Note:

Manufacturers must use the results of testing under this appendix to determine compliance with the relevant standards for portable air conditioners at § 430.32(cc) with which compliance is required as of January 10, 2025. Specifically, before November 13, 2023 representations must be based upon results generated either under this appendix or under this appendix CC as it appeared in the 10 CFR parts 200-499 edition revised as of January 1, 2021. Any representations made on or after November 13, 2023 but before the compliance date of any amended standards for portable ACs must be made based upon results generated using this appendix.

Manufacturers must use the results of testing under appendix CC1 to this subpart to determine compliance with any standards that amend the portable air conditioners standard at § 430.32(cc) with which compliance is required on January 10, 2025 and that use the Annualized Energy Efficiency Ratio (AEER) metric. Any representations related to energy also must be made in accordance with the appendix that applies (i.e., this appendix or appendix CC1) when determining compliance with the relevant standard. Manufacturers may also use appendix CC1 to certify compliance with any amended standards prior to the applicable compliance date for those standards.

0. Incorporation by Reference

DOE incorporated by reference in § 430.3 the entire standard for ANSI/AHAM PAC-1-2015, ANSI/AMCA 210-99, ASHRAE 37-2009, ASHRAE 41.1-1986, ASHRAE 41.6-1994, and IEC 62301; however, only enumerated provisions of ANSI/AHAM PAC-1-2015, ANSI/AMCA 210-99, ASHRAE 37-2009, and IEC 62301 apply to this appendix CC as follows. Treat “should” in IEC 62301 as mandatory. When there is a conflict, the language of this appendix takes precedence over those documents.

0.1 ANSI/AHAM PAC-1-2015

(a) Section 4 “Definitions,” as specified in section 3.1.1 of this appendix, except for AHAM's definition for “Portable Air Conditioner”;

(b) Section 7 “Tests,” as specified in sections 3.1.1, 3.1.1.3, 3.1.1.4, 4.1.1, and 4.1.2 of this appendix.

0.2 ANSI/AMCA 210-99 (“ANSI/AMCA 210”)

(a) Figure 12 “Outlet chamber Setup—Multiple Nozzles in Chamber” as specified in section 4.1.1 of this appendix;

(b) Figure 12 Notes as specified in section 4.1.1 of this appendix.

0.3 ASHRAE 37-2009

(a) Section 5.4 “Electrical Instruments,” as specified in sections 4.1.1 and 4.1.2 of this appendix;

(b) Section 7.3 “Indoor and Outdoor Air Enthalpy Methods,” as specified in sections 4.1.1 and 4.1.2 of this appendix;

(c) Section 7.6 “Outdoor Liquid Coil Method,” as specified in sections 4.1.1 and 4.1.2 of this appendix;

(d) Section 7.7 “Airflow Rate Measurement,” as specified in sections 4.1.1 and 4.1.2 of this appendix;

(e) Section 8.7 “Test Procedure for Cooling Capacity Tests,” as specified in sections 4.1.1 and 4.1.2 of this appendix;

(f) Section 9.2 “Test Tolerances,” as specified in sections 4.1.1 and 4.1.2 of this appendix;

(g) Section 11.1 “Symbols Used In Equations,” as specified in sections 4.1.1 and 4.1.2 of this appendix.

0.4 IEC 62301

(a) Paragraph 4.2 “Test room,” as specified in section 3.2.4 of this appendix;

(b) Paragraph 4.3.2 “Supply voltage waveform,” as specified in section 3.2.2.2 of this appendix;

(c) Paragraph 4.4 “Power measuring instruments,” as specified in section 3.2.3 of this appendix;

(d) Paragraph 5.1, “General,” Note 1, as specified in section 4.3 of this appendix;

(e) Paragraph 5.2 “Preparation of product,” as specified in section 3.2.1 of this appendix;

(f) Paragraph 5.3.2 “Sampling method,” as specified in section 4.3 of this appendix;

(g) Annex D, “Determination of Uncertainty of Measurement,” as specified in sections 3.2.1, 3.2.2.2, and 3.2.3 of this appendix.

1. Scope

This appendix covers the test requirements used to measure the energy performance of single-duct and dual-duct portable air conditioners, as defined at 10 CFR 430.2.

2. Definitions

Combined-duct means the condenser inlet and outlet air streams flow through separate ducts housed in a single duct structure.

Combined energy efficiency ratio means the energy efficiency of a portable air conditioner as measured in accordance with this test procedure in Btu per watt-hours (Btu/Wh) and determined in section 5.4 of this appendix.

Cooling mode means a mode in which a portable air conditioner either has activated the main cooling function according to the thermostat or temperature sensor signal, including activating the refrigeration system, or has activated the fan or blower without activating the refrigeration system.

Dual-duct means drawing some or all of the condenser inlet air from outside the conditioned space through a duct attached to an adjustable window bracket, potentially drawing additional condenser inlet air from the conditioned space, and discharging the condenser outlet air outside the conditioned space by means of a separate duct attached to an adjustable window bracket.

Full compressor speed (full) means the compressor speed at which the unit operates at full load test conditions, when using user controls with a unit thermostat setpoint of 75 °F to achieve maximum cooling capacity.

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

Low compressor speed (low) means the compressor speed specified by the manufacturer, at which the unit operates at low load test conditions (i.e., Test Condition C and Test Condition E in Table 2 of this appendix, for a dual-duct and single-duct portable air conditioner, respectively), such that the measured cooling capacity at this speed is no less than 50 percent and no greater than 60 percent of the measured cooling capacity with the full compressor speed at full load test conditioners (i.e., Test Condition A and Test Condition C in Table 2 of this appendix, for a dual-duct and single-duct portable air conditioner, respectively).

Off-cycle mode means a mode in which a portable air conditioner:

(a) Has cycled off its main cooling or heating function by thermostat or temperature sensor signal;

(b) May or may not operate its fan or blower; and

(c) Will reactivate the main function according to the thermostat or temperature sensor signal.

Off mode means a mode that may persist for an indefinite time in which a portable air conditioner is connected to a mains power source, and is not providing any active mode, off-cycle mode, or standby mode function. This includes an indicator that only shows the user that the portable air conditioner is in the off position.

Seasonally adjusted cooling capacity means the amount of cooling provided to the indoor conditioned space, measured under the specified ambient conditions, in Btu/h,

Seasonally adjusted cooling capacity, full means the amount of cooling provided to the indoor conditions space, measured under the specified ambient conditions when the unit compressor is operating at full speed at each condition, in Btu/h.

Single-duct means drawing all of the condenser inlet air from the conditioned space without the means of a duct, and discharging the condenser outlet air outside the conditioned space through a single duct attached to an adjustable window bracket.

Single-speed means incapable of automatically adjusting the compressor speed based on detected conditions.

Standby mode means any mode where a portable air conditioner 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 cooling mode) by remote switch (including remote control), internal sensor, or timer; or

(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.

