the incoming air, see section 7.4 of this appendix and Figure 4a or 4b of ASHRAE 103-1993. For units that do significantly preheat the incoming air, see Figure 4c or 4d of ASHRAE 103-1993.

7.9 Additional optional method of testing for determining DP and DF for furnaces. On units whose design is such that there is no measurable airflow through the combustion chamber and heat exchanger when the burner(s) is (are) off as determined by the optional test procedure in section 7.9.1 of this appendix, DF and DP may be set equal to 0.05.

7.9.1 Optional test method for indicating the absence of flow through the heat exchanger. Manufacturers may use the following test protocol to determine whether air flows through the combustion chamber and heat exchanger when the burner(s) is (are) off. The minimum default draft factor may be used only for units determined pursuant to this protocol to have no airflow through the combustion chamber and heat exchanger.

7.9.1.1 Test apparatus. Use a smoke stick that produces smoke that is easily visible and has a density less than or approximately equal to air. Use a smoke stick that produces smoke that is non-toxic to the test personnel and produces gas that is unreactive with the environment in the test chamber.

7.9.1.2 Test conditions. Minimize all air currents and drafts in the test chamber, including turning off ventilation if the test chamber is mechanically ventilated. Wait at least two minutes following the termination of the furnace on-cycle before beginning the optional test method for indicating the absence of flow through the heat exchanger.

7.9.1.3 Location of the test apparatus. After all air currents and drafts in the test chamber have been eliminated or minimized, position the smoke stick based on the following equipment configuration:

(a) For horizontal combustion air intakes, approximately 4 inches from the vertical plane at the termination of the intake vent and 4 inches below the bottom edge of the combustion air intake; or

(b) for vertical combustion air intakes, approximately 4 inches horizontal from vent perimeter at the termination of the intake vent and 4 inches down (parallel to the vertical axis of the vent).

7.9.1.4 Duration of test. Establish the presence of smoke from the smoke stick and then monitor the direction of the smoke flow for no less than 30 seconds.

7.9.1.5 Test results. During visual assessment, determine whether there is any draw of smoke into the combustion air intake vent.

(a) If absolutely no smoke is drawn into the combustion air intake, the furnace meets the requirements to allow use of the minimum default draft factor pursuant to section 7.9 of this appendix.

(b) If there is any smoke drawn into the intake, proceed with the methods of testing as prescribed in section 8.8 of ASHRAE 103-1993.

8. Test procedure. Conduct testing and measurements as specified in section 9 of ASHRAE 103-1993 (except for the excluded sub-sections as enumerated at § 430.3(g)(15)); and as specified in sections 8.1 through 8.10 of this appendix. Section 8.4 of this appendix may be used in lieu of section 9.2 of ASHRAE 103-1993.

8.1 Fuel input. For gas units, measure and record the steady-state gas input rate in Btu/hr, including pilot gas, corrected to standard conditions of 60 °F and 30 in. Hg. Use measured values of gas temperature and pressure at the meter and barometric pressure to correct the metered gas flow rate to the above standard conditions. For oil units, measure and record the steady-state fuel input rate.

8.2 Electrical input. During the steady-state test, perform a single measurement of all of the electrical power involved in burner operation (PE), including energizing the ignition system, controls, gas valve or oil control valve, and draft inducer, if applicable.

During the steady-state test, perform a single measurement of the electrical power to the circulating air blower (BE).

8.3 Input to interrupted ignition device. For burners equipped with an interrupted ignition device, record the nameplate electric power used by the ignition device, PEIG, or record that PEIG = 0.4 kW if no nameplate power input is provided. Record the nameplate ignition device on-time interval, tIG, or, if the nameplate does not provide the ignition device on-time interval, measure the on-time interval with a stopwatch at the beginning of the test, starting when the burner is turned on. Set tIG = 0 and PEIG = 0 if the device on-time interval is less than or equal to 5 seconds after the burner is on.

