### 1501 WILSON BOULEVARD**~.** 

### ARLINGTON, VIRGINIA 22209 

# 1981 STANDARD

# for

.IIP;



# ...I'.

AIR-CONDITIONING 

# &REFRIGERATION INSTITUTE 

# AIR-SOURCEUNITARY HEAT PUMP EOUIPMENT

I Standard 240 

# I

### PART Section 1. 

### Purpose TABLE OF CONTENTS



### PAGE

Section 2. Scope

. Section 3. Definitions 1 Section 4. Classification 2 Section 5. Testing and Rating Requirements 2 Section 6. Performance Requirements 5 Section 7. Safety Requirements 8 Section 8. Voluntary Conformance 8 Appendix A Uniform Test Method 8

FOREWORD


### This standard is prepared primarily for use in connection with, and is a part of, the ARI Air-Source Unitary Heat Pump Certification Program. ARI, as copyright owner of the standard, reserves the right at all times to question any claims ofconformance and to test the equipment of any manufacturer making such claims. It 

### is also understood that nonparticipantsin the ARI CertificationProgrambasedonthis standardshallhave norightto use the ARI certification symbol, or any facsimile or reproduction thereof, on any of their equipment or literature pertaining to said equipment.
This standard supersedes ARI Standard 240-77.

Price $11.00 Printed in U.S.A. © .cOPYRIGHT 1986, -byAir·Conditioning andRefrigeration Institute Registered United States Patentand Trademark Office

## ADDENDUM TO
ARI STANDARD 210-81 UNITARY AIR-CONDITIONING EQUIPMENT AND ARI STANDARD 240-81 AIR-SOURCE UNITARY HEAT PUMP EQUIPMENT FOR VARIABLE SPEED EQUIPMENT

Variable Speed Equipment shall be tested in accordance with one ofthe procedures referenced as follows: 1. 

### "D.O.E. Waiver From Test Procedure" to Carrier Corp, described in Case No. CAC-OOl (Federal Register Vol. 51 No. 192 pages 35403 through 35410).

2. DOE, Waiver From Test Procedure, to the Trane Company and modification ofCase No. CAC-OOl (to Carrier Corp) described in Case No. CAC-002 and CAC-OOl (Federal Register Vol. 52 No. 70 pages 11855 through 11863).

3. (open)

4. (open)

Note: Equipment with ratings established by one or more of the above procedures shall have the procedure(s) referenced, as above, in all published performance information for that equipment.

June, 1987

# ADDENDUM TO ARI STANDARD 210-81 UNITARY AIR-CONDITIONING EQUIPMENT

PART-LOAD RATING CONDITIONS FOR NON-DOE COVERED SYSTEMS WHICH ARE CAPABLE OF CAPACITY CONTROL SHALL BE RATED AT EACH STEP OF CAPACITY REDUCTION PROVIDED BY THE SYSTEM, AND ALLOWED BY THE CONTROLS, AT THE CONDITIONS SHOWN IN THE FOLLOWING TABLES.



### TABLE 1. FOR TWO SPEED, TWO COMPRESSORS, OR OTHER EQUIPMENT CAPABLE OF CAPACITY CONTROL
Indoor Outdoor Unit

Unit Air EnterinQ Water Air Entering Air Cooled Evaporative Cooled Cooled 

### Water Temp DB WB DB WB DB WB IN OUT TEST 

### F F 

### F F F F F F 

## <-' Standard Rating Conditions, Z 

### 75' 

## :::; a) Cooling 

### 80 67 95 95 75 85 95 0 65' 

### * 0 b) Cooling 

### 80 67 82 80 67 75 0
NOTES: *SAME WATER FLOWRATE AS OBTAINED IN TEST ABOVE. 'THE WET BULB TEMPERATURE CONDITION IS NOT REQUIRED WHEN TESTING AIR-COOLED CONDENSERS WHICH DO NOT EVAPORATE CONDENSATE.



### TABLE 2. FOR INFINITELY VARIABLE CAPACITY CONTROL EQUIPMENT Entering Air Indoor Unit Outdoor Unit DB WB DB WB TEST 

### F F F F Standard Rating Conditions,

Maximum compressor A 

### 80 67 95 75' speed, steady state 

### t' B 

### 80 67 82 65' Z Minimum Compressor 

## :::; a 

### 80 67 82 65' 0 speed, steady state 

### 0 b 

### 80 67 67 53.5' 0 Inlermediate cooling, steady slale, variable compressor speed2 

### 80 '67 87 69'
NOTES:

1 NOT REQUIRED IF CONDENSATE IS NOT REJECTED TO OUTDOOR COIL 2COMPRESSOR SPEED IS SELECTED TO PROVIDE CAPACITY EQUIVALENT TO 67% THE CAPACITY IN TEST A 

## )

## IPLV ADDENDUM TO ARI STANDARD 210-81
UNITARY AIR-CONDITIONING EQUIPMENT 65,000 BTU/H UP TO BUT LESS

THAN 135,000 BTU/H WHICH IS CAPABLE OF CAPACITY CONTROL AIRCOOLED SINGLE PHASE EQUIPMENT LESS THAN 65,000 BTUlH OR EQUIPMENT WITH NO CAPACITY CONTROL IS EXCLUDED FROM THE REQUIREMENT OF 5.2 OF THIS ADDENDUM. NOTE: THE EARLIER ADDENDUM COVERING PART LOAD RATING CONDITIONS (TABLE 1) SHALL APPLY TO EQUIPMENT WITHOUT MEANS OF CONTROLLED CAPACITY REDUCTION



### This addendum replaces 5.2

### through 5.4

### ofthe standard. 

### 5.2 PartLoadRating. 

### Systems which are capable ofcapacity reduction shall be rated at 100% 

### and at each step ofcapacity reduction provided by the refrigeration system(s) as published by the manufacturer. These rating points shall be used to calculate the IPLV (see 5.2.2). 

### (IPLV Defined: Integrated Part Load Value (IPLV). A single number part load efficiency figure of merit calculated per the method described in 5.2.2.) 

### 5.2.1 Part Load Rating Conditions. 

### The conditions of test for part load ratings are the same as for the Standard Ratings (See 5.1) 

### except for the following:


### 5.2.1.1 Part LoadRating 7emperatures. For all units 

### Air temperature entering indoor portion

ofunit 80 

### F [26.7°C] 

### dry bulb 67 

### F [19.4°C] 

### wet bulb For air-cooled units 

### Air temperature entering outdoor portion ofunit 80 

### F [26.7°C] 

### dry bulb (and 67 

### F [19.4 C] 

### wet bulb when condensate is rejected into the air stream) For evaporatively-cooled units 

### Air temperature entering outdoor portion

ofunit 80 

### F [26.7°C] 

### dry bulb 67 

### F [19.4OC] 

### wet bulb For water-cooled units 

### Water temperature entering

condenser 75 

### F [23.9°C] 

### Water flow rate (Same as Standard Rating Conditions)
5.2.1.2 The capacity reduction means may be adjusted to obtain the specified step ofunloading. No manual adjustment of indoor and outdoor air quantities from those ofthe Standard Rating Conditions shall be made. However, automatic adjustment ofoutdoor air quantities by system function is permissible. 5.2.2 Integrated Part Load Value (lPLV).For 

### equipment covered by this standard, the IPLV (in EER) shall be calculated as follows:
June, 1987 

### a. Determine the capacity and EER at the 'Conditions specified in 5.2. 

### b. Determine the part-loadfactor (PLF) from Figure 1 "Part-Load Factor Curve" at each rating point (see example in the Addendum's Appendix).
c. Use the following equation to calculate IPLV:

IPLV 

## = (PLF]

- PLF2) 

### (EER] ; EER2)



## + (PLF 2 - 

### PLF 3) 

### (EER2 ; 

### EER3)



## +

.


## + (PLF

_ PLF)

# (EER

n -] 

## + EERn ) n-] n 

### 2



## + (PLFn)(EERn )



### where: PLF = 

### Part-Load Factordetermined from Figure 1
n = 

### Total number ofcapacity steps Subscript 1 = 

### 100% 

### capacity and EER at part-load rating conditions Subscript 2; 3 etc. = 

### specific capacity and EER at part-load steps per 5.2.



### 5.3 Application Ratings. 

### Ratings at conditions of temperature or air quantity, other than those specified in 5.1.3 

### and 5.2.1 

### may be published as application ratings, and shall be based on data determined by the methods prescribed in this Section.

5.4 Publication ofRatings. 

### Whenever application ratings are published or printed, they shall include, or be accompanied by, the Standard Rating plus the PartLoad Rating (where applicable), clearly designated as such, including a statement of the conditions at which the ratings apply.
5.4.1 Capacity Designation. 

### The capacity designation used in published specifications, literature
or advertising, controlled by the manufacturer, for air-conditioners rated under this standard, are to

### 2 

### be expressed only ,in Btu/h [W] at the Standard Rating Conditions specifiedin5.1.3 plus PartLoad Rating Conditions specified in 5.2.1 and in the terms described in 5.1.1 and 5.1.2. Horsepower, tons, or other units shall not be used as capacity designations. 5.5 

## Tolerances. To complywith this standard, published cooling capacity and energy efficiency ratio and/or seasonal energy ratios shall be based on data obtained in accordance with the provisions ofthis section, and shall be such that anyproduction unit, whentested, willmeet these ratings except for an allowance to cover testing and manufacturing variations; the amount ofallowance to be minus 5 per cent.