Theoretical comparable single-speed means a hypothetical single-speed unit that would have the same cooling capacity and electrical power input as the variable-speed unit under test, with no cycling losses considered, when operating with the full compressor speed and at the test conditions in Table 1 of this appendix.

Variable-speed means capable of automatically adjusting the compressor speed based on detected conditions.

3. Test Apparatus and General Instructions

3.1 Active mode.

3.1.1 Test conduct. The test apparatus and instructions for testing portable air conditioners in cooling mode and off-cycle mode must conform to the requirements specified in section 4, “Definitions” and section 7, “Tests,” of ANSI/AHAM PAC-1-2015, except as otherwise specified in this appendix. Measure duct heat transfer and infiltration air heat transfer according to sections 4.1.1 and 4.1.2 of this appendix, respectively.

3.1.1.1 Duct setup. Use all ducting components provided by or required by the manufacturer and no others. Ducting components include ducts, connectors for attaching the duct(s) to the test unit, sealing, insulation, and window mounting fixtures. Do not apply additional sealing or insulation. For combined-duct units, the manufacturer must provide the testing facility an adapter that allows for the individual connection of the condenser inlet and outlet airflows to the test facility's airflow measuring apparatuses. Use that adapter to measure the condenser inlet and outlet airflows for any corresponding unit.

3.1.1.2 Single-duct evaporator inlet test conditions. When testing single-duct portable air conditioners, maintain the evaporator inlet dry-bulb temperature within a range of 1.0 °F with an average difference within 0.3 °F.

3.1.1.3 Condensate Removal. Set up the test unit in accordance with manufacturer instructions. If the unit has an auto-evaporative feature, keep any provided drain plug installed as shipped and do not provide other means of condensate removal. If the internal condensate collection bucket fills during the test, halt the test, remove the drain plug, install a gravity drain line, and start the test from the beginning. If no auto-evaporative feature is available, remove the drain plug and install a gravity drain line. If no auto-evaporative feature or gravity drain is available and a condensate pump is included, or if the manufacturer specifies the use of an included condensate pump during cooling mode operation, then test the portable air conditioner with the condensate pump enabled. For units tested with a condensate pump, apply the provisions in Section 7.1.2 of ANSI/AHAM PAC-1-2015 if the pump cycles on and off.

3.1.1.4 Unit Placement. There shall be no less than 3 feet between any test chamber wall surface and any surface on the portable air conditioner, except the surface or surfaces of the portable air conditioner that include a duct attachment. The distance between the test chamber wall and a surface with one or more duct attachments is prescribed by the test setup requirements in Section 7.3.7 of ANSI/AHAM PAC-1-2015.

3.1.1.5 Electrical supply. Maintain the input standard voltage at 115 V ±1 percent. Test at the rated frequency, maintained within ±1 percent.

3.1.1.6 Duct temperature measurements. Install any insulation and sealing provided by the manufacturer. For a dual-duct or single-duct unit, adhere four thermocouples per duct, spaced along the entire length equally, to the outer surface of the duct. Measure the surface temperatures of each duct. For a combined-duct unit, adhere sixteen thermocouples to the outer surface of the duct, spaced evenly around the circumference (four thermocouples, each 90 degrees apart, radially) and down the entire length of the duct (four sets of four thermocouples, evenly spaced along the entire length of the duct), ensuring that the thermocouples are spaced along the entire length equally, on the surface of the combined duct. Place at least one thermocouple preferably adjacent to, but otherwise as close as possible to, the condenser inlet aperture and at least one thermocouple on the duct surface preferably adjacent to, but otherwise as close as possible to, the condenser outlet aperture. Measure the surface temperature of the combined duct at each thermocouple. Temperature measurements must have an error no greater than ±0.5 °F over the range being measured.

3.1.2 Control settings. For a single-speed unit, set the controls to the lowest available temperature setpoint for cooling mode, as described in section 4.1.1 of this appendix. For a variable-speed unit, set the thermostat setpoint to 75 °F to achieve the full compressor speed and use the manufacturer instructions to achieve the low compressor speed, as described in section 4.1.2 of this appendix. If the portable air conditioner has a user-adjustable fan speed, select the maximum fan speed setting. If the unit has an automatic louver oscillation feature and there is an option to disable that feature, disable that feature throughout testing. If the unit has adjustable louvers, position the louvers parallel with the air flow to maximize air flow and minimize static pressure loss. If the portable air conditioner has network functions, that an end-user can disable and the product's user manual provides instructions on how to do so, disable all network functions throughout testing. If an end-user cannot disable a network function or the product's user manual does not provide instruction for disabling a network function, test the unit with that network function in the factory default configuration for the duration of the test.

3.2 Standby Mode and Off Mode

3.2.1 Installation requirements. For the standby mode and off mode testing, install the portable air conditioner in accordance with Paragraph 5.2 of IEC 62301, referring to Annex D of that standard as necessary. Disregard the provisions regarding batteries and the determination, classification, and testing of relevant modes.

3.2.2 Electrical energy supply.

3.2.2.1 Electrical supply. For the standby mode and off mode testing, maintain the input standard voltage at 115 V ±1 percent. Maintain the electrical supply at the rated frequency ±1 percent.

3.2.2.2 Supply voltage waveform. For the standby mode and off mode testing, maintain the electrical supply voltage waveform indicated in, Paragraph 4.3.2 of IEC 62301, referring to Annex D of that standard as necessary.

3.2.3 Standby mode and off mode wattmeter. The wattmeter used to measure standby mode and off mode power consumption must meet the requirements specified in Paragraph 4.4 of IEC 62301, using a two-tailed confidence interval and referring to Annex D of that standard as necessary.

3.2.4 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 (incorporated by reference; see § 430.3).

4. Test Measurement 4.1 Cooling Mode Note:

For the purposes of this cooling mode test procedure, evaporator inlet air is considered the “indoor air” of the conditioned space and condenser inlet air is considered the “outdoor air” outside of the conditioned space.

4.1.1 Single-Speed Cooling Mode Test. For single-speed portable air conditioners, measure the indoor room cooling capacity and overall power input in cooling mode in accordance with sections 7.1.b and 7.1.c of ANSI/AHAM PAC-1-2015, respectively, including the references to sections 5.4, 7.3, 7.6, 7.7, and 11 of ASHRAE 37-2009. Determine the test duration in accordance with section 8.7 of ASHRAE 37-2009, including the reference to section 9.2 of the same standard, referring to Figure 12 and the Figure 12 Notes of ANSI/AMCA 210 to determine placement of static pressure taps, and including references to ASHRAE 41.1-1986 and ASHRAE 41.6-1994. Disregard the test conditions in Table 3 of ANSI/AHAM PAC-1-2015. Instead, apply the test conditions for single-duct and dual-duct portable air conditioners presented in Table 1 of this appendix. For single-duct units, measure the indoor room cooling capacity, CapacitySD, and overall power input in cooling mode, PSD, in accordance with the ambient conditions for test condition 1.C, presented in Table 1 of this appendix. For dual-duct units, measure the indoor room cooling capacity and overall power input twice, first in accordance with ambient conditions for test condition 1.A (Capacity95, P95), and then in accordance with test condition 1.B (Capacity83, P83), both presented in Table 1 of this appendix. For the remainder of this test procedure, test combined-duct single-speed portable air conditioners following any instruction for dual-duct single-speed portable air conditioners, unless otherwise specified.

4.1.2 Variable-Speed Cooling Mode Test. For variable-speed portable air conditioners, measure the indoor room cooling capacity and overall power input in cooling mode in accordance with sections 7.1.b and 7.1.c of ANSI/AHAM PAC-1-2015, respectively, including the references to sections 5.4, 7.3, 7.6, 7.7, and 11 of ASHRAE 37-2009, except as detailed below. Determine the test duration in accordance with section 8.7 of ASHRAE 37-2009, including the reference to section 9.2 of the same standard. Disregard the test conditions in Table 3 of ANSI/AHAM PAC-1-2015. Instead, apply the test conditions for single-duct and dual-duct portable air conditioners presented in Table 2 of this appendix. For a single-duct unit, measure the indoor room cooling capacity and overall power input in cooling mode twice, first in accordance with the ambient conditions and compressor speed settings for test condition 2.D (CapacitySD_Full, PSD_Full), and then in accordance with the ambient conditions for test condition 2.E (CapacitySD_Low, PSD_Low), both presented in Table 2 of this appendix. For dual-duct units, measure the indoor room cooling capacity and overall power input three times, first in accordance with ambient conditions for test condition 2.A (Capacity95_Full, P95_Full), second in accordance with the ambient conditions for test condition 2.B (Capacity83_Full, P83_Full), and third in accordance with the ambient conditions for test condition 2.C (Capacity83_Low, P83_Low), each presented in Table 2 of this appendix. For the remainder of this test procedure, test combined-duct variable-speed portable air conditioners following any instruction for dual-duct variable-speed portable air conditioners, unless otherwise specified. For test conditions 2.A, 2.B, and 2.D, achieve the full compressor speed with user controls, as defined in section 2.13 of this appendix. For test conditions 2.C and 2.E, set the required compressor speed in accordance with instructions the manufacturer provided to DOE.

4.1.3. Duct Heat Transfer

Throughout the cooling mode test, measure the surface temperature of the condenser exhaust duct and condenser inlet duct, where applicable. Calculate the average temperature at each thermocouple placement location. Then calculate the average surface temperature of each duct. For single-duct and dual-duct units, calculate the average of the four average temperature measurements taken on the duct. For combined-duct units, calculate the average of the sixteen average temperature measurements taken on the duct. Calculate the surface area (Aduct_j) of each duct according to:

Aduct_j = Cj × Lj Where: Cj = the circumference of duct “j”, including any manufacturer-supplied insulation, measured by wrapping a flexible measuring tape, or equivalent, around the outside of a combined duct, making sure the tape is on the outermost ridges or, alternatively, if the duct has a circular cross-section, by multiplying the outer diameter by 3.14. Lj = the extended length of duct “j” while under test. j represents the condenser exhaust duct for single-duct units, the condenser exhaust duct and the condenser inlet duct for dual-duct units, and the combined duct for combined-duct units.

Calculate the total heat transferred from the surface of the duct(s) to the indoor conditioned space while operating in cooling mode at each test condition, as follows:

For single-duct single-speed portable air conditioners:

Qduct_SD = 3 × Aduct_j × (Tduct_j−Tei)

For dual-duct single-speed portable air conditioners:

Qduct_DD_95 = Σj{3 × Aduct_j × (Tduct_95_j−Tei)} Qduct_DD_83 = Σj{3 × Aduct_j × (Tduct_83_j−Tei)}

For single-duct variable-speed portable air conditioners:

Qduct_SD_Full = 3 × Aduct × (Tduct_Full_j−Tei) Qduct_SD_Low = 3 × Aduct × (Tduct_Low_j−Tei)

For dual-duct variable-speed portable air conditioners:

Qduct_DD_95_Full = Σj{3 × Aduct_j × (Tduct_Full_95_j−Tei)} Qduct_DD_83_Full = Σj{3 × Aduct_j × (Tduct_Full_83_j−Tei)} Qduct_DD_83_Low = Σj{3 × Aduct_j × (Tduct_Low_83_j—Tei)} Where: Qduct_SD = the total heat transferred from the duct to the indoor conditioned space in cooling mode, in Btu/h, when tested at Test Condition 1.C. Qduct_DD_95 and Qduct_DD_83 = the total heat transferred from the ducts to the indoor conditioned space in cooling mode, in Btu/h, when tested at Test Conditions 1.A and 1.B, respectively. Qduct_SD_Full and Qduct_SD_Low = the total heat transferred from the duct to the indoor conditioned space in cooling mode, in Btu/h, when tested at Test Conditions 2.D and 2.E, respectively. Qduct_DD_95_Full, Qduct_DD_83_Full, and Qduct_DD_83_Low = the total heat transferred from the ducts to the indoor conditioned space in cooling mode, in Btu/h, when tested at Test Condition 2.A, Test Condition 2.B, and Test Condition 2.C, respectively. 3 = empirically-derived convection coefficient in Btu/h per square foot per °F. Aduct_j = surface area of the duct “j”, as calculated in this section, in square feet. Tduct_j = average surface temperature for duct “j” of single-duct single-speed portable air conditioners, in °F, as measured at Test Condition 1.C. Tduct_95_j and Tduct_83_j = average surface temperature for duct “j” of dual-duct single-speed portable air conditioners, in °F, as measured at Test Conditions 1.A and 1.B, respectively. Tduct_Full_j and Tduct_Low_j = average surface temperature for duct “j” of single-duct variable-speed portable air conditioners, in °F, as measured at Test Conditions 2.D and 2.E, respectively. Tduct_Full_95_j, Tduct_Full_83_j, and Tduct_Low_83_j = average surface temperature for duct “j” of dual-duct variable-speed portable air conditioners, in °F, as measured at Test Conditions 2.A, 2.B, and 2.C, respectively. j represents the condenser exhaust duct for single-duct units, the condenser exhaust duct and the condenser inlet duct for dual-duct units, and the combined duct for combined-duct units. Tei = average evaporator inlet air dry-bulb temperature, as measured in section 4.1 of this appendix, in °F.

4.1.4. Infiltration Air Heat Transfer.

Calculate the sample unit's heat contribution from infiltration air into the conditioned space for each cooling mode test as follows:

Calculate the dry air mass flow rate of infiltration air, which affects the sensible and latent components of heat contribution from infiltration air, according to the following equations.