8.4 Optional test procedures for condensing furnaces, measurement of condensate during the establishment of steady-state conditions. For units with step-modulating or two-stage controls, conduct the test at both the maximum and reduced inputs. In lieu of collecting the condensate immediately after the steady state conditions have been reached as required by section 9.2 of ASHRAE 103-1993, condensate may be collected during the establishment of steady state conditions as defined by section 9.1.2.1 of ASHRAE 103-1993. Perform condensate collection for at least 30 minutes. Measure condensate mass immediately at the end of the collection period to prevent evaporation loss from the sample. Record fuel input for the 30-minute condensate collection test period. Observe and record fuel higher heating value (HHV), temperature, and pressures necessary for determining fuel energy input (Qc,ss). Measure the fuel quantity and HHV with errors no greater than 1%. The humidity for the room air shall at no time exceed 80%. Determine the mass of condensate for the establishment of steady state conditions (Mc,ss) in pounds by subtracting the tare container weight from the total container and condensate weight measured at the end of the 30-minute condensate collection test period.

8.5 Cool-down test for gas- and oil-fueled gravity and forced-air central furnaces without stack dampers. Turn off the main burner after completing steady-state testing, and measure the flue gas temperature by means of the thermocouple grid described in section 7.6 of ASHRAE 103-1993 at 1.5 minutes (TF,OFF(t3)) and 9 minutes (TF,OFF(t4)) after shutting off the burner. When taking these temperature readings, the integral draft diverter must remain blocked and insulated, and the stack restriction must remain in place. On atmospheric systems with an integral draft diverter or draft hood and equipped with either an electromechanical inlet damper or an electromechanical flue damper that closes within 10 seconds after the burner shuts off to restrict the flow through the heat exchanger in the off-cycle, bypass or adjust the control for the electromechanical damper so that the damper remains open during the cool-down test.

For furnaces that employ post-purge, measure the length of the post-purge period with a stopwatch. Record the time from burner “OFF” to combustion blower “OFF” (electrically de-energized) as tP. If the measured tP is less than or equal to 30 seconds, set tP at 0 and conduct the cool-down test as if there is no post-purge. If tP is prescribed by the I&O manual or measured to be greater than 180 seconds, stop the combustion blower at 180 seconds and use that value for tP. Measure the flue gas temperature by means of the thermocouple grid described in section 7.6 of ASHRAE 103-1993 at the end of the post-purge period, tP(TF,OFF (tP)), and at the time (1.5 + tP) minutes (TF,OFF(t3)) and (9.0 + tP) minutes (TF,OFF(t4)) after the main burner shuts off.

8.6 Cool-down test for gas- and oil-fueled gravity and forced-air central furnaces without stack dampers and with adjustable fan control. For a furnace with adjustable fan control, measure the time delay between burner shutdown and blower shutdown, t +. This time delay, t +, will be 3.0 minutes for non-condensing furnaces or 1.5 minutes for condensing furnaces or until the supply air temperature drops to a value of 40 °F above the inlet air temperature, whichever results in the longest fan on-time. For a furnace without adjustable fan control or with the type of adjustable fan control whose range of adjustment does not allow for the time delay, t +, specified above, bypass the fan control and manually control the fan to allow for the appropriate delay time as specified in section 9.5.1.2 of ASHRAE 103-1993. For a furnace that employs a single motor to drive both the power burner and the indoor air circulating blower, the power burner and indoor air circulating blower must be stopped at the same time.

8.7 [Reserved]

8.8 Calculation options. The rate of the flue gas mass flow through the furnace and the factors DP, DF, and DS are calculated by the equations in sections 11.6.1, 11.6.2, 11.6.3, 11.6.4, 11.7.1, and 11.7.2 of ASHRAE 103-1993. On units whose design is such that there is no measurable airflow through the combustion chamber and heat exchanger when the burner(s) is (are) off (as determined by the optional test procedure in section 7.9 of this appendix), DF and DP may be set equal to 0.05.

8.9 Optional test procedures for condensing furnaces that have no off-period flue losses. For units that have applied the test method in section 7.9 of this appendix to determine that no measurable airflow exists through the combustion chamber and heat exchanger during the burner off-period and having post-purge periods of less than 5 seconds, the cool-down and heat-up tests specified in sections 9.5 and 9.6 of ASHRAE 103-1993 may be omitted. In lieu of conducting the cool-down and heat-up tests, the tester may use the losses determined during the steady-state test described in section 9.1 of ASHRAE 103-1993 when calculating heating seasonal efficiency, EffyHS.