June, 1987

### June, 1987 PART LOAD FACTOR CURVE

1.0 ./ 

## / Ii"'" 0.9 

# /

0.8 

# I

0.7 

# I 

# I Ii:' 0.6 ...J 0- 

# J a:: 

# f2 0.5 

# I U 

# I

0 0.4 

# If (§ 

# J ...J 

# I a:: 0.3 

# /

0.2 

# I /

0.1 

# /

PERCENT OF FULL-LOAD CAPACITY AT PART-LOAD CONDITIONS



### Note: Curve is Based on Following Equation: PLF = 

### AO + (AI 

### x Q)+(A2 x Q2) +(A3 X 

### Q3) +(A4x Q4)+(A5 x Q5)+ (A6x Q6) where: PLF = 

### Part-Load Factor Q 

## = Percent offull-load capacity at part-load rating conditions. AO = 

### -0.12773917 X 

### 10-6 Al = 

### -0.27648713 x 

### 10-3 A2 = 

### 0.50672449 x 

### 10-3 A3 = 

### -0.25966636 x 

### 10-4 A4 = 

### 0.69875354 x 

### 10-6 A5 = 

### -0.76859712 x 

### 10- 8 

### A6 = 

### 0.28918272 x 

### 10- 10



### FIGURE 1



### 3

## APPENDIX A METHOD AND EXAMPLE OF CALCULATING INTEGRATED PART LOAD VALUES (IPLV)

EERj 

## = 8.9 EER2 = 

### 7.7 EER3 

## = 7.1 EER4 = 

### 5.0

4 Section A1. Purpose and Scope



### AI.I Purpose. 

### A.I.I.I This appendix shows examplecalculations for determining Integrated Part Load Values (IPLV).



### AI.2 Scope. 

### A.I.2.1 This appendix is for equipment covered by this standard.

Section A2. Equations and Definitions of Terms



### A2.1 General Equation. 

### (EER + EER) IPLV 

## = (PLF1 - 

### PLF 2) \ 1 

### 2 2



### (EER2 

### + EER3) 

### + (PLF 2
- 

### PLF 3) 

### 2



## + .



## + (PLF
n _ 1 - 

### PLFn )

# (EER
n

- 12

## + EERn )

+ (PLFn)(EERn )
where: PLF = 

### Part-Load Factor determined from Figure 1
n 

## = Total number ofcapacity steps Subscript 1 

## = 100% capacity and EER at partload rating conditions Subscript 2; 3 etc. 

## = specific capacity steps per 5.2. Section A3. Calculation Example for a Four Capacity Step System


### A3.1 Unit Performance Data & 

### Sample Calculation. 

### A3.1.1 Assume equipment has four capacity steps as follows: • 100% (full load)

• 75% offull load

• 50% offull load

• 25% offull load 

### A3.1.2 Obtain partloadfactors from Figure 1 (see Figure Al Example). 

### A3.1.3 Obtain EER at each capacity step per 5.2. 

### A3.1.4 Calculate IPLV using the general equation with:

n = 

### 4 

### PLFj 

## = 1.0 PLF2 

## = 0.9 PLF3 = 

### 0.4 PLF4 = 

### 0.1
Enterthe above values in the general equation, (A2.1).

IPLV 

## = (1.0_0.9)(8.9 ; 7.7)



## + (0.9-0.4)C.7 ; 7.1)

)(7.1+5.0) + (0.4-0.1 2 +(0.lx5.0)

= 

### (0.1 x 8.3) + (0.5 x7.4) + (0.3 x 6.0) + 0.5



## = 0.83 + 3.70 + 1.80 + 0.5 IPLV 

## = 6.83 rounded to 6.8 To further illustrate the calculationprocess see Figure A2 Example.

June, 1987

## APPENDIX A

PART LOAD FACTOR CURVE



# - 1.0 r" 

## .... ./ 

## / 0.9 

# - I

0.8 

# I ,

0.7 

# I I LL I
...J 0.6 Cl. 

# J 

# , a: 

# I 0.5 () 

# I Lt 0 0.4 

# I (§



# -- .... J ...J 

# I a: 0.3 

# g: 

# / ) 0.2 

# J 

# /

0.1 

# /

100 80 60 40 

# ..,/ 

# ,**O""",,,~I--......I...L.~_....Io._..a-_** .....

_ .......**I.....I_"""'_~** 

### o 20

PERCENT OF FULL-LOAD CAPACITY AT PART-LOAD CONDITIONS



### Note: Curve is Based on Following Equation: PLF = 

### AO + (AI x Q) 

### +(A2 X 

### Q2) 

### + (A3 X 

### Q3) 

### + (A4x Q4) 

### + (AS X 

### Q5) 

### + (A6x Q6) 

### where: PLF 

## = Part-Load Factor Q 

## = Percent offull-load capacity at part-load rating conditions. AO = 

### -0.12773917 X 

### 10- 6 

### Al = 

### -0.27648713 x 

### 10- 3 

### A2 = 

### 0.50672449 x 

### 10- 3 

### A3 = 

### -0.25966636 x 

### 10- 4 

### A4 = 

### 0.69875354 x 

### 10- 6 

### AS = 

### -0.76859712 X 

### 10- 8 

### A6 = 

### 0.28918272 x 

### 10- 10



### FIGURE A1 

### June, 1987 S

### 6 

## APPENDIX A

FIGURE A-2 EXAMPLE

IPLV CALCULATION 

### Using information from A3.1.1; A3.1.2 and A3.1.3

Capacity Mfrs. Net % Full PLF' Mfrs. Part Avg. Part PLF Diff. Weighted

Step Cap. (Tons) Load Cap.' Load EER Load EER Avg. EER x PLF Diff. = Avg. (For R Only)

1 50.0 100% 1.0 8.9'

= 8.3 (1.0-0.9)=0.1 8.3 x 0.1 = 0.83 2 37.5 75% 0.9 7.7

= 7.4 (0.9

- 0.4) =0.5 7.4 x 0.5 = 3.70 3 25.0 50% 0.4 7.1

= 6.0 (0.4-0.1)=0.3 6.0 x 0.3 = 1.80 4 12.5 25% 0.1 5.0

= 5.01 (0.1-0.0)=0.1 5.01 x 0.1 0.50

----- 0% 0.0

----- Single number IPLV 6.83*

*Rounded to 6.8 NOTES IFor the range between 0% capacity and the last capacity step, use EER ofthe last capacity step for the average EER. 'The 100% capacity and EER are to be determined at the part-load rating conditions. 3Part-load factor from Figure AI.



### June, 

### 1987

### A'RI STANDARD 

### 240-81 

# AIR-SOURCE UNITARY HEAT PUMP EQUIPMENT

Section 1. Purpose 

### 1.1 Purpose. The purpose ofthis standardisto establish, for air-source unitary heat pump equipment: definitions and classification; requirements for testing and rating; specifications, literature and advertising requirements; performance requirements; safety requirements; and conformance conditions. 1.1.1 This standard is intended for the guidance of the industry, including manufacturers, distributors, consultants, contractors, and consumers. 

### 1.2 Review andAmendment. This standard is subject to review and amendment as the art of the industry advances. Section 2. Scope 

### 2.1 Scope. This standard applies to factory-made residential, commercial, and industrial air-source unitary heat pumps, as defined in 3.1. 

### 2.1.1 Energy Source. This standard applies only to electrically-driven, mechanical compression type systems. 

### 2.2 Exclusions. This standard does not apply to the rating and testing of individual assemblies for separate use, nor to room air-conditioner or packaged terminal heat pumps. norto unitary heatpumpsas defined in ARI Standard 340, with capacities of 135,000 Btuh [40 kW]
orgreater, nor to water-source heat pumps as defined in ARI Standard 320.
Section 3. Definitions 

### 3.1 Air-Source Unitary Heat Pump. An 

### air-source unitary heatpump consists ofone or more factory-made assemblies which normally include an indoorconditioning coil, compressor(s) and outdoor coil, including
means to provide a heating function and may optionally include a cooling function. When such equipment is provided in more than one assembly, the separated assemblies shall be designed to be used together, and the requirements ofrating outlinedin the standard are based upon the use of matched assemblies. 

### 3.1.1 Functions. Unitary heat pumps shall provide the function of heating with controlled temperature. and may include the functions of air-cooling, air-circulating, air-cleaning, dehumidifying or humidifying. 

### 3.2 Published Rating. A statement of the assigned values of those performance characteristics, under stated rating conditions, by which a unit may be chosen to fit its application. Thesevalues applyto allunits oflike nominal size and type (identification) produced by the
same manufacturer. As usedherein, the term "published rating" includes the rating of all performance characteristics shown on the heat pump orpublishedin specifications, advertising, or otherliterature controlled by the manufacturer, at stated rating conditions. 

### 3.2.1 StandardRating. A rating based on tests performed at Standard Rating Conditions. 

### 3.2.2 Application Rating. A rating based on tests performed at application rating conditions (other than Standard Rating Conditions). 

### 3.3 Rating Conditions. Any set ofoperating conditions under which a single level of performance results, and which causes only that level ofperformance to occur. 

### 3.3.1 Standard Rating Conditions. Rating conditions used as the basis of comparison of performance characteristics. 

### 3.4 Energy Efficiency Ratio (EER). A ratio calculated by dividing the cooling capacity in Btuh by the power input in watts at any given set of rating conditions, expressed in Btuh per watt (Btuh/watt). 

### 3.4.1 Standard Energy Efficiency Ratio. A ratio calculatedfrom the capacity and powerinput values obtained at Standard Rating Conditions.


### 3.5 Seasonal Energy EfficiencyRatio (SEER). Seasonal Energy Efficiency Ratio means the total cooling of a unitary heat pump Btu's during its normal usage period for cooling (not to exceed 12 months) divided by the totalelectric energy input in watt-hours during the same period, as determined in Appendix A. 

### 3.6 Coefficient ofPerformance (COP). A ratio calculated by dividing the total heat capacity provided by the refrigeration system including circulating fan heat but excluding supplementary resistance heat, (Btuh) by the total electrical input (watts) x 3.412. [A ratio calculated for both cooling and heating capacities by dividing capacity in watts by power input in watts.] 

### 3.6.1 Standard Coefficient of Performance. A ratio calculatedfrom the capacity andpowerinputvalues (obtained in accordance with 3.6) at Standard Rating Heating Conditions. 

### 3.7 Heating Seasonal Performance Factor (HSPF). HSPF is the total heating output ofa heat pump during its normal annual usageperiodforheating divided by the total electric power input during the same period, as determined in Appendix A.

1

### ARt STANDAR 0 

### 240·81

_
3.8 "Shall", "Should", "Recommended", or "ItIs Recommended". "Shall", "should", "recommended" or"it is f"ecommended" shall be interpreted as follows: 

### 3.8.1 Shall. Where "shall" or "shall not" is used for
a provision specified, that provision is mandatory if compliance with the standard is claimed. 

### 3.8.2 Should, Recommended, or It Is Recommended. "Should", "recommended", or "It 

### is recommended" is used to indicate provisions which are not mandatory but which are desirable as {?,ood practice.
Section 4. Classification 

### 4.1 Classification. Normally, air-source unitary heat pumps within the scope ofthis standardmaybe classified
as shown in Table 1.

Section 5. Testing and Rating Requirements 

### 5.1 Standard Ratings. Standard ratings shall be established at the Standard Rating Conditions specified in 5.1.3. All standard ratings shall be verified by tests conducted in accordance with the ANSI!ASHRAE Standard 37-1978 

### Methods ofTesting for Rating Unitary Air-Conditioning and Heat Pump Equipment (American Society of Heating, Refrigerating and AirConditioning Engineers, Inc.), andwith thetestmethods and procedures as described in this standard. 

## t
In addition, Seasonal Energy Efficiency Ratio (SEER) (not required for heating-only units) and Heating Seasonal Performance Factor (HSPF) shall be determined for units rated less than 65,000 Btuh cooling capacity and with single-phase power input in accordance with Appendix A. Other equipment within the scope of this standard may have the SEER and HSPFdetermined (as
an applicationrating) inaccordancewithAppendixA, at the option ofthe manufacturer. Standard Ratings relating to cooling or heating capacities shall be net values, including the effects of circulating-fan heat, but not including supplementary heat. Power input shall be the total power input to the compressor(s) and fanes), plus controls and other items included as part ofthe model number(s).
Standard Ratings of units which do not have indoor air-circulating fans furnished as part ofthe model, i.e., split system with indoorcoil alone (See Table 1), shall be established by subtracting from the total cooling capacity 1,250 Btuh/lOOO dm [0.78 watts per tis], 

### and by adding the same amount to the heating capacity. Total power input for both heating and cooling· shall be increased by 365 watts/lOOO dm [0.78 watts per tis] 

### of indoor air handled. Units equipped with desuperheater/water heaters shall be rated in accordance with ARI Standard 290.

2 

### 5.1.1 Values ofStandard Capacity Ratings. These ratings shall be expressed only in terms ofBtu per hour (Btuh) [watts] in multiples of: Capacities Multiples (Btuh (W] (Stuh) (WI Less than 20,000(5,900] 100(30] 20.000-37.800(5.900-11,000] 200(60] 38.000-64.500(11.100-18,900] 500(160] 65.000 and above (19.000] 1000(300] 

### 5.1.2 Values ofMeasures ofEnergy Efficiency. Standard measure of energy efficiency, whenever published, shall be expressed in multiples of the nearest 0.05 BtuhlW for EER, SEER and HSPF. Coefficients of performance (COP) for heating or cooling, whenever published, shall be expressed in multiples ofthe nearest 0.02. 

### 5.1.3 Standard Rating Conditions. The conditions oftestforStandard Ratings shallinclude the following:



### 5.1.3.1 StimdardRating Temperatures.

a. 

### Cooling (Not required for heating-only units) 

### For all units Air temperature entering indoor

portion ofunit

.. 80 F [26.7°C] dry bulb, 67 F [l9.4°C] wet bulb Air temperature surrounding unit 95 F [3SOC] dry bulb* Air temperature entering outdoor

portion ofunit

.. 95 F [3SOC] dry bulb, (and 75 F [23.9°C] wet bulb when condensate is rejected to the air stream) b. 

### High Temperature Heating For all units Air temperature entering indoor

portion ofunit

.. 70 F [21.1 0c] 

### dry bulb, 60 F [l5.6°C] wet bulb, max. 'For units or portions thereofintended to be installed only indoors, this temperature may be changed to be the same as the air temperature entering the indoor portion ofunit.
"tAll tests required to obtain Standard Ratings for single phase equipment rated less than 65,000Stuh (DOE covered) shall be conducted in accordance with Appendix A. All tests required to obtain Standard Ratings for equipment which is poly phase or 65,000 Stuh or more (non-DOE covered) shall be conducted in accordance with ANSIIASHRAE 37-1978.

### _________________________ A R 

### I STAN DARD 240·81

Table 1-Classification of Unitary Heat Pumps
Types ofUnitary Air-Source Heat Pumps


### t ARI Type Designation Heating and Heating Only Arrangement Cooling
Single Package HSP-A HOSP-A FAN COMP INDOOR OUTDOOR

COIL COIL

Remote Outdoor Coil HRC-A-CB HORC-A-CB FAN INDOOR OUTDOOR

COIL COIL COMP

Remote Outdoor Coil HRC-A-C HORC-A-C INDOOR OUTDOOR

with No Indoor Fan COIL COIL COMP

Split System HRCU-A-CB HORCU-A-CB FAN COMP INDOOR OUTDOOR

COIL COIL

Split System with HRCU-A-C HORCU-A-C COMP

No Indoor Fan INDOOR OUTDOOR COIL COIL



### tA suffix of"-0" following any ofthe above classifications indicates equipment not intended for use with field-installed duct systems (See 5.1.3.7).



### Air temperature surrounding unit 47 F [8.3°C] 

### dry bulb*
Air temperature entering outdoor

portion ofunit

.. 47 F [8.3°C] 

### dry bulb, 43 F 

### [6.1°C] 

### wet bulb

c. 

### Low Temperature Heating Air temperature entering indoor

portion ofunit

.. 70 F 

### [21.1 0c] 

### dry bulb, 60 F 

### [l5.6°C] 

### wet bulb, max.

'For units or portions thereofintended to be installed only indoors, this temperature may be changed to be the same as the air temperature entering the indoor portion ofunit. 

### Air temperature surrounding unit 17 F [-8.3°C] 

### dry bulb* Air temperature entering outdoor

portion ofunit

.. 17 F [-8.3°C] 

### dry bulb, 15 F



### [-9.4°C] 

### wet bulb



### 5.1.3.2 Measures ofEnergy Efficiency. SEER's and HSPFs shall be determined at the appropriate temperature conditions shown in Appendix A. 

### 5.1.3.3 Electrical Conditions. Recommended nameplate voltages are shown in Table 1 ofARI Standard 110 for 

### Air-Conditioning and Refrigerating Equipment Nameplate Voltages.

3

### ARI STAN DAR 0 240-81

_



### 4 Standard Rating tests shall be performed at the nameplate -rated voltage(s) and frequency.
Forheat pumps with dual nameplate voltage ratings, Standard Rating tests shall be performed at both voltages, oratthe lowerofthe two voltages, ifonly a singleStandardRatingistobepublished. 

### 5.1.3.4 

### Indoor-side Air Quantity. All Standard Ratings shall be determined at an indoor-side air quantity, delivered against at least the minimum external resistance required by 5.1.3.7, as outlined below. All air quantities shall be expressed
as cfm [tis]

### .ofStandard Air (density 0.0751b per cu ft [1.2 kg/m3]).



### a. Heat pumps shall be rated at the indoorside air quantity (not to exceed 37.5 scfm per 1000 Btuh [0.06 tis 

### per watt] ofrated capacity) delivered when operating against the minimum external resistance specified in 5.1.3.7 oratalowerindoor-side airquantity ifso specified by manufacturer. b. Heat pumps which do not incorporate an indoor fan, but are rated in combination with a device employing afan shall be rated
as described under a. above. For heat pumps ofthis class which are rated forgeneral use to be appliedto avariety ofheating plants, the indoor side air quantity shall be
as specifiedby the manufacturerinhis standard ratings, not to exceed 37.5 scfml1000 

### Btuh [0.06 tis

### perwatt] ofrated capacity or the air quantity obtained through the indoor coil assembly when the pressure drop
across the indoorcoil assembly andthe recommended enclosures and attachment
means is not greater than 0.30 inches of water [74.7 Pa], whichever is less.
Indoor-side air quantities as referred to herein apply to the air quantity experienced when the unit is cooling anddehumidifyingunderthe Standard Rating Conditions specified in this section. Heating-only units shall use the air quantity experienced when the unit is operating under the Standard High Temperature Heating Rating Conditions. This air quantity, except as noted in 6.4, shallbeemployedinallothertestsprescribed herein without regard to resulting external static pressure.



### 5.1.3.5 

### Outdoor-sideAir Quantity. All Standard Ratings shall be determined at the outdoor-side air quantity specified by the manufacturer where the fan drive is adjustable; or, where the fan drive is non-adjustable, they shall be determined at the outdoor-side air quantity inherent in the heat pump when operated with all of the resistance elements associated with inlet louvers and any ductwork and attachments considered by the manufacturer as normal installation practice. Once established, the outdoor-side air circuit of the heat pump shall remain unchanged throughout all tests prescribed herein.


### 5.1.3.6 

### Requirementsfor Separated Assemblies. All Standard Ratings for heatpumps in which the outdoor sectionis separatedfrom the indoor section, as in Types HRC, HORC, HRCU, and HORCU (shown in Section 4), shall be determined with at least 25 feet

## I7.62 m] ofinterconnection tubing on each line, of the size recommendedbythe manufacturer. Suchheatpumpsin which the interconnection tubing is furnished as an integral partofthe machine notrecommended for cutting to length shallbe tested with the complete length of tubing furnished, or with 25 feet [7.62 m] oftubing, whichever is greater. At least 10 feet [3.05 m] of the interconnection tubing shall be exposed to the outside conditions, with the rest ofthe tubing exposedto 

## theinside conditions. The line sizes, insulation, and details of installation shallbe in accordance with the manufacturer's published recommendations.



### 5.1.3.7 

### Minimum External Resistance. Indoor air-moving equipmentintendedfor use with field installedductsystemsshallbedesignedtooperate against, and tested at not less than, the minimum external resistance shown in Table 2 when delivering the rated capacity and airquantity specified in 5.1.3.4. Indoor air-moving equipment not intended for use with field installed duct systems shall be tested at 0 in. water [0 Pa] external pressure. In interpreting this requirement, it is understood that the most restrictive filters, supplementary heating coils, and other equipment recommended as optional parts ofthe heap pump be in place and that the net external resistances specifiedabove are availableforthe external duct system.
5.2 

### Application Ratings. Ratings at conditions of temperature or air quantity other than those specified in 5.1.3, may be published as application ratings, and shall be based on data determinedby the methods prescribed in 5.1. Application ratings in the defrost region shall include net capacity and COP based upon a complete defrost cycle.

### _________________________ A R I STANDARD 240-81

Table 2. Minimum External Resistance

'Standard Capacity Ratings

(Thousands ofBtuh)

Up thm 28.8 29 thm 42.5 43 thru 70 71 thru 105 106 thru 134 [kW]

up thru 8.4 8.5 thru 12.5 12.6 thru 20.5 20.8 thru 30.8 31.1 thru 39.3 Minimum External Resistance

(Inches of

Water) [Pal

0.10 24.9 0.15 37.4 0.20 49.8 0.25 62.3 0.30 74.7

'Cooling Capacity for units with cooling function; High Temperature Heating Capacity for heating-only units (See 5.1.3.4)



### 5.3 Publication ofRatings. Wherever application ratings are published or printed, they shall include, or be accompanied by, the Standard Capacity Ratings and theircorrespondingefficiency ratings, clearly designated
as such, including a statement ofthe conditions at which the ratings apply. 

### 5.3.1 Capacity Designation. The capacity designation used in published specifications, literature or advertising, controlled by the manufacturer, for heat pumps rated under this standard, are to be expressed only in Btuh [watts] at the Standard Rating Conditions specified in 5.1.3 and in terms described in 5.1.1 and 5.1.2. Horsepower, tons, or other units shall not be used as capacity designations. 

### 5.4 Tolerances. To comply with this standard, published cooling capacity, heat capacity(s) and efficiency ratings, shall be based on data obtained in accordance with the provisions of this section, and shall be such that any production unit, when tested, will meet these ratings exceptforan allowance to covertesting and manufacturing variations; the amount of allowance to be minus 5 per cent.

Section 6. Performance Requirements 

### 6.1 Performance Requirements. To comply with this standard, air-source unitary heat pumps shall be designed and produced in accordance with the provisions ofthis section in such a mannerthat any production unit will meet the requirements detailed herein. 

### t6.2 Maximum Operating Conditions Test. Air-source

unitary heat pumps shall be designed and produced to pass the following maximum operating conditions test with an indoor side coil air quantity as determined under 5.1.3.4: 

### 6.2.1 Temperature Conditions.

6.2.1.1 Cooling. {Not required for heating-only units) Air temperature surrounding unit 115 F [46.10c] 

### dry bulb* Air temperature entering indoor

portion ofunit

.. 80 F [26.7°C] dry bulb, 67 F [l9.4°C] wet bulb Outside air

temperature

.. 115F [46.1 0c] 

### dry bulb (and 75 F [23.9°C] wet bulb when condensate is rejected to the condenser air stream) at the standard condenSer air quantity specified and stated by the manufacturer.

tThis test will become effective on publication ofthis standard, at the

manufacturer's option. but not later than January I, 1982. In the interim period, ifthe manufacturerdoes not elect the new test procedures, the requirements for this test are those shown in 6.2 ofARI Standard 240-77.

"Forunits orportionsthereofintendedto be installedonlyindoors, this temperature may be changed to be the same as the air temperature entering the indoor portion ofunit.



### 5

### A RI STAN DA R 0 

### 240·81

_
6.2.1.2 Heating. Air temperature entering indoor

portion ofunit

.. 80 F [26.7°C] dry bulb
Air temperature surrounding

unit 75 F [23.9°C] dry bulb*
Outside air

temperature

.. 75 F [23.9°C] dry bulb, 65F [18.3°C] wet bulb



### 6.2.2 Voltages. Tests shall be run at the Range A minimum utilization voltage from ARI Standard 110, Table 1, based upon the unit's nameplate rated voltage(s). This voltage shall be supplied at the unit's service connection and at rated frequency. 

### 6.2.3 Procedure. The heat pump shall be operated for one hour at the temperature conditions and voltage specified. 

### 6.2.4 Requirements. The heat pump shall operate continuously without interruption for any reason for one hour. 

### t6.3 Voltage Tolerance Test. Air-source unitary heat pumps shall be designed and produced. to**p~ss** 

### .the following voltage tolerance testwith acoolmgcoIl aIrquantity as determined under 5.1.3.4. 

### 6.3.1 Temperature Conditions. Temperature conditions shall be maintained as shown in 5.1.3.1.a (or in 5.1.3.1.b for heating only units). 

### 6.3.2 Voltages. 6.3.2.1 Tests shall be run at the range B minimum and maximum utilizationvoltagesfrom ARI Standard 110, Table 1, based upon the unit's nameplate rated voltage(s). These voltages shall be supplied atthe unit's service connection and at ratedfrequency. A lowerorahighervoltage shall be used, iflisted on the nameplate. 

### 6.3.2.2 The power supplied to the heat pump shall be adjusted just prior to the shut down period (See 6.3.3.2) so that the resulting voltage

'For units or portions thereof intended to be installed only indoors, this temperature may be changed to be the same as the au temperature entering the indoor portion ofunit.

tThis test will become effective on publication ofthis standard, at the manufacturer's option, but not later than January 1, 1982. In the interim period, ifthe manufacturerdoes not electthe new test procedures. the requirements for this test are those shown in 6.2 of ARI Standard 240-77.



### 6 at the unit's service connection is 86 per cent of nameplate rated voltage when the compressor is
on lockedrotor. Forthe purpose ofthis standard, the compressor nameplate locked-rotor amperes may be used to determine this voltage. The proper value of no-load voltage which will give the specified voltage at locked-rotor conditions should be determined prior to the test. The locked-rotorcurrentvalue ofany motorshall be measured as follows:

a. All hermetic compressor motors shall be tested as a compressor assembly. b. The motor winding temperature shall not exceed 77 F [25°C] when the voltage is applied.

c. The current reading shall be taken within four seconds after the voltage is applied. If 

### the testis repeated, the motor winding shall be allowed to cool to 77 F [25°C] or lower before the current is reapplied. d. The voltage at the unit service connection, at the time the current reading is taken, shall be the manufacturer's nameplate rated voltage.

e. The locked-rotorcurrent shall be measured with an ammeter, with the rotor actually locked. 

### 6.3.2.3 Within one minute after the heat pump has resumed continuous operation (See 6.3.4.3), the voltage shall be restored to the values specified in6.3.2.1. 

### 6.3.3 Procedure. 6.3.3.1 The heat pump shall be operated for one hour at the temperature conditions and voltage(s) specified. 

### 6.3.3.2 All power to the heat pump shall be cut offfor a period sufficient to'Cause the compressor to stop (not to exceed five se'Conds) and then restored. 

### 6.3.4 Requirements.

6.3.4.1 During both entire tests, the heat pump shall operate without failure ofany ofits parts. 

### 6.3.4.2 The heat pump shall operate continuously without interruption for any reason for the
one hour period preceding the power interruption. 

### 6.3.4.3 The unit shall resume 'Continuous operation within two hours ofrestoration ofpower and shall then operate continuously for one halfhour.

### _________________________ A RI STANDAR 0 240-81


### Operation and resetting ofsafety devices prior to establishment ofcontinuous operation is permitted. 6.4 

### Low-Temperature Operation Test (Cooling). (Not required for heating-only units) Air-source unitary heat pumps shall be designed and produced to pass the following low-temperature operation test with initial air quantities as determined in 5.1.3.4 and 5.1.3.5, and with controls and dampers set to produce the maximum tendency to frost or ice the evaporator, provided such settings are not contrary to the manufacturer's instructions to the user:
6.4.1 

### Temperature Conditions. Air temperature entering indoor

portion ofunit

.. 67 F [l9.4°C] dry bulb, 57 F [13.9°C] wet bulb Outside air temperature

.. 67 F [l9.4°C] dry bulb, 57 F [13.9°C] wet bulb*
6.4.2 

### Procedure. The test shall be continuous with the unit on the cooling mode, for not less than four hours after establishment ofthe specified temperature conditions. The unit will be permitted to operate under control of an automatic limit device, if provided.
6.4.3 

### Requirements.

6.4.3.1 During the entire test, the heat pump shall operate without damage to the equipment. 

### 6.4.3.2 During the entire test, the air quantity shall not drop more than 25 percent from that determined under the Standard Rating test. 

### 6.4.3.3 During the test, and during the defrosting period after the completion ofthe test, all ice
or meltage must be caught and removed by the drain provisions.
6.5 

### Insulation Efficiency Test (Cooling). (Not required for heating-only units) Heat Pumps shall be designed and produced to pass the following insulation efficiency test when operating with air quantities as determined in 5.1.3.4 and 5.1.3.5 with controls, fans, dampers and grilles set to produce the maximum tendency to sweat, provided such settings are not contrary to the manufacturer's instructions to the user.

*The wet-bulb temperature condition is not required when testing air-source heat pumps which do not evaporate condensate. 

### 6.5.1 

### Temperature Conditions. Air temperature entering

and surrounding indoor portion ofunit 80 F [26.7°C] ry bulb, 75 F [23.9°C] wet· bulb Outside air temperature

.. 80 F [26.7°C] dry bulb, 75 F [23.9°C] wet bulb* 6.5.2 

### Procedure. After establishment of the specified temperature conditions, the unit shall be operated continuously for a period offour hours. 6.5.3 

### Requirements. During the test, no condensed water shall drip, run, or blow off from the unit casing. 6.6 

### Condensate Disposal Test (Cooling). ** (Not required for heating-only units) Heat pumps which reject condensate to the condenser air shall be designed and produced to pass the following condensate disposal test when operating with air quantities as determined in 5.1.3.4 and 5.1.3.5 and with controls anddampers set to producecondensateatthe maximumrate, provided such settings are not contrary to the manufacturer's instructions to the user: 6.6.1 

### Temperature Conditions. Air temperature entering

and surrounding indoor portion ofunit 80 F [26.7°C] drybulb, 75 F [23.9°C] wet bulb Outside air temperature

.. 80 F [26.7°C] dry bulb, 75 F [23.9°C] wet bulb 6.6.2 

### Procedure. After establishment of the specified temperature conditions, the heat pump shall be started with its condensate collection pan filled to the overflowingpoint and shall be operated continuously for four hours after the condensate level has reached equilibrium. 6.6.3 

### Requirements. During the test, there shall be
no dripping, running-off, orblowing-offofmoisture from the unit casing.

*The wet-bulb temperature condition is not required when testing air-source heat pumps which do not evaporate condensate.

**This testmayberuni:oncurrentiywiththeInsulation EfficiencyTest

(See 6.5).



### 7

### ARI STANDARD 240-81



### 6.7 Tolerances. The conditions for the tests outlined in 6.2, 6.3, 6.4, 6:5 and 6.6 are average values subject to tolerances of ±1.0 F [±O.56°C] for air wet-bulb and dry-bulb temperatures and ±1.0 percent ofthe reading for voltages.
Section 7. Safety Requirements 

### 7.1 Refrigerating System. It is strongly recommended that the refrigerating system be designed, constructed, and assembled so as to be in accordance with the ANSIIASHRAE Standard 15-1978 

### Safety CodeforMechanical Refrigeration (American Society of Heating, Refrigerating and Air-Conditioning Engineers, Inc.) 

### 7.2 Product Safety. It is strongly recommended that unitary heat pumps be designed, constructed, and assembled so as to meet the safety requirements of UL Standard for 

### HeatPumps (Underwriters' Laboratories, Inc. Standard 559, 1975 (Rev. 1979).
Section 8. Voluntary Conformance 

### 8.1 Conformance. Conformance withthis standardshall notbe claimedorimpliedforunitaryheatpumpscoming within the scope ofthis standard unless the unitary heat pumps for whiCh such claims are made meet all the performance, safety and rating requirements specified herein.

APPENDIX A 

## *Uniform Test Method for Measuring the Energy Consumption of Central Air-Conditioners Appendix Mto SubpartB-Unifonn Test 1.10 

### "Cyclic Test" means a test where the 1.19 

### "Seasonal energy efficiency ratio Method for Measuring the Energy indoorand outdoor conditions are held (SEER)" means the total cooling ofa central Consumption ofCentral AirConditioners constant. but the unit is manually turned "on" air conditionerin Btu's during its normal and "off' for specific time periods to simulate annual usage periodfor cooling divided by 1. Definitions part-load operation. the total electricpowerinputin watt-hours

1.1 "Annual performance factor" 1.11 "Degradation coefficient (Cn )" means during the same period. means the total hellting and cooling the measure ofthe efficiency loss due to the 1.20 "Sensible cooling" means the amount done by a heat pump in a particular cycling ofthe unit. ofcooling inBtu's perfonnedby a unit over a region in one year divided by the total 1.12 

### "Demand-defrost control system" period oftime. excluding latentcooling. electric powerused 

### in one year. means a system which is designed to perform 1.21 "Single package unit" means any

1.2 

### "ARI" means Air-Conditioning and the defrostfunction on the outdoor coil ofthe central airconditionerin which all the major Refrigeration Institute. heat pump only when a predetennined assemblies are enclosed in one cabinet.

1.3 

### "ARI Standard 210-79" 

### means the test degradation ofperformance is measured. 1.22 

### "Split system" means any central air standard publishedin 1979 

### by the ARI and 1.13 

### "Design heating requirement (DHR)" conditionerin which one ormore ofthe major titled "Standardfor Unitary Air-Conditioning is the amount ofheating reqUired to maintain assemblies are separate from the others. Equipment". a given indoortemperature at a particular 1.23 

### "Steady-state test" means a testin

1.4 

### "ARI Standard 240-77" 

### means the test outdoordesign temperature. which all indoorand outdoorconditions are standardpublished in 1977 

### by the ARI and 1.14 

### "Dry-coil test" means a test held constant and the unit is innon-changing titled "StandardforAir-Source Unitary Heat conducted at a wet-bulb tempera'l're and a operating mode. Pump Equipment". dry-bulb temperature such that moisture will 1.24 

### "Temperature bin" means a 5' 

### F

1.5 

### "ARI Standard 320-76" 

### means the test not condense on the evaporatorcoil ofthe increment over a dry-bulb temperature range standardpublishedin 1976

### by the ARI and unit. of65° F through 104' 

### Ffor the cooling cycle titled "StandardforWater-Source Heat 1.15 "Heating seasonal perfonnance and -25' 

### Fthrough 

### 64° Ffor the heating Pumps". factor (HSPF)" means the total heating output cycle.

1.6 

### "ASHRAE" means the American ofa heatpump during its nonnal annual 1.25 

### '"Time-temperature defrost control Society ofHeating, Refrigeration and Air- usage periodfor heating divided by the total system" means a system which automatically Conditioning Engineers. Inc. electric power input during the same period. provides the defrost function at a

1.7 

### "ASHRAE Standard 37-78" 

### means the 1.16 

### "Heating load factor (HLF)" 

### means predeterminedtime interval wheneverthe test standardpublishedby ASHRAE in 1978 

### the ratio ofthe total heating done in a outdoortemperature drops below a level and titled "Methods ofTesting for Rating complete cycle ofa specified time period. where frosting will occur. Unitary Air-Conditioning and Heat Pump consisting ofan "on" time "off' time. to the 1.26 "Testcondition tolerance" means the Equipment." steady state heating done overthe same maximum permissible variation ofthe

1.8 

### "Continuouslyrecorded" means a period at constant ambient conditions. average ofthe test observations from the method ofrecording measurements in 1.17 

### "Latent cooling" means the amount standard ordesired test condition as intervals no greaterthan 5 

### seconds. ofcooling in Btu's necessary to remove water provided in 6.1.1, 6.2.1, 6.2.2, 

### and 6.2.3 

### ofthis

1.9 

### "Cooling load factor (CLF)" means the vaporfrom the airpassing overthe indoor Appendix. ratio ofthe total cooling done in 

### a complete coil by condensation during a period oftime. 1.27 '"Test operating tolerance" means the cycle ofa specified time period, consisting of 1.18 

### "Part-load factor (PLF)" 

### means the maximumpennissible difference between the an "on" time and "off' time, to the steady- ratio ofthe cyclic energy efficiency ratio to maximum and the minimum instrument state cooling done over the same period at the steady-state energy efficiency ratio at observation during a test as provided in 6.1.1, constant ambient conditions. identical ambient conditions, 6.2.1, 6.2.2, 

### and 6.2.3 

### ofthis Appendix.

'Copiedfrom Appendix M, pages 76707 thru 76723, Federal Register, Vol. 44, No. 249, Thursday, December27,1979. This Appendix Mis subject to change by the U. S. Government. Only those portions ofAppendix M pertaining to air-source heat pumps are to be used.



### 8

### -----------------------

__ AR I STAN DA R D 240-81

1.28 "Wet-coil test" means a test conducted at a wet-bulb temperature and a dry-bulb temperature such that moisture will condense on the test unit evaporator coil.


### 2. TestingRequired

2.1 

### Testing required forairsource cooling only units with single speedcompressors. two-speedcompressors. two compressors. or cylinderunloading. Two steady state wet coil tests required to be performed, test A and test B. Test A is to be conducted as an outdoor dry bulb temperature of95° F and test B at 82" F. Test C and D are optional tests to be conducted when cyclic performance parameters are to be measured in order to determine the degradation coefficient, CD Test C is a steady state dry coUtest conducted at an outdoor dry bulb temperature of82° F. Test D is a cyclic test also conducted at an outdoor dry bulb temperature of82° F. In lieu ofconducting tests C and D, an assigned value of0.25 may be used for the degradation coefficient, CD.

2.1.1 

### Testing required for units with single speedcompressors andsingle speed condenser fans. Test A and testB shall be performed according to the test procedures outlined in 4.1 ofthis Appendix. In addition. the cyclicperformance shall be evaluated by conducting test C and 

### D according to the requirements outlined in4.1 ofthis Appendix.

2.1.2 

### Testing required for units with single speedcompressors andmultiple-speed condenserfans. The test requirements for multiple-speed condenserfan units shall be the same as described in section 2.1.1 for single speed condensor fan units.

2.1.3 

### Testing required for units with twospeedcompressors. two compressors. or cylinderunloading. The test requirements for two-speed compressorunits, two compressor units. orunits with cylinderunloading are the same as described in 2.1.1 ofthis Appendix except that test A and test B shall be performed at each compressor speed or at each compressor capacity.

2.1.4 

### Testing required for units with twospeedcompressors, two compressors, or cylinderunloading capable ofvarying the sensible to total(SIT) capacityratio. When a unit employing a two-speed compressor, two compressors. or cylinderunloading provides a method ofvarying the ratio ofthe sensible cooling capacity to the total cooling capacity. (S/T), the test requirements are the same as for two-speed compressorunits as described in 2.1.3 ofthis Appendix.

2.2 

### Testing required forairsource heating onlyunits with single speedcompressors, two-speedcompressors. two compressors, or cylinderunloading. Fourtypes oftests are required to be performed: HighTemperature, Cyclic. FrostAccumulation. and Low Temperature. In lieu ofconducting the Cyclic Test an assigned value of0.25 may be used for the degradation coefficient, CD.