For a single-duct single-speed unit:

For a dual-duct single-speed unit:

For a single-duct variable-speed unit:

For a dual-duct variable-speed unit:

Where: m SD, m SD_Full, and m SD_Low = dry air mass flow rate of infiltration air for single-duct portable air conditioners, in pounds per minute (lb/m) when tested at Test Conditions 1.C, 2.D, and 2.E, respectively. m 95, m 83, m 95_Full, m 83_Full, and m 83_Low = dry air mass flow rate of infiltration air for dual-duct portable air conditioners, in lb/m, when tested at Test Conditions 1.A, 1.B, 2.A, 2.B, and 2.C, respectively. Vco_SD, Vco_SD_Full, Vco_SD_Low, Vco_95, Vco_83, Vco_95_Full, Vco_83_Full, and Vco_83_Low = average volumetric flow rate of the condenser outlet air, in cubic feet per minute (cfm), as measured at Test Conditions 1.C, 2.D, 2.E, 1.A, 1.B, 2.A, 2.B, and 2.C, respectively, as required in sections 4.1.1 and 4.1.2 of this appendix. Vci_95, Vci_83, Vci_95_Full, Vci_83_Full, and Vci_83_Low = average volumetric flow rate of the condenser inlet air, in cfm, as measured at Test Conditions 1.A, 1.B, 2.A, 2.B, and 2.C, respectively, as required in sections 4.1.1 and 4.1.2 of this appendix. ρco_SD, ρco_SD_Full, ρco_SD_Low, ρco_95, ρco_83, ρco_95_Full, ρco_83_Full, and ρco_83_Low = average density of the condenser outlet air, in pounds mass per cubic foot (lbm/ft 3), as measured at Test Conditions 1.C, 2.D, 2.E, 1.A, 1.B, 2.A, 2.B, and 2.C, respectively, as required in sections 4.1.1 and 4.1.2 of this appendix. ρci_95, ρci_83, ρci_95_Full, ρci_83_Full, and ρci_83_Low = average density of the condenser inlet air, in lbm/ft 3, as measured at Test Conditions 1.A, 1.B, 2.A, 2.B, and 2.C, respectively, as required in sections 4.1.1 and 4.1.2 of this appendix. ωco_SD, ωco_SD_Full, ωco_SD_Low, ωco_95, ωco_83, ωco_95_Full, ωco_83_Full, and ωco_83_Low = average humidity ratio of condenser outlet air, in pounds mass of water vapor per pounds mass of dry air (lbw/lbda), as measured at Test Conditions 1.C, 2.D, 2.E, 1.A, 1.B, 2.A, 2.B, and 2.C, respectively, as required in sections 4.1.1 and 4.1.2 of this appendix. ωci_95, ωci_83, ωci_95_Full, ωci_83_Full, and ωci_83_Low = average humidity ratio of condenser inlet air, in lbw/lbda, as measured at Test Conditions 1.A, 1.B, 2.A, 2.B, and 2.C, respectively, as required in sections 4.1.1 and 4.1.2 of this appendix.

Calculate the sensible component of infiltration air heat contribution according to the following equations.

For single-duct single-speed units:

Qs_SD_95 = m SD × 60 × [cp_da × (95−80) + (cp_wv × (0.0141 × 95 − 0.0112 × 80))] Qs_SD_83 = m SD × 60 × [(cp_da × (83 − 80) + (cp_wv × (0.01086 × 83 − 0.0112 × 80))]

For dual-duct single-speed units:

Qs_DD_95 = m 95 × 60 × [cp_da × (95 − 80) + (cp_wv × (0.0141 × 95 − 0.0112 × 80))] Qs_DD_83 = m 83 × 60 × [(cp_da × (83 − 80) + (cp_wv × (0.01086 × 83 − 0.0112 × 80))]

For single-duct variable-speed units:

Qs_SD_95_Full = m SD_Full × 60 × [cp_da × (95 − 80) + (cp_wv × (0.0141 × 95 − 0.0112 × 80))] Qs_SD_83_Full = m SD_Full × 60 × [(cp_da × (83 − 80) + (cp_wv × (0.01086 × 83 − 0.0112 × 80))] Qs_SD_83_Low = m SD_Low × 60 × [(cp_da × (83 − 80) + (cp_wv × (0.01086 × 83 − 0.0112 × 80))]

For dual-duct variable-speed units:

Qs_DD_95_Full = m 95_Full × 60 × [cp_da × (95 − 80) + (cp_wv × (0.0141 × 95 − 0.0112 × 80))] Qs_DD_83_Full = m 83_Full × 60 × [(cp_da × (83 − 80) + (cp_wv × (0.01086 × 83 − 0.0112 × 80))] Qs_DD_83_Low = m 83_Low × 60 × [(cp_da × (83 − 80) + (cp_wv × (0.01086 × 83 − 0.0112 × 80))] Where: Qs_SD_95, Qs_SD_83, Qs_DD_95, and Qs_DD_83 = sensible heat added to the room by infiltration air, in Btu/h, for each duct configuration and temperature condition. Qs_SD_95_Full, Qs_SD_83_Full, Qs_SD_83_Low, Qs_DD_95_Full, Qs_DD_83_Full, and Qs_DD_83_Low = sensible heat added to the room by infiltration air, in Btu/h, for each duct configuration, temperature condition, and compressor speed. m SD, m 95, and m 83 = dry air mass flow rate of infiltration air for single-speed portable air conditioners, in lb/m, as calculated in section 4.1.4 of this appendix. m SD_95_Full, m SD_83_Low, m 95_Full and m 83_Low = dry air mass flow rate of infiltration air for variable-speed portable air conditioners, in lb/m, as calculated in section 4.1.4 of this appendix. cp_da = specific heat of dry air, 0.24 Btu/(lbm °F). cp_wv = specific heat of water vapor, 0.444 Btu/(lbm °F). 80 = indoor chamber dry-bulb temperature, in °F. 95 = infiltration air dry-bulb temperature for Test Conditions 1.A and 2.A, in °F. 83 = infiltration air dry-bulb temperature for Test Conditions 1.B, 2.B, and 2.C, in °F. 0.0141 = humidity ratio of the dry-bulb infiltration air for Test Conditions 1.A and 2.A, in lbw/lbda. 0.01086 = humidity ratio of the dry-bulb infiltration air for Test Conditions 1.B, 2.B, and 2.C, in lbw/lbda. 0.0112 = humidity ratio of the indoor chamber air, in lbw/lbda (ωindoor). 60 = conversion factor from minutes to hours.

Calculate the latent heat contribution of the infiltration air according to the following equations. For a single-duct single-speed unit:

Ql_SD_95 = m SD × 60 × 1061 × (0.0141 − 0.0112) Ql_SD_83 = m SD × 60 × 1061 × (0.01086 − 0.0112)

For a dual-duct single-speed unit:

Ql_DD_95 = m 95 × 60 × 1061 × (0.0141 − 0.0112) Ql_DD_83 = m 83 × 60 × 1061 × (0.01086 − 0.0112) For a single-duct variable-speed unit: Ql_SD_95_Full = m SD_Full × 60 × 1061 × (0.0141 − 0.0112) Ql_SD_83_Full = m SD_Full × 60 × 1061 × (0.01086 − 0.0112) Ql_SD_83_Low = m SD_Low × 60 × 1061 × (0.01086 − 0.0112)

For a dual-duct variable-speed unit:

Ql_DD_95_Full = m 95_Full × 60 × 1061 × (0.0141 − 0.0112) Ql_DD_83_Full = m 83_Full × 60 × 1061 × (0.01086 − 0.0112) Ql_DD_83_Low = m 83_Low × 60 × 1061 × (0.01086 − 0.0112) Where: Ql_SD_95, Ql_SD_83, Ql_DD_95, and Ql_DD_83 = latent heat added to the room by infiltration air, in Btu/h, for each duct configuration and temperature condition. Ql_SD_95_Full, Ql_SD_83_Full, Ql_SD_Low, Ql_DD_95_Full, Ql_DD_83_Full, and Ql_DD_83_Low = latent heat added to the room by infiltration air, in Btu/h, for each duct configuration, temperature condition, and compressor speed. m SD, m 95, and m 83 = dry air mass flow rate of infiltration air for portable air conditioners, in lb/m, when tested at Test Conditions 1.C, 1.A, and 1.B, respectively, as calculated in section 4.1.4 of this appendix. m SD_Full, m SD_Low, m 95_Full, m 83_Full and m 83_Low = dry air mass flow rate of infiltration air for portable air conditioners, in lb/m, when tested at Test Conditions 2.D, 2.E, 2.A, 2.B, and 2.C, respectively, as calculated in section 4.1.4 of this appendix. 1061 = latent heat of vaporization for water vapor, in Btu/lbm (Hfg). 0.0141 = humidity ratio of the dry-bulb infiltration air for Test Conditions 1.A and 2.A, in lbw/lbda. 0.01086 = humidity ratio of the dry-bulb infiltration air for Test Conditions 1.B, 2.B, and 2.C, in lbw/lbda. 0.0112 = humidity ratio of the indoor chamber air, in lbw/lbda. 60 = conversion factor from minutes to hours.

Calculate the total heat contribution of the infiltration air at each test condition by adding the sensible and latent heat according to the following equations.

For a single-duct single-speed unit:

Qinfiltration_SD_95 = Qs_SD_95 + Ql_SD_95 Qinfiltration_SD_83 = Qs_SD_83 + Ql_SD_83 For a dual-duct single-speed unit: Qinfiltration_DD_95 = Qs_DD_95 + Ql_DD_95 Qinfiltration_DD_83 = Qs_DD_83 + Ql_DD_83 For a single-duct variable-speed unit: Qinfiltration_SD_95_Full = Qs_SD_95_Full + Ql_SD_95_Full Qinfiltration_SD_83_Full = Qs_SD_83_Full + Ql_SD_83_Full Qinfiltration_SD_83_Low = Qs_SD_83_Low + Ql_SD_83_Low

For a dual-duct variable-speed unit:

Qinfiltration_DD_95_Full = Qs_DD_95_Full + Ql_DD_95_Full Qinfiltration_DD_83_Full = Qs_DD_83_Full + Ql_DD_83_Full Qinfiltration_DD_83_Low = Qs_DD_83_Low + Ql_DD_83_Low Where: Qinfiltration_SD_95, Qinfiltration_SD_83, Qinfiltration_DD_95, Qinfiltration_DD_83 = total infiltration air heat in cooling mode, in Btu/h, for each duct configuration and temperature condition. Qinfiltration_SD_95_Full, Qinfiltration_SD_83_Full, Qinfiltration_SD_83_Low, Qinfiltration_DD_95_Full, Qinfiltration_DD_83_Full, and Qinfiltration_DD_83_Low = total infiltration air heat in cooling mode, in Btu/h, for each duct configuration, temperature condition, and compressor speed. Qs_SD_95, Qs_SD_83, Qs_DD_95, and Qs_DD_83 = sensible heat added to the room by infiltration air, in Btu/h, for each duct configuration, temperature condition, and compressor speed. Qs_SD_95_Full, Qs_SD_83_Full, Qs_SD_83_Low, Qs_DD_95_Full, Qs_DD_83_Full, and Qs_DD_83_Low = sensible heat added to the room by infiltration air, in Btu/h, for each duct configuration, temperature condition, and compressor speed. Ql_SD_95, Ql_SD_83, Ql_DD_95, and Ql_DD_83 = latent heat added to the room by infiltration air, in Btu/h, for each duct configuration, and temperature condition. Ql_SD_95_Full, Ql_SD_83_Full, Ql_SD_83_Low, Ql_DD_95_Full, Ql_DD_83_Full, and Ql_DD_83_Low = latent heat added to the room by infiltration air, in Btu/h, for each duct configuration, temperature condition, and compressor speed.

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 unit does not enter any active modes during the test. As discussed in Paragraph 5.1, Note 1 of IEC 62301, allow sufficient time for the unit to reach the lowest power state before proceeding with the test measurement. Follow the test procedure specified in 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. If the standby mode is cyclic and irregular or unstable, collect 10 cycles worth of data.

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 Measurements 5.1 Adjusted Cooling Capacity

5.1.1 Single-Speed Adjusted Cooling Capacity. For a single-speed portable air conditioner, calculate the adjusted cooling capacity at each outdoor temperature operating condition, in Btu/h, according to the following equations.

For a single-duct single-speed portable air conditioner unit:

ACCSD_95_SS = CapacitySD − Qduct_SD − Qinflitration_SD_95 ACCSD_83_SS = CapacitySD − Qduct_SD − Qinflitration_SD_83

For a dual-duct single-speed portable air conditioner unit:

ACCDD_95_SS = Capacity95 − Qduct_DD_95 − Qinflitration_DD_95 ACCDD_83_SS = Capacity83 − Qduct_DD_83 − Qinflitration_DD_83 Where: CapacitySD, Capacity95, and Capacity83 = cooling capacity for each duct configuration or temperature condition measured in section 4.1.1 of this appendix. Qduct_SD, Qduct_DD_95, and Qduct_DD_83 = duct heat transfer for each duct configuration or temperature condition while operating in cooling mode, calculated in section 4.1.3 of this appendix. Qinfiltration_SD_95, Qinfiltration_SD_83, Qinfiltration_DD_95, Qinfiltration_DD_83 = total infiltration air heat transfer in cooling mode for each duct configuration and temperature condition, calculated in section 4.1.4 of this appendix.

5.1.2 Variable-Speed Adjusted Cooling Capacity. For variable-speed portable air conditioners, calculate the adjusted cooling capacity at each outdoor temperature operating condition, in Btu/h, according to the following equations:

For a single-duct variable-speed portable air conditioner unit:

ACCSD_95 = CapacitySD_Full − Qduct_SD_Full − Qinflitration_SD_95_Full ACCSD_83_Full = CapacitySD_Full − Qduct_SD_Full − Qinflitration_SD_83_Full ACCSD_83_Low = CapacitySD_Low − Qduct_SD_Low − Qinflitration_SD_83_Low

For a dual-duct variable-speed portable air conditioner unit:

ACCDD_95 = CapacityDD_95_Full − Qduct_DD_95_Full − Qinflitration_DD_95_Full ACCDD_83_Full = CapacityDD_83_Full − Qduct_DD_83_Full − Qinflitration_DD_83_Full ACCDD_83_Low = CapacityDD_83_Low − Qduct_DD_83_Low − Qinflitration_DD_83_Low Where: CapacitySD_Full, CapacitySD_Low, CapacityDD_95_Full, CapacityDD_83_Full, and CapacityDD_83_Low = cooling capacity in Btu/h for each duct configuration, temperature condition (where applicable), and compressor speed, as measured in section 4.1.2 of this appendix. Qduct_SD_Full, Qduct_SD_Low, Qduct_DD_95_Full, Qduct_DD_83_Full, and Qduct_DD_83_Low = combined duct heat transfer for each duct configuration, temperature condition (where applicable), and compressor speed, as calculated in section 4.1.3 of this appendix. Qinfiltration_SD_95_Full, Qinfiltration_SD_83_Full, Qinfiltration_SD_83_Low, Qinfiltration_DD_95_Full, Qinfiltration_DD_83_Full, and Qinfiltration_DD_83_Low = total infiltration air heat transfer in cooling mode for each duct configuration, temperature condition, and compressor speed, as calculated in section 4.1.4 of this appendix. 5.2 Seasonally Adjusted Cooling Capacity

5.2.1 Calculate the unit's seasonally adjusted cooling capacity, SACC, in Btu/h, according to the following equations:

For a single-speed portable air conditioner unit:

SACCSD = ACCSD_95_SS × 0.2 + ACCSD_83_SS × 0.8 SACCDD = ACCDD_95_SS × 0.2 + ACCSD_83_SS × 0.8

For a variable-speed portable air conditioner unit:

SACCSD = ACCSD_95 × 0.2 + ACCSD_83_Low × 0.8 SACCDD = ACCDD_95 × 0.2 + ACCDD_83_Low × 0.8 Where: ACCSD_95_SS, ACCSD_83_SS, ACCDD_95_SS, and ACCDD_83_SS = adjusted cooling capacity for single-speed portable air conditioners for each duct configuration and temperature condition, in Btu/h, calculated in section 5.1.1 of this appendix. ACCSD_95, ACCSD_83_Low, ACCDD_95, and ACCDD_83_Low = adjusted cooling capacity for variable-speed portable air conditioners for each duct configuration, temperature condition, and compressor speed, in Btu/h, calculated in section 5.1.2 of this appendix. 0.2 = weighting factor for the 95 °F test condition. 0.8 = weighting factor for the 83 °F test condition.

5.2.2 For variable-speed portable ACs determine a Full-Load Seasonally Adjusted Cooling Capacity (SACCFull_SD for single-speed units and SACCFull_DD for dual-duct units) using the following formulas:

SACCFull_SD = ACCSD_95 × 0.2 + ACCSD_83_Full × 0.8 SACCFull_DD = ACCDD_95 × 0.2 + ACCDD_83_Full × 0.8 ACCSD_95, ACCSD_83_Full, ACCDD_95, and ACCDD_83_Full = adjusted cooling capacity for variable-speed portable air conditioners for each duct configuration, temperature condition, and compressor speed (where applicable), in Btu/h, calculated in section 5.1.2 of this appendix. 0.2 = weighting factor for the 95 °F test condition. 0.8 = weighting factor for the 83 °F test condition.

5.3 Annual Energy Consumption. Calculate the sample unit's annual energy consumption in each operating mode according to the equation below. For each operating mode, use the following annual hours of operation and equation:

AECm = Pm × tm × 0.001 Where: AECm = annual energy consumption in the operating mode, in kWh/year. m represents the operating mode as shown in the table above with each operating mode's respective subscript. Pm = average power in the operating mode, in watts, as determined in sections 4.1.1 and 4.1.2. tm = number of annual operating time in each operating mode, in hours. 0.001 kWh/Wh = conversion factor from watt-hours to kilowatt-hours.

Calculate the sample unit's total annual energy consumption in off-cycle mode and inactive or off mode as follows:

Where: AECT = total annual energy consumption attributed to off-cycle mode and inactive or off mode, in kWh/year; AECm = total annual energy consumption in the operating mode, in kWh/year. ncm represents the following two non-cooling operating modes: off-cycle mode and inactive or off mode. 5.4 Combined Energy Efficiency Ratio

5.4.1 Combined Energy Efficiency Ratio for Single-Speed Portable Air Conditioners.

Using the annual operating hours established in section 5.3 of this appendix, calculate the combined energy efficiency ratio, CEER, in Btu/Wh, for single-speed portable air conditioners according to the following equation, as applicable:

Where: CEERSD and CEERDD = combined energy efficiency ratio for a single-duct unit and dual-duct unit, respectively, in Btu/Wh. ACCSD_95_SS, ACCSD_83_SS, ACCDD_95_SS, ACCDD_83_SS = adjusted cooling capacity for each duct configuration and temperature condition, in Btu/h, calculated in section 5.1 of this appendix. AECSD, AECDD_95 and AECDD_83 = annual energy consumption in cooling mode for each duct configuration and temperature condition, 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. 0.750 = number of cooling mode hours per year, 750, multiplied by the conversion factor for watt-hours to kilowatt-hours, 0.001 kWh/Wh. 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.

5.4.2 Unadjusted Combined Energy Efficiency Ratio for Variable-Speed Portable Air Conditioners.

For a variable-speed portable air conditioner, calculate the unit's unadjusted combined energy efficiency ratio, CEERUA, in Btu/Wh, as follows:

For single-duct variable-speed portable air conditioners:

For dual-duct variable-speed portable air conditioners:

Where: CEERSD_UA, and CEERDD_UA = unadjusted combined energy efficiency ratio for a single-duct and dual-duct sample unit, in Btu/Wh, respectively. ACCSD_95, ACCSD_83_Low, ACCDD_95, and ACCDD_83 = adjusted cooling capacity for each duct configuration, temperature condition, and compressor speed, as calculated in section 5.1.2 of this appendix, in Btu/h. AECSD_Full, AECSD_Low, AECDD_95_Full, and AECDD_83_Low = annual energy consumption for each duct configuration, temperature condition, and compressor speed in cooling mode operation, as calculated in section 5.3 of this appendix, in kWh/year. AECia/om = annual energy consumption attributed to inactive or off mode, in kWh/year, calculated in section 5.3 of this appendix. 0.750 = number of cooling mode hours per year, 750, multiplied by the conversion factor for watt-hours to kilowatt-hours, 0.001 kWh/Wh. 0.2 = weighting factor for the 95 °F dry-bulb outdoor temperature operating condition. 0.8 = weighting factor for the 83 °F dry-bulb outdoor temperature operating condition.