8.10 Measurement of electrical standby and off mode power.

8.10.1 Standby power measurement. With all electrical auxiliaries of the furnace not activated, measure the standby power (PW,SB) in accordance with the procedures in IEC 62301, except that section 8.5, Room Ambient Temperature, of ASHRAE 103-1993 and the voltage provision of section 8.2.1.4, Electrical Supply, of ASHRAE 103-1993 shall apply in lieu of the corresponding provisions of IEC 62301 at section 4.2, Test room, and the voltage specification of section 4.3, Power supply. Frequency shall be 60Hz. Clarifying further, IEC 62301 section 4.4, Power measurement instruments, and Section 5, Measurements, apply in lieu of ASHRAE 103-1993 section 6.10, Energy Flow Rate. Measure the wattage so that all possible standby mode wattage for the entire appliance is recorded, not just the standby mode wattage of a single auxiliary. Round the recorded standby power (PW,SB) to the second decimal place, except for loads greater than or equal to 10W, which must be recorded to at least three significant figures.

8.10.2 Off mode power measurement. If the unit is equipped with an off switch or there is an expected difference between off mode power and standby mode power, measure off mode power (PW,OFF) in accordance with the standby power procedures in IEC 62301, except that section 8.5, Room Ambient Temperature, of ASHRAE 103-1993 and the voltage provision of section 8.2.1.4, Electrical Supply, of ASHRAE 103-1993 shall apply in lieu of the corresponding provisions of IEC 62301 at section 4.2, Test room, and the voltage specification of section 4.3, Power supply. Frequency shall be 60Hz. Clarifying further, IEC 62301 section 4.4, Power measurement instruments, and section 5, Measurements, apply for this measurement in lieu of ASHRAE 103-1993 section 6.10, Energy Flow Rate. Measure the wattage so that all possible off mode wattage for the entire appliance is recorded, not just the off mode wattage of a single auxiliary. If there is no expected difference in off mode power and standby mode power, let PW,OFF = PW,SB, in which case no separate measurement of off mode power is necessary. Round the recorded off mode power (PW,OFF) to the second decimal place, except for loads greater than or equal to 10W, in which case round the recorded value to at least three significant figures.

9. Nomenclature. Nomenclature includes the nomenclature specified in section 10 of ASHRAE 103-1993 and the following additional variables:

Effmotor = Efficiency of power burner motor PEIG = Electrical power to the interrupted ignition device, kW RT,a = RT,F if flue gas is measured = RT,S if stack gas is measured RT,F = Ratio of combustion air mass flow rate to stoichiometric air mass flow rate RT,S = Ratio of the sum of combustion air and relief air mass flow rate to stoichiometric air mass flow rate tIG = Electrical interrupted ignition device on-time, min. Ta,SS,X = TF,SS,X if flue gas temperature is measured, °F = TS,SS,X if stack gas temperature is measured, °F yIG = Ratio of electrical interrupted ignition device on-time to average burner on-time yP = Ratio of power burner combustion blower on-time to average burner on-time ESO = Average annual electric standby mode and off mode energy consumption, in kilowatt-hours PW,OFF = Furnace off mode power, in watts PW,SB = Furnace standby mode power, in watts

10. Calculation of derived results from test measurements. Perform calculations as specified in section 11 of ASHRAE 103-1993 (except for the excluded sub-sections as enumerated at § 430.3(g)(15)); and as specified in sections 10.1 through 10.11 and Figure 1 of this appendix.

10.1 Annual fuel utilization efficiency. The annual fuel utilization efficiency (AFUE) is as defined in sections 11.2.12 (non-condensing systems), 11.3.12 (condensing systems), 11.4.12 (non-condensing modulating systems) and 11.5.12 (condensing modulating systems) of ASHRAE 103-1993, except for the definition for the term EffyHS in the defining equation for AFUE. EffyHS is defined as:

EffyHS = heating seasonal efficiency as defined in sections 11.2.11 (non-condensing systems), 11.3.11 (condensing systems), 11.4.11 (non-condensing modulating systems) and 11.5.11 (condensing modulating systems) of ASHRAE 103-1993, except that for condensing modulating systems sections 11.5.11.1 and 11.5.11.2 are replaced by sections 10.2 and 10.3 of this appendix. EffyHS is based on the assumptions that all weatherized warm air furnaces are located outdoors and that non-weatherized warm air furnaces are installed as isolated combustion systems.

10.2 Part-load efficiency at reduced fuel input rate. If the option in section 8.9 of this appendix is not employed, calculate the part-load efficiency at the reduced fuel input rate, EffyU,R, for condensing furnaces equipped with either step-modulating or two-stage controls, expressed as a percent and defined as: