Title 10
PART 430 APPENDIX CC
Test configuration | Evaporator inlet
air, °F ( °C) |
Condenser inlet
air, °F ( °C) |
||
---|---|---|---|---|
Dry bulb | Wet bulb | Dry bulb | Wet bulb | |
3 (Dual-Duct, Condition A) | 80 (26.7) | 67 (19.4) | 95 (35.0) | 75 (23.9) |
3 (Dual-Duct, Condition B) | 80 (26.7) | 67 (19.4) | 83 (28.3) | 67.5 (19.7) |
5 (Single-Duct) | 80 (26.7) | 67 (19.4) | 80 (26.7) | 67 (19.4) |
4.1.1. Duct Heat Transfer. Measure the surface temperature of the condenser exhaust duct and condenser inlet duct, where applicable, throughout the cooling mode test. Calculate the average temperature at each individual location, and then calculate the average surface temperature of each duct by averaging the four average temperature measurements taken on that duct. Calculate the surface area (Aduct_j) of each duct according to:
Aduct_j = π × dj × Lj Where: dj = the outer diameter of duct “j”, including any manufacturer-supplied insulation. Lj = the extended length of duct “j” while under test. j represents the condenser exhaust duct and, for dual-duct units, the condenser exhaust duct and the condenser inlet duct.Calculate the total heat transferred from the surface of the duct(s) to the indoor conditioned space while operating in cooling mode for the outdoor test conditions in Table 1 of this appendix, as follows. For single-duct portable air conditioners:
Qduct_SD = h × Aduct_j × (Tduct_SD_j−Tei) For dual-duct portable air conditioners: Qduct_95 = ∑j{h × Aduct_j × (Tduct_95_j−Tei)} Qduct_83 = ∑j{h × Aduct_j × (Tduct_83_j−Tei)} Where: Qduct_SD = for single-duct portable air conditioners, the total heat transferred from the duct to the indoor conditioned space in cooling mode when tested according to the test conditions in Table 1 of this appendix, in Btu/h. Qduct_95 and Qduct_83 = for dual-duct portable air conditioners, the total heat transferred from the ducts to the indoor conditioned space in cooling mode, in Btu/h, when tested according to the 95 °F dry-bulb and 83 °F dry-bulb outdoor test conditions in Table 1 of this appendix, respectively. h = convection coefficient, 3 Btu/h per square foot per °F. Aduct_j = surface area of duct “j”, in square feet. Tduct_SD_j = average surface temperature for the condenser exhaust duct of single-duct portable air conditioners, as measured during testing according to the test condition in Table 1 of this appendix, in °F. Tduct_95_j and Tduct_83_j = average surface temperature for duct “j” of dual-duct portable air conditioners, as measured during testing according to the two outdoor test conditions in Table 1 of this appendix, in °F. j represents the condenser exhaust duct and, for dual-duct units, the condenser exhaust duct and the condenser inlet duct. Tei = average evaporator inlet air dry-bulb temperature, in °F.4.1.2. Infiltration Air Heat Transfer. Measure the heat contribution from infiltration air for single-duct portable air conditioners and dual-duct portable air conditioners that draw at least part of the condenser air from the conditioned space. Calculate the heat contribution from infiltration air for single-duct and dual-duct portable air conditioners for both cooling mode outdoor test conditions, as described in this section. Calculate the dry air mass flow rate of infiltration air according to the following equations:
For dual-duct portable air conditioners:
Where: m SD = dry air mass flow rate of infiltration air for single-duct portable air conditioners, in pounds per minute (lb/m). m 95 and m 83 = dry air mass flow rate of infiltration air for dual-duct portable air conditioners, as calculated based on testing according to the test conditions in Table 1 of this appendix, in lb/m. Vco_SD, Vco_95, and Vco_83 = average volumetric flow rate of the condenser outlet air during cooling mode testing for single-duct portable air conditioners; and at the 95 °F and 83 °F dry-bulb outdoor conditions for dual-duct portable air conditioners, respectively, in cubic feet per minute (cfm). Vci_95 and Vci_83 = average volumetric flow rate of the condenser inlet air during cooling mode testing at the 95 °F and 83 °F dry-bulb outdoor conditions for dual-duct portable air conditioners, respectively, in cfm. ρco_SD, ρco_95, and ρco_83 = average density of the condenser outlet air during cooling mode testing for single-duct portable air conditioners, and at the 95 °F and 83 °F dry-bulb outdoor conditions for dual-duct portable air conditioners, respectively, in pounds mass per cubic foot (lbm/ft 3). ρci_95 and ρci_83 = average density of the condenser inlet air during cooling mode testing at the 95 °F and 83 °F dry-bulb outdoor conditions for dual-duct portable air conditioners, respectively, in lbm/ft 3. ωco_SD, ωco_95, and ωco_83 = average humidity ratio of condenser outlet air during cooling mode testing for single-duct portable air conditioners, and at the 95 °F and 83 °F dry-bulb outdoor conditions for dual-duct portable air conditioners, respectively, in pounds mass of water vapor per pounds mass of dry air (lbw/lbda). ωci_95 and ωci_83 = average humidity ratio of condenser inlet air during cooling mode testing at the 95 °F and 83 °F dry-bulb outdoor conditions for dual-duct portable air conditioners, respectively, in lbw/lbda.For single-duct and dual-duct portable air conditioners, calculate the sensible component of infiltration air heat contribution according to:
Qs_95 = m × 60 × [(cp_da × (Tia_95−Tindoor)) + (cp_wv × (ωia_95 × Tia_95−ωindoor × Tindoor))] Qs_83 = m × 60 × [(cp_da × (Tia_83−Tindoor)) + (cp_wv × (ωia_83 × Tia_83−ωindoor × Tindoor))] Where: Qs_95 and Qs_83 = sensible heat added to the room by infiltration air, calculated at the 95 °F and 83 °F dry-bulb outdoor conditions in Table 1 of this appendix, in Btu/h. m = dry air mass flow rate of infiltration air, m SD or m 95 when calculating Qs_95 and m SD or m 83 when calculating Qs_83, in lb/m. cp_da = specific heat of dry air, 0.24 Btu/lbm- °F. cp_wv = specific heat of water vapor, 0.444 Btu/lbm- °F. Tindoor = indoor chamber dry-bulb temperature, 80 °F. Tia_95 and Tia_83 = infiltration air dry-bulb temperatures for the two test conditions in Table 1 of this appendix, 95 °F and 83 °F, respectively. ωia_95 and ωia_83 = humidity ratios of the 95 °F and 83 °F dry-bulb infiltration air, 0.0141 and 0.01086 lbw/lbda, respectively. ωindoor = humidity ratio of the indoor chamber air, 0.0112 lbw/lbda. 60 = conversion factor from minutes to hours.Calculate the latent heat contribution of the infiltration air according to:
Ql_95 = m × 60 × Hfg × (ωia_95−ωindoor) Ql_83 = m × 60 × Hfg × (ωia_83−ωindoor) Where: Ql_95 and Ql_83 = latent heat added to the room by infiltration air, calculated at the 95 °F and 83 °F dry-bulb outdoor conditions in Table 1 of this appendix, in Btu/h. m = mass flow rate of infiltration air, m SD or m 95 when calculating Ql_95 and m SD or m 83 when calculating Ql_83, in lb/m. Hfg = latent heat of vaporization for water vapor, 1061 Btu/lbm. ωia_95 and ωia_83 = humidity ratios of the 95 °F and 83 °F dry-bulb infiltration air, 0.0141 and 0.01086 lbw/lbda, respectively. ωindoor = humidity ratio of the indoor chamber air, 0.0112 lbw/lbda. 60 = conversion factor from minutes to hours.The total heat contribution of the infiltration air is the sum of the sensible and latent heat:
Qinfiltration_95 = Qs_95 + Ql_95
Qinfiltration_83 = Qs_83 + Ql_83
Where: Qinfiltration_95 and Qinfiltration_83 = total infiltration air heat in cooling mode, calculated at the 95 °F and 83 °F dry-bulb outdoor conditions in Table 1 of this appendix, in Btu/h. Qs_95 and Qs_83 = sensible heat added to the room by infiltration air, calculated at the 95 °F and 83 °F dry-bulb outdoor conditions in Table 1 of this appendix, in Btu/h. Ql_95 and Ql_83 = latent heat added to the room by infiltration air, calculated at the 95 °F and 83 °F dry-bulb outdoor conditions in Table 1 of this appendix, in Btu/h.4.2 Off-cycle mode. Establish the test conditions specified in section 3.1.1 of this appendix for off-cycle mode and use the wattmeter specified in section 3.2.3 of this appendix (but do not use the duct measurements in section 3.1.1.6). Begin the off-cycle mode test period 5 minutes following the cooling mode test period. Adjust the setpoint higher than the ambient temperature to ensure the product will not enter cooling mode and begin the test 5 minutes after the compressor cycles off due to the change in setpoint. Do not change any other control settings between the end of the cooling mode test period and the start of the off-cycle mode test period. The off-cycle mode test period must be 2 hours in duration, during which period, record the power consumption at the same intervals as recorded for cooling mode testing. Measure and record the average off-cycle mode power of the portable air conditioner, Poc, in watts.
4.3 Standby mode and off mode. Establish the testing conditions set forth in section 3.2 of this appendix, ensuring that the portable air conditioner does not enter any active modes during the test. For portable air conditioners 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, (incorporated by reference; see § 430.3), allow sufficient time for the portable air conditioner to reach the lowest power state before proceeding with the test measurement. Follow the test procedure specified in Section 5, Paragraph 5.3.2 of IEC 62301 for testing in each possible mode as described in sections 4.3.1 and 4.3.2 of this appendix.
4.3.1 If the portable air conditioner has an inactive mode, as defined in section 2.6 of this appendix, but not an off mode, as defined in section 2.8 of this appendix, measure and record the average inactive mode power of the portable air conditioner, Pia, in watts.
4.3.2 If the portable air conditioner has an off mode, as defined in section 2.8 of this appendix, measure and record the average off mode power of the portable air conditioner, Pom, in watts.
5. Calculation of Derived Results From Test Measurements5.1 Adjusted Cooling Capacity. Calculate the adjusted cooling capacities for portable air conditioners, ACC95 and ACC83, expressed in Btu/h, according to the following equations. For single-duct portable air conditioners:
ACC95 = CapacitySD − Qduct_SD − Qinfiltration_95 ACC83 = CapacitySD − Qduct_SD − Qinfiltration_83For dual-duct portable air conditioners:
ACC95 = Capacity95 − Qduct_95 − Qinfiltration_95 ACC83 = Capacity83 − Qduct_83 − Qinfiltration_83 Where: CapacitySD, Capacity95, and Capacity83 = cooling capacity measured in section 4.1.1 of this appendix. Qduct_SD, Qduct_95, and Qduct_83 = duct heat transfer while operating in cooling mode, calculated in section 4.1.1.1 of this appendix. Qinfiltration_95 and Qinfiltration_83 = total infiltration air heat transfer in cooling mode, calculated in section 4.1.1.2 of this appendix.5.2 Seasonally Adjusted Cooling Capacity. Calculate the seasonally adjusted cooling capacity for portable air conditioners, SACC, expressed in Btu/h, according to:
SACC = ACC95 × 0.2 + ACC83 × 0.8 Where: ACC95 and ACC83 = adjusted cooling capacity, in Btu/h, calculated in section 5.1 of this appendix. 0.2 = weighting factor for ACC95. 0.8 = weighting factor for ACC83.5.3 Annual Energy Consumption. Calculate the annual energy consumption in each operating mode, AECm, expressed in kilowatt-hours per year (kWh/year). Use the following annual hours of operation for each mode:
Operating mode | Annual operating hours |
---|---|
Cooling Mode, Dual-Duct 95 °F 1 | 750 |
Cooling Mode, Dual-Duct 83 °F 1 | 750 |
Cooling Mode, Single-Duct | 750 |
Off-Cycle | 880 |
Inactive or Off | 1,355 |
1 These operating mode hours are for the purposes of calculating annual energy consumption under different ambient conditions for dual-duct portable air conditioners, and are not a division of the total cooling mode operating hours. The total dual-duct cooling mode operating hours are 750 hours.
m represents the operating mode (“95” and “83” cooling mode at the 95 °F and 83 °F dry-bulb outdoor conditions, respectively for dual-duct portable air conditioners, “SD” cooling mode for single-duct portable air conditioners, “oc” off-cycle, and “ia” inactive or “om” off mode).
t = number of annual operating time in each mode, in hours. k = 0.001 kWh/Wh conversion factor from watt-hours to kilowatt-hours.Total annual energy consumption in all modes except cooling, is calculated according to:
Where: AECT = total annual energy consumption attributed to all modes except cooling, in kWh/year; AECm = total annual energy consumption in each mode, in kWh/year.m represents the operating modes included in AECT (“oc” off-cycle, and “im” inactive or “om” off mode).
5.4 Combined Energy Efficiency Ratio. Using the annual operating hours, as outlined in section 5.3 of this appendix, calculate the combined energy efficiency ratio, CEER, expressed in Btu/Wh, according to the following:
Where: CEERSD and CEERDD = combined energy efficiency ratio for single-duct and dual-duct portable air conditioners, respectively, in Btu/Wh. ACC95 and ACC83 = adjusted cooling capacity, tested at the 95 °F and 83 °F dry-bulb outdoor conditions in Table 1 of this appendix, in Btu/h, calculated in section 5.1 of this appendix. AECSD = annual energy consumption in cooling mode for single-duct portable air conditioners, in kWh/year, calculated in section 5.3 of this appendix. AEC95 and AEC83 = annual energy consumption for the two cooling mode test conditions in Table 1 of this appendix for dual-duct portable air conditioners, in kWh/year, calculated in section 5.3 of this appendix. AECT = total annual energy consumption attributed to all modes except cooling, in kWh/year, calculated in section 5.3 of this appendix. t = number of cooling mode hours per year, 750. k = 0.001 kWh/Wh conversion factor for watt-hours to kilowatt-hours. 0.2 = weighting factor for the 95 °F dry-bulb outdoor condition test. 0.8 = weighting factor for the 83 °F dry-bulb outdoor condition test. [81 FR 35265, June 1, 2016, as amended at 81 FR 70923, Oct. 14, 2016; 85 FR 21746, Apr. 20, 2020]