5.5 Adjustment of the Combined Energy Efficiency Ratio. Adjust the sample unit's unadjusted combined energy efficiency ratio as follows.

5.5.1 Theoretical Comparable Single-Speed Portable Air Conditioner Cooling Capacity and Power at the Lower Outdoor Temperature Operating Condition. Calculate the cooling capacity without and with cycling losses, in British thermal units per hour (Btu/h), and electrical power input, in watts, for a single-duct or dual-duct theoretical comparable single-speed portable air conditioner at an 83 °F outdoor dry-bulb outdoor temperature operating condition according to the following equations:

For a single-duct theoretical comparable single speed portable air conditioner:

CapacitySD_83_SS = CapacitySD_Full CapacitySD_83_SS_CF = CapacitySD_Full × 0.82 PSD_83_SS = PSD_Full

For a dual-duct theoretical comparable single speed portable air conditioner:

CapacityDD_83_SS = Capacity83_Full CapacityDD_83_SS_CF = Capacity83_Full × 0.77 PDD_83_SS = P83_Full Where: CapacitySD_83_SS and CapacityDD_83_SS = cooling capacity of a single-duct and dual-duct theoretical comparable single-speed portable air conditioner, calculated for the 83 °F dry-bulb outdoor temperature operating condition (Test Conditions 2.E and 2.B, respectively), in Btu/h. CapacitySD_83_SS_CF and CapacityDD_83_SS_CF = cooling capacity of a single-duct and dual-duct theoretical comparable single-speed portable air conditioner with cycling losses, in Btu/h, calculated for the 83 °F dry-bulb outdoor temperature operating condition (Test Conditions 2.E and 2.B, respectively). CapacitySD_Full and Capacity83_Full = cooling capacity of the sample unit, measured in section 4.1.2 of this appendix at Test Conditions 2.D and 2.B, in Btu/h. PSD_83_SS and PDD_83_SS = power input of a single-duct and dual-duct theoretical comparable single-speed portable air conditioner calculated for the 83 °F dry-bulb outdoor temperature operating condition (Test Conditions 2.E and 2.B, respectively), in watts. PSD_Full and P83_Full = electrical power input of the sample unit, measured in section 4.1.2 of this appendix at Test Conditions 2.D and 2.B, in watts. 0.82 = empirically-derived cycling factor for the 83 °F dry-bulb outdoor temperature operating condition for single-duct units. 0.77 = empirically-derived cycling factor for the 83 °F dry-bulb outdoor temperature operating condition for dual-duct units.

5.5.2 Duct Heat Transfer for a Theoretical Comparable Single-Speed Portable Air Conditioner at the Lower Outdoor Temperature Operating Condition. Calculate the duct heat transfer to the conditioned space for a single-duct or dual-duct theoretical comparable single-speed portable air conditioner at the 83 °F dry-bulb outdoor temperature operating condition as follows:

For a single-duct theoretical comparable single-speed portable air conditioner:

Qduct_SD_83_SS = Qduct_SD_Full

For a dual-duct theoretical comparable single-speed portable air conditioner:

Qduct_DD_83_SS = Qduct_DD_83_Full Where: Qduct_SD_83_SS and Qduct_DD_83_SS = total heat transferred from the condenser exhaust duct to the indoor conditioned space in cooling mode, for single-duct and dual-duct theoretical comparable single-speed portable air conditioners, respectively, at the 83 °F dry-bulb outdoor temperature operating condition (Test Conditions 2.E and 2.B, respectively), in Btu/h. Qduct_SD_Full and Qduct_DD_83_Full = the total heat transferred from the duct to the indoor conditioned space in cooling mode, when tested at Test Conditions 2.D and 2.B, respectively, as calculated in section 4.1.3 of this appendix, in Btu/h.

5.5.3 Infiltration Air Heat Transfer for a Theoretical Comparable Single-Speed Portable Air Conditioner at the Lower Outdoor Temperature Operating Condition. Calculate the total heat contribution from infiltration air for a single-duct or dual-duct theoretical comparable single-speed portable air conditioner at the 83 °F dry-bulb outdoor temperature operating condition, as follows:

For a single-duct theoretical comparable single-speed portable air conditioner:

Qinfiltration_SD_83_SS = Qinfiltration_SD_83_Full

For a dual-duct theoretical comparable single-speed portable air conditioner:

Qinfiltration_DD_83_SS = Qinfiltration_DD_83_Full Where: Qinfiltration_SD_83_SS and Qinfiltration_DD_83_SS = total infiltration air heat in cooling mode for a single-duct and dual-duct theoretical comparable single-speed portable air conditioner, respectively at the 83 °F dry-bulb outdoor temperature operating condition (Test Conditions 2.E and 2.B, respectively), in Btu/h. Qinfiltration_SD_83_Full and Qinfiltration_DD_83_Full = total infiltration air heat transfer of the sample unit in cooling mode for each duct configuration, temperature condition, and compressor speed, as calculated in section 4.1.4 of this appendix, in Btu/h.

5.5.4 Adjusted Cooling Capacity for a Theoretical Comparable Single-Speed Portable Air Conditioner at the Lower Outdoor Temperature Operating Condition. Calculate the adjusted cooling capacity without and with cycling losses for a single-duct or dual-duct theoretical comparable single-speed portable air conditioner at the 83 °F dry-bulb outdoor temperature operating condition, in Btu/h, according to the following equations:

For a single-duct theoretical comparable single-speed portable air conditioner:

ACCSD_83_SS = CapacitySD_83_SS − Qduct_SD_83_SS − Qinfiltration_SD_83_SS ACCSD_83_SS_CF = CapacitySD_83_SS_CF − Qduct_SD_83_SS − Qinfiltration_SD_83_SS

For a dual-duct theoretical comparable single-speed portable air conditioner:

ACCDD__83_SS = Capacity83_SS − Qduct_DD_83_SS − Qinfiltration_DD_83_SS ACCDD_83_SS_CF = CapacityDD_83_SS_CF − Qduct_DD_83_SS − Qinfiltration_DD_83_SS Where: ACCSD_83_SS, ACCSD_83_SS_CF, ACCDD_83_SS, and ACCDD_83_SS_CF = adjusted cooling capacity for a single-duct and dual-duct theoretical comparable single-speed portable air conditioner at the 83 °F dry-bulb outdoor temperature operating condition (Test Conditions 2.E and 2.B, respectively) without and with cycling losses, respectively, in Btu/h. CapacitySD_83_SS and CapacitySD_83_SS_CF = cooling capacity of a single-duct theoretical comparable single-speed portable air conditioner without and with cycling losses, respectively, at Test Conditions 2.E and 2.B (the 83 °F dry-bulb outdoor temperature operating condition), respectively, calculated in section 5.5.1 of this appendix, in Btu/h. CapacityDD_83_SS and CapacityDD_83_SS_CF = cooling capacity of a dual-duct theoretical comparable single-speed portable air conditioner without and with cycling losses, respectively, at Test Conditions 2.E and 2.B (the 83 °F dry-bulb outdoor temperature operating condition), respectively, calculated in section 5.5.1 of this appendix, in Btu/h. Qduct_SD_83_SS and Qduct_DD_83_SS = total heat transferred from the ducts to the indoor conditioned space in cooling mode for a single-duct and dual-duct theoretical comparable single-speed portable air conditioner, at Test Conditions 2.E and 2.B (the 83 °F dry-bulb outdoor temperature operating condition), respectively, calculated in section 5.5.2 of this appendix, in Btu/h. Qinfiltration_SD_83_SS and Qinfiltration_DD_83_SS = total infiltration air heat in cooling mode for a single-duct and dual-duct theoretical comparable single-speed portable air conditioner, respectively, at Test Conditions 2.E and 2.B (the 83 °F dry-bulb outdoor temperature operating condition), respectively, calculated in section 5.5.3 of this appendix, in Btu/h.