2.2.1 

### Testing required for units with single speedcompressors. Units with single speed compressors shall be subjected respectively to the High TemperatureTest at 

## 4rF described in section 3.2.1.1, the Cyclic Test as described in section 3.2.1,2, the Frost AccumulationTest as described in section 3.2.1.3, and the Low Temperature Test as described in section 3.2.1.4.

2.2.2 

### Testing required for units with twospeedcompressors. two compressors, or cylinderunloading. With the unit operating: at high compressors speed (two-speed compressor), with both compressors in operation (two-compressors), or at the maximum capacity (cylinder unloading); the following tests are required to be performed on all units; the High Temperature Test at 47° F, the Frost Accumulation Test, and the Low Temperature Test. An additional test (cyclic at 47" F) is required, with the unit operating at the high compressor speed (twospeed compressor), with both compressors in operation (two compressors), or at the maximum capacity (cylinder unloading); if the normal mode ofoperation requires cycling "on" and "off' ofthe compressor(s) at high speed or maximum capacity.

With the unit operating: at the low compressor speed (two-speed compressor). with the single compressor which normally operates at low loads (two compressors). or at the low compressor capacity (cylinder unloading); the following tests are required to be performed on all units: the High Temperature Test at 47° F. the High Temperature Test at 62° F, and the Cyclil; Test. Additional tests. (Frost Accurr.ulation Test and Low Temperature Test) are required. with the unit operating: on low compressor speed (two-speed compressor), with the single compressor which normally operates at low loads (two compressors) or at the low compressor capacity (cylinder unloading). if the unit's low speed, one compressor or low capacity performance at and below 40° F is needed to calculate its seasonal performance.

2.3 

### Testing required for airsource units whichprovide both heating andcooling. The requirements for units which provide both heating and cooling shall be the same as the requirements in Section 2.1. and 2.2 ofthis Appendix.

2.4 

### Testing required for watersource units whichprovide both heating andcooling. (Reserved) 

### 3. Testing conditions

3.1 

### Testing conditionsforairsource cooling only units with single speed compressors, two-speedcompressors, twa compressors orcylinderunloading_ The test room requirement and equipment installation procedures are the same as those specified in sections 11.1 and 11.2 ofASHRAE Standard 37-78. Units designed for both horizontal and vertical installation shall be tested in the orientation in which they are most frequently installed. All tests shall be performed at the normal residential voltage and frequency for which the equipment is designed (either 115 or 230 volts and 60 hertz), the test installation shall be designed such that there will be no air flow through the cooling coil due to natural orforced convection while the indoor fan is "off'. This shall be accomplished by installing dampers upstream and downstream ofthe test unit to block the offperiod air flow. Values ofcapacity for rating purposes are to be rounded offto the nearest 100Btu/ hour for capacities less than 20,000 Btu/hour; to the nearest 200Btu/hourfor capacities between 20,000 and 37,999 Btu/hour; and to the nellrest 500Btu/hourfor capacities between 38,000 and 64,999 Btu/hour.

The following conditions listed inARI Standard 210.79 shall apply to all tests performed in Section 3.1 ofthis Appendix: 5.1.3.4 Cooling Coil Air Quantity. 5.1.3.6 Requirements for Separated Assemblies. 3.1.1 

### Testing conditionsfor units with single speedcompressors andsingle speed condenser fans. 3.1.1.1 

### Steadystate wet-coilperformance tests (TestA andTestB). TestA and testB shall be performed with the air entering the indoor side ofthe unit having a dry-bulb temperature of

## soo F and a wet-bulb temperature of

# 8rF. The dry-bulb temperature ofthe airentering the outdoor side ofthe unit shall be 95° F in test A and 82' Fin test B. The temperature ofthe air surrounding the outdoor side ofthe unit in each test shall be the same as the outdoor entering air temperature exceptfor units or sections thereofintended to be installed only indoors, in which case the dry-bulb temperature surrounding that indoor side of t.1e unit shall be 80° F. Forthose units which reject condensate to the condenser, located in the outdoor side ofthe unit. the outdoor wetbulb temperature surrounding the outdoor side ofthe unit shall be 75° F in test A and 65° Fin test B.

3.1.1.2 

### Steadystate dry coilperformance test(TestC) andcyclicdry coilperformance test(TestD). Test C and test D shall be performed with the air entering the indoor side ofthe unit having a dry-bulb temperature of

## soo F and a wet-bulb temperature which does not result in formation ofcondensate on the indoor coil. (It is recommended that an indoorwet-bulb temperature of57° F or less be used.) The dry-bulb temperature ofthe air entering the outdoorportion ofthe unit shall be 82° F. The outdoorportion ofthe unit shall be subject to the same conditions as the requirements for conducting test B as stated previously in section 3.1.1.1. Test C shall be conducted with the unit operating steadily. Test

### Dshall be conducted by cycling the unit "on" and "ofr' by manual or automatic operation ofthe normal control circuit ofthe unit. The unit shall cycle with the compressor "on" for 8 minutes and "off' for 24 minutes. The indoor fan shall also cycle "on" and "ofr', the duration ofthe indoorfan "on" and "off' periods being governed by the automatic controls which the manufacturernormally supplies with the unit. The results oftests C and D shall be used to calculate a degradation coefficient, CDby the procedures outlined in 5.1 ofthis Appendix.



### 9

### ARI STANDARD 240-81

3.1.2 Testing conditionsfor units with single speedcompressors andmultiple-speed condenserfans. The condenserfan speed to be used in test A shall be that speed which normally occurs at an outdoor dry-bulb temperature of95" F, and for test B, the fan speed shall be that which normally occurs at an outdoor dry-bulb temperature of82" 

### F. If 

### elected to be performed, tests C andD shall be conducted at the same condenserfan speed as in test B.



### 3.1.3 Testing conditionsfor units with two-speedcompressors, two compressors. or cylinderunloading. The condenserfan speed used in conducting testA at each compressor speed shall be that which normally occurs at an outdoor dry-bulb temperature of95" F. For testB, the condenserfan speed at each compressor speed shall be thatwhich normally occurs at an outdoordry-bulb temperature of82" 

### F. If

### elected to be performed, tests C andD shall be conducted at the low compressor speed with the same condenserfan speed as used in test B. For those two-speed units in which the normal mode ofoperation involves cycling the compressor "on" and "off' at high speed, tests C and D shall also be performed with the compressor operating athigh speed and at a condenserfan speed that normally occurs at test A ambient conditions. Units consisting oftwo compressors are subject to the same requirements as those units containing two-speed compressors, except that when operated at high speed, both compressors shall be operating and when operating at low speed, only the compressor which normally operates at an outdoor drybulb temperature of82" 

### F shall be operating.

In 

### lieu ofconducting tests C andD, an assigned value of0.25 

### maybe usedfor the degradation coefficient, 

### 4>, at each compressor speed. If

### the assigned degradation coefficient is used for one compressor speed itmust also be used for thp othercompressor speed.

In 

### the case ofunits with cylinder unloading, the loaded and the unloaded conditions correspond to high 

### and low compressor speed on two-speed units respectively.



### 3.1.4 Testing conditionsfor units with two-speedcompressors, two compressors, or cylinderunloading capable ofvarying the sensible to total(SIT) capacityratio. The mode ofoperation selectedfor controlling the SIT ratio in the performance oftest A and test Bat each compressor speed shall be such that it does notresult in an operating configuration which is not typical ofa normal residential installation. If

### elected to be performed, tests C and D shall be conducted at low compressor speed (single compressor operating) with the same SIT controlmode as used in testB when performed at the low compressor speed. Likewise, tests C and D shall also be conducted at high compressorspeed (two compressors operating) and with the same S/ T control mode as in test A whenperformed at the high compressor speed.



### 10 In the case ofunits with cylinder unloading. the loaded and unloaded conditions correspond to high and low compressor speed on two-speed units respectively.



### 3.2 Testing conditionsforairsource heatingonly units with single speed compressors, two-speedcompressors, two compressors, orcylinderunloading. The equipment under test shall be installed according to the requirements ofSection 11.2 

### ofASHRAE Standard 37-78 

### and Section 5.1.4.5 ofARI 

### Standard 240-77. 

### Test chamber requirements are the same as given in Section 11.1 

### ofASHRAE Standard 37-78. 

### Units designed for both horizontal and vertical installation shall 

### be tested in the orientation in which they are most often installed. 

### AIl tests shall be performed at the normal residential voltage and frequency for which the equipmentis designed (either 115 

### or 230 

### volts and 60 

### hertz). Values ofcapacity for rating purposes 

### are to be rounded offto the nearest 100

### Btu/hourfor capacities less than 20,000 

### Btu/hour; to the nearest 200

### Btu/hour for capacities between 20,000 

### and 37,999

### Btu/ hour; and to the nearest 500

### Btu/hourfor capacities between 38,000 

### and 64,999 

### Btu/ hour.



### 3.2.1 Testing conditionsfor units with single speedcompressors.

3.2.1.1 High temperature testconditions. The High Temperature Test at 47" 

### F shall be conducted at an outdoor dry-bulb temperature of47" 

### F and an outdoorwet-bulb temperature at 43" 

### F. The High Temperature Test at 62" 

### F shall be conducted at an outdoor dry-bulb temperature of62° 

### F and an outdoor wet-bulb temperature of56.5° 

### F. Forboth tests, the dry-bulb airtemperature entering and surrounding the indoorportion ofthe unit shall be 70° 

### F and a maximum wet-bulb temperature of60° 

### F. The duration ofthe tests shall be for a minimum of If1! 

### hour.



### 3.2.1.2 Cycling testconditions. The Cycling Test at 47° 

### F shall be conducted at the same dry-bulb and wet-bulb temperature as the High Temperature Test at 47° 

### F as described in 3.2.1.1. 

### During the Cycling Test, the indoorfan shall cycle "on" and "off', as the compressorcycles "on" and "off', except that the indoorfan cycling times may be delayed due to controls that 

### are normally installed with the unit The compressor cycling times shall be 6 

### minutes "On" and 24 

### minutes "off:' The test installation shall be designed such that there 

### will be no airflow through the indoorunit due to natural or forced convection while the indoorfan is "off:' This shall be accomplished by installing dampers upstream and downstream ofthe test unit to block the offperiod airflow.



### 3.2.1.3 Frastaccumulation testconditions. The dry-bulb temperature and the resultant dew-point temperature ofthe airentering the outdoorportion ofthe unit shall be 35° F and 30° Frespectively. The indoor dry-bulb temperature shall 

### be 70° F and the maximum indoor wet-bulb temperature shall 

### be 60° 

### F. The FrostAccumulationTestrequires that the unit undergo a defrostpriorto the actual test. The test then begins at defrost termination and ends at the next defrost termination. Defrost termination occurs when the controls normally installedwithin the unit are actuated to cause it to change defrost operation to normal heating operation. During the test, auxiliary resistance heaters shall not be employed during eitherthe heating or defrost portion ofthe test



### 3.2.1.4 Lowtemperature testconditions. The LowTemperature Test shall be conducted at a dry-bulb temperature entering the outdoorportion ofthe unit of17" 

### F and a wet-bulb temperature of15° F. The air entering the indoorportion ofthe unit shall have a dry-bulb temperature of70° 

### F and a maximum wet-bulb temperature of60° 

### F.



### 3.2.1.5 Additionaltesting conditions. All tests shall be conducted at the indoor-side air quantities specifiedin Sections 4.1.4.3 

### and 5.1.4.6 

### and Table 2 

### ofARI 

### Standard 240-77. 

### The following conditions listed in ARI 

### Standard 240-77 

### shall apply to all tests performedin Section 3.2 

### ofthis Appendix. 

### 5.1.4.4 Outdoor-SideAirQuantity: and 5.1.4.5 RequirementsforSeparated Assemblies. In 

### all tests, the specified dry-bulb temperature entering the outdoorportion of the unit also applies to the air temperature surrounding the outdoorportion ofthe unit. Similarly, models where portions are intended to

### be installedindoors shall have the air temperature surrounding thatportion ofthe unit the same as the indoor air 

### temperature.



### 3.2.2 Testing conditionsfor units with two-speedcompressors, two compressors or cylinderunloading. The testing conditions for two-speed compressors, two compressors, or cylinderunloading shall be the same as those for single speed units as described in 3.2.1.



### 3.3 Testing conditionsforairsource units whichprovide both heating andcooling. The testing conditions for units which provide both heating and cooling shall be the same as the requirements in Sections 3.1 

### and 3.2 

### of this Appendix.

3.4 

### Testing conditionsfor watersource units whichprovide bothheatiIlg andcooling. {Reserved)

4.0 

### Testingprocedures. Measure all electrical inputs as described in the procedures below. All electrical measurements during all "on" and "off' periods shall include auxiliary power or energy (controls, transformers, crankcase heaters, etc.) delivered to the unit.



### 4.1 Testingproceduresforairsource cooling only units with single speed compressors, two-speedcompressors, two compressors, orcylinderunloading. All steady-state wet- and dry-coil performance tests on single package units shall simultaneously employ the Air-Enthalpy Method (Section 3 ofASHRAE Standard 37- 78) 

### on the indoor side and one othermethod consisting ofeither the Air-Enthalpy Method or the CompressorCalibration Method (Section 4ofASHRAE Standard 37-78 

### on the outdoor side. 

### AIl steady-state wet- and drycoil performance tests on split systems shall simultaneously employ the Air-Enthalpy Method or the CompressorCalibration Method on the indoor side and the AirEnthalpy Method, the Compressor Calibration Method or the Volatile Refrigerant Flow Method (Section 5 of ASHRAE Standard 37-78) on the outside. All cyclic dry-coil performance tests shall employ the Air-Enthalpy Method. indoor side only. The values calculated from the two test methods must agree within 6percent in order to constitute a valid test. Only the results from the Air-Enthalpy Method on the indoor side shall be used in the calculations in Section 5.1. Units shall be installed and tested in such a manner that when operated under steady-state conditions, the cooling coil and condenser coil airflows meet the requirements ofSections 5.1.3.4, 5.1.3.5, and 5.1.3.7 ofARI Standard 210.79.



### 4.1.1 Test operatingprocedures. 4.1.1.1 Steady-state wet-coilperformance tests (TestA and TestB). Steady-state wetcoil performance tests (A and B) shall be conducted in accordance with the conditions described in sections 3.1.1.1, 3.1.2, 3.1.3, 3.1.4, and 3.1.5 ofthis Appendix and the procedures described for cooling tests in Section 11.3 of ASHRAE standard 37-78 and evaluated in accordance with the cooling-related requirements ofSection 12 ofthe ASHRAE Standard 37-78. The testroom reconditioning apparatus and the equipment under test shall be operated until equilibrium conditions are attained.



### 4.1.1.2 Steady-state andcyclic dry-coil performance tests (Test Cand Test D). The steady-state and cyclic dry-coil tests (C and D) shall be conducted as described below in accordance with the conditions described in sections 3.1.1.2, 3.1.2, 3.1.3, 3.1.4, and 3.1.5 of this Appendix. The results shall be evaluated in accordance with the cooling related requirements ofSections 12.1.5, 12.1.6, 12.1.7, ofASHRAE Standard 37.78. The test room reconditioning apparatus and the equipment under test shall be operated until equilibrium conditions are attained, but not for less than one hourbefore data for test C are recorded. For all equipment test methods including the Compressor Calibration Method. test C shall be performed with data recorded at 10- minute intervals until four consecutive sets of readings are attained with the tolerance prescribed in Section 11.6 ofASHRAE Standard 37-78. When the Air-Enthalpy Method is used on the outdoor side for test C, the requirements ofthis section shall apply to both the preliminary test and the regular equipment test; the requirements ofSection 3.6 ofASHRAE Standard 37-78 shall also apply. Immediately after test C is completed the test unit shall be manually cycled "off' and "on" using the time periods from 3.1.1 of this Appendix until steadily repeating ambient conditions are again achieved in both the indoor and outdoor test chambers, but for not less than 2complete "off'/"on" cycles. Without a break in the cycling pattern, the unit shall be run through an additional "off'/"on" cycle during which the test data required in 5.1 shall be recorded. During this last cycle, which is referred to as the test cycle, the indoor and outdoor test room ambient conditions shall remain within the tolerances specified in4.1.3 ofthis Appendix during the cyclic dry-coil tests, all air moving equipment on the condenser side shall cycle "on" and "off' when the compressor cycles "on" and "off'. The indoor air moving equipment shall also cycle "off'
as governed by any automatic controls normally installed with the unit. This last requirement applies to units having an indoor fan time delay. Units not supplied with an indoor fan time delay shall have the indoor air moving equipment cycle "on" and "off' as the compressor cycles "on" and "off,"



### 4.1.2 Test instromentation. The steadystate and cyclic performance tests shall have the same requirements pertaining to instrumentation and data as those specified in Section 10 and Table II ofASHRAE Standard 37.78. For the cyclic dry-coil performance tests, the dry-bulb temperature ofthe airentering and leaving the cooling coil, or the difference between these two drybulb temperatures, shall be continuously recorded with instrumentation accurate to within ±0.3" F ofindicated value and have a response time of2.5 seconds or less. Response time in the time required for the instrumentation to obtain 63 percent ofthe final steady-state temperature difference when subjected to a step change in temperature difference of15" F or more. Electrical measurement devices [watt-hour meters) used during all tests shall be accurate to within ±0.5 percent ofindicated value.



### 4.1.3 Test tolerances. All steady-state wet-and dry-coil performance tests shall be performed within the applicable operating and test condition tolerances specified in Section 11.6 and Table ill ofASHRAE Standard 37-78.

4.1.3.1 The indoor and outdoor average dry-bulb temperature for the cyclic dry coil test D shall both be within 1.0" Fofthe indoor and outdoor average dry bulb temperature for the steady-state dry coil test C, respectively.

4.1.3.2 The test condition and test operating tolerances for conducting test Dare stated in 6.1.1 ofthis Appendix. Variation in the test conditions greater than the tolerances prescribed in 8.1.1 ofthis Appendix shall invalidate the lest. It is suggested that an electric resistance heater having a heating capacity approximately equal to the sum of the cooling capacity and compressor and condenser fan power should be installed in the outdoor test room and cycled "off' and "on" as the unit cycles "on" and "off' respectively to improve control in the outdoor test room. Similarly, an electric resistance heater having a heating capacity approximately equal to the cooling capacity ofthe unit could be installed in the indoor test room, and cycled "on" and "off' as the test unit cycles "on" and "off' to improve indoor room control.



### 4.2 Testingproceduresforairsource heating only units with single speed 

### ARI STANDARD 240-81

compressors. two-speedcompressors. two compressors. orcylinderunloading.

4.2.1 Test operatingprocedures. All High Temperature Tests, the Cyclic Test, the Frost Accumulation Test, and the low Temperature test shall have the performance evaluated by the Air-Enthalpy Method on the indoor side. In addition, the High Temperature Test and the Low Temperature Test shall have a simultaneous test method (as described in 4.1) used as a check. The values calculated from the two methods must agree within 6 percent in order to constitute a valid test. Only the results from the Air-Enthalpy Method on the indoor side shall be used in the calulations in section 5.2.