5.5.5 Annual Energy Consumption in Cooling Mode for a Theoretical Comparable Single-Speed Portable Air Conditioner at the Lower Outdoor Temperature Operating Condition. Calculate the annual energy consumption in cooling mode for a single-duct or dual-duct theoretical comparable single-speed portable air conditioner at the 83 °F dry-bulb outdoor temperature operating condition, in kWh/year, according to the following equations:

For a single-duct theoretical comparable single-speed portable air conditioner:

AECSD_83_SS = PSD_83_SS × 0.750

For a dual-duct theoretical comparable single-speed portable air conditioner:

AECDD_83_SS = PDD_83_SS × 0.750 Where: AECSD_83_SS and AECDD_83_SS = annual energy consumption for a single-duct and dual-duct theoretical comparable single-speed portable air conditioner, respectively, in cooling mode at the 83 °F dry-bulb outdoor temperature operating condition (Test Conditions 2.E and 2.B, respectively), in kWh/year. PSD_83_SS and PDD_83_SS = electrical power input for a single-duct and dual-duct theoretical comparable single-speed portable air conditioner, respectively, at the 83 °F dry-bulb outdoor temperature operating condition (Test Conditions 2.E and 2.B, respectively) as calculated in section 5.5.1 of this appendix, in watts. 0.750 = number of cooling mode hours per year, 750, multiplied by the conversion factor for watt-hours to kilowatt-hours, 0.001 kWh/Wh.

5.5.6 Combined Energy Efficiency Ratio for a Theoretical Comparable Single-Speed Portable Air Conditioner. Calculate the combined energy efficiency ratios for a theoretical comparable single-speed portable air conditioner without cycling losses, CEERSD_SS and CEERDD_SS, and with cycling losses, CEERSD_SS_CF and CEERDD_SS_CF, in Btu/Wh, according to the following equations:

For a single-duct portable air conditioner:

For a dual-duct portable air conditioner:

Where: CEERSD_SS and CEERSD_CF_SS = combined energy efficiency ratio for a single-duct theoretical comparable single-speed portable air conditioner without and with cycling losses, respectively, in Btu/Wh. CEERDD_SS and CEERDD_CF_SS = combined energy efficiency ratio for a dual-duct theoretical comparable single-speed portable air conditioner without and with cycling losses, respectively, in Btu/Wh. ACCSD_95 and ACCDD_95 = adjusted cooling capacity of the sample unit, as calculated in section 5.1.2 of this appendix, when tested at Test Conditions 2.D and 2.A, respectively, in Btu/h. ACCSD_83_SS and ACCSD_83_SS_CF = adjusted cooling capacity for a single-duct theoretical comparable single-speed portable air conditioner at the 83 °F dry-bulb outdoor temperature operating condition (Test Conditions 2.E) without and with cycling losses, respectively, as calculated in section 5.5.4 of this appendix, in Btu/h. ACCDD_83_SS and ACCDD_83_SS_CF = adjusted cooling capacity for a dual-duct theoretical comparable single-speed portable air conditioner at the 83 °F dry-bulb outdoor temperature operating condition (Test Condition 2.B) without and with cycling losses, respectively, as calculated in section 5.5.4 of this appendix, in Btu/h. AECSD_Full = annual energy consumption of the single-duct sample unit, as calculated in section 5.4.2.1 of this appendix, in kWh/year. AECDD_95_Full = annual energy consumption for the dual-duct sample unit, as calculated in section 5.4.2.1 of this appendix, in kWh/year. AECSD_83_SS and AECDD_83_SS = annual energy consumption for a single-duct and dual-duct theoretical comparable single-speed portable air conditioner, respectively, in cooling mode at the 83 °F dry-bulb outdoor temperature operating condition (Test Conditions 2.E and 2.B, respectively), calculated in section 5.5.5 of this appendix, in kWh/year. AECT = total annual energy consumption attributed to all operating modes except cooling for the sample unit, calculated in section 5.3 of this appendix, in kWh/year. 0.750 as defined previously in this section. 0.2 = weighting factor for the 95 °F dry-bulb outdoor temperature operating condition. 0.8 = weighting factor for the 83 °F dry-bulb outdoor temperature operating condition.

5.5.7 Performance Adjustment Factor. Calculate the sample unit's performance adjustment factor, Fp, as follows:

For a single-duct unit:

For a dual-duct unit:

Where: CEERSD_SS and CEERSD_SS_CF = combined energy efficiency ratio for a single-duct theoretical comparable single-speed portable air conditioner without and with cycling losses considered, respectively, calculated in section 5.5.6 of this appendix, in Btu/Wh. CEERDD_SS and CEERDD_SS_CF = combined energy efficiency ratio for a dual-duct theoretical comparable single-speed portable air conditioner without and with cycling losses considered, respectively, calculated in section 5.5.6 of this appendix, in Btu/Wh.

5.5.8 Single-Duct and Dual-Duct Variable-Speed Portable Air Conditioner Combined Energy Efficiency Ratio. Calculate the sample unit's final combined energy efficiency ratio, CEER, in Btu/Wh, as follows:

For a single-duct portable air conditioner:

CEERSD = CEERSD_UA × (1 + Fp_SD)

For a dual-duct portable air conditioner:

CEERDD = CEERDD_UA × (1 + Fp_DD) Where: CEERSD and CEERDD = combined energy efficiency ratio for a single-duct and dual-duct sample unit, in Btu/Wh, respectively. CEERSD_UA and CEERDD_UA = unadjusted combined energy efficiency ratio for a single-duct and dual-duct sample unit, respectively, calculated in section 5.4.2.1 of this appendix, in Btu/Wh. Fp_SD and Fp_DD = single-duct and dual-duct sample unit's performance adjustment factor, respectively, calculated in section 5.5.7 of this appendix. [81 FR 35265, June 1, 2016, as amended at 81 FR 70923, Oct. 14, 2016; 85 FR 21746, Apr. 20, 2020; 88 FR 31127, May 15, 2023]