### 4.2.1.1 Testprocedureforhigh temperature test. When the outdoorAirEnthalpy Method is used. the outdoor chamber must not interfere with the normal air circulating pattern during the preliminary test. It is necessary to determine and adjust for system resistance when the outdoor air measuring apparatus is attached to the outdoorportion ofthe unit. The test roam apparatus and test units must be operated for at least one hourwith at least Ih hour at equilibrium and at the specified test conditions prior to starting the test. The High Temperature Test shall then 

### be conducted for
a minimum of Ih hour with intermittent data being recorded at lo-minute intervals. For all units, especially those having controls which periodically cause the unit to operate in defrost mode, attention should be given to prevent defrost during the High Temperature Test. Units which have undergone a defrost should operate in the heating mode for at least 10-minutes after defrost termination prior to the start ofthe test. When the outdoor Air-Enthalpy Method is used as a second test then a preliminary test must be conducted for a minimum of30 minutes with 4 ormore sets ofdata recorded at 10 minute intervals. all remaining requirements of Section 3.6.1 in the ASHRAE Standard 37-78 shall then apply in conducting the preliminary test for the outdoor air enthalpy method. For some units, at the ambient condition ofthe test. frost may accumulate on the outdoorcoil. Ifthe supply air temperature or the difference between the supply air temperature and the indoor air entering temperature has decreased by more than 1.5· F at the end ofthe test. the unit shall be defrosted and the test restarted. Only the results ofthis second High Temperature Test shall be used in the heating seasonal performance calculation in section 5.2. Prior to beginning the High Temperature Test. a unit shall operate in the heating mode for at least 10 minutes after defrost termination to establish equilibrium conditions for the unit and the room reconditioning apparatus. The High Temperature Test may only begin when the test unit and room conditions are within the test condition tolerances specified in Section 6.2.1 ofthis Appendix.



### 4.2.1.2 Testproceduresforthe cyclictest. The cyclic test shall follow the High TemperatureTest and by cycled "on" and "off" as specified in 3.2.1.2 until steadily



### 11

### ARI STAN DAR 0 240-81

_
repeating ambient conditions are achieved for boththe indoor and outdoortest chambers, butfor not less than 2complete "ofr'/"on" cycles. Without a breakin the cycling pattern. the unit shall be operated through an additional "off'/"on" cycle. during which the required test data shall be recorded. During the last cycle, which is referred to as the test cycle. the indoor and outdoortest room ambient conditions shall remain within the tolerance specified in section 6.2.2. ofthis Appendix. 

### If. prior to the High Temperature Test. the unit underwent a defrostt:ycle to rid the outdoor coil ofany accumulated frost, then prior to cycling the unit "off' and "on" it should be made to undergo a defrost. After defrost is completed and before starting the cycling process. the unit shall be operated continuously in the heating mode for a least 10 minutes to assure that equilibrium conditions have again been established for the unit and the room conditioning apparatus. Cycling the unit may begin when the test unit and roomt:onditions are within the High Temperature Test condition tolerances specified in section 6.2.1 ofthis Appendix. Attention should be given to prevent defrost after the cycling process has begun.



### 4.2.1.3 Testproceduresfor thefrost accumulation test. The defrost controls shall be set at the normal settings which most typify those encountered in Region IV as described in section 6.2.4 and 6.2.5 ofthis Appendix. The test room reconditioning equipment and the unit under test shall be operated for at least '/2 hour prior to the start ofa "preliminary" tesl period. The preliminary test period and the test period itselfare to be conducted within the test tolerances given in section 4.2.3.3 ofthis Appendix. In some cases. the preliminary defrost cycle may be manually induced, however. it is important that the normally operating controls govern the defrost termination in all cases. Forunits containing dafrost controls which are likely to cause defrost at intervals less than one hour when the unit is operating at the requited test cond:tiC'ns, the preliminary tesl period shall slart at the termination ofa defrost cycle which automatically occurs and shaH end at the termination ofthe next automaticolly occurring defrost cycle. Forunits containing defrost controls which are iikcly to cause defrost at intervals exceeding one hour when operating at the required test condition. the preliminary test period consists of"healingonly" preliminary operation for at least one hour. after which a defrost may be manually
or automatically induced. The test period then begins at the termination ofthis defroat cycle and ends at the termination ofthe next automatically occurring defroat cycle. 

### Ifthe unit bas not unde1'8one a defrost after 12 hours. then the teata ahall be concluded and the results calculated for thia 12-hourperiod. Forunits which turn the Indoorfan offduring defrost the indoor supply duct shall 

### be blocked during all defrost cycles to prevent natural orforced convection through the indoorunit. During defrost, resistance heaters



### 12 normally installed with the unit shall 

### be prevented from operating.



### 4.2.1.4 Testproceduresfor the low temperature test. Where applicable. the High Temperature Testpreparation and performance requirements shall also be used in the Low Temperature Test. The testroom reconditioning equipment shall first

### be operated in a steady-state manner for at least one-halfhour at equilibrium and at the specified test conditions. The unit shall then undergo a defrost. either automatic or manually induced. It

### IS important that the unit terminate the defrost sequence by the action ofits own defrost controls. The defrost controls are to remain at the same setting as specified in 4.2.1.3. At a time no earlierthan 10 minutes after defrost termination, the test shall start. Test duration is one-halfhour. For all units, defrost should be prevented during the one-halfhour testperiod.



### 4.2.2 Test instrumentation, 4.2.2.1 Test instrumentationfor the high temperature test. The indoor air flow rate shall be determined as described in Section 7.1 through 7.4 ofASHRAE Standard 37-78. This requires the construction ofan air receiving chamber and discharge chamber separated by partition in which one ormore no;!:;!:les are located. The receiving chamberis connected to the indoor air discharge side of the test specimen through a short plenum. The exhaust side ofthe airflow rate measuring device contains an exhaustfan with some means to vary its capacity to obtain the desired external resistance to air flow rate. The exhaust side is then left open to the test room or is ducted through a conditioning apparatus and then back to the test specimen inlet. The static pressure across the nozzles, the velocity pressure. and the static pressure measurements at the nozzle throat shall be measured with manometers which will result in errors which are no greater than ±1.0 percent ofindicated value and having minimum scale divisions not**exceedin~~** :.0 percent ofthe reading. Static pressu;,e and temperature measurements must be taken at the nozzle throat in order to obtain density ofthe air. The areas ofthe nozzles shall be determined by measuring their diameter with an error no grealer than ±O.2 percent in four places approximately 45 degrees apart around the nozzle in each oftwo places through the nozzle throat. one at the outlets and the others in the straight section near the ra·dius. Th!! energy usage ofthe compressor. indoor and outdoor fan. and all other equipment components shall be measured with a watthour meter Which is accurate to within ±0.5 percent ofthe quantity measured. Measurements ofthe air temperature entering and leaving the indoor coil or the difference between these two shall be made In accordance with the requirements of ASHRAE Standard 41 part 1. These temperatures shall be continuouslyrecorded with instrumentation having a total system accuracy within ±O.3" F ofindicated value and a response time of2.5 seconds orless. Temperature measurements are to be made upstream ofthe staticpressure tap on the inlet and downstream ofthe static pressure taps on the outlet. The indoor and outdoor dry-bulb temperatures shall be continuously recorded with instrumentation which will result in an errorno greaterthan ±0.3° F of indicated value. The outdoorwet-bulb temperature shall 

### be continuously recorded. Static pressure measurements in the ducts and across the unit shall be made in accordance with Section 8 ofASHRAE Standard 37-78 using equipment which will resultin an errorno greaterthan ±0.01 inch ofwater. Static pressure measurements shall be made and recorded at 5 minute intervals. All other data not continuously recorded shall be recorded at 10minute intervals.



### 4.2.2.2 Test instrumentationforthe cycling test. The air flow rate during the onperiod ofthe CyclicTest shall be the same agreed within ±1. percent as the air flow rate measured during the previously conducted High Temperature Test. AlI other instrumentation requirements are identical to 4.2.2.1 ofthis Appendix.



### 4.2.2.3 Test instrumentationfor thefrost accumulation test. The airflow rate for the FrostAccumulation Test shall be the same as described in 4.2.2.1. The indoor-side dry-bulb temperature and outdoor-side dry-bulb temperature shall be continuously recorded with instrumentation having a total system accuracy within ±0.3° F ofindicated value. The outdoor dew point temperature shall be determined with an errorno greaterthan ±O.5° F ofindicated value using continuously recording instrumentation. All other data shall be recorded at 10 minute intervals during the heating cycle. Defrost initiation, termination and complete test cycle time (from defrost termination to defrost termination) shall be racorded. Defrost initiation is defined liS the actuation [either automatically or manually) ofthe controls normally installed with the unit which cause it to alter its normal heating operation in order to eliminate possible accumulations of frost on the outdoor coil. Defrost termination occurs when the controls normally within the unit are actuated to change from defrost operation to normal heating operation. Provisions should be made 50 that instrumentation in capable ofrecording the cooling done during defrost as well as the total electrical energy usage during defrost. These data and the .continuously recorded data need be the only data obtained during defrost.



### 4.2.2.4 Test instrumentatioT!far the low temperature test. Instrumentation for the Lew Temperature Test is identical to that ofthe High Temperature Test described in section 4.2.2.1 ofthis Appendix.



### 4.2.3 Test tolerances. 4.2.3.1 Test toleranceslorthe high temDerature test. All tests shall be conducted within the tolerances specified in Section 6.2.1. Variation greaterthan those given shaH invalidate the test. The heating capacity results by the indoorAirEnthalpy Method shall agree within 6percent ofthe value determined by any other simultaneously

### _________________________ A RI STAN DAR D 240-81

conducted capacity test in orderfor the test to be valid.



### 4.2.3.2 Test tolerancesfor the cyclic test. The test condition tolerances and test operating tolerances for the on-period portion ofthe test cycle are specifiedin SectioI1 6.2.2. Variation exceeding any specified test tolerance shall invalidate the testresults.



### 4.2.3.3 Test tolerancesfor thefrost accumulation test. Test condition and test operating tolerances for FrostAccumulation Tests are specified in Section 6.2.3. Test operating tolerances during heating applies when the unit is in the heating mode. except for the first 5 minutes after the termination of a defrost cycle. Test operating tolerance during defrost applies during a defrost cycle and during the first 5 minutes after defrost termination when the unitis operating in the heating mode. In determining whether the test condition tolerances are met. only the heating portion ofthe testperiod shall be used in calculating the average values. Variations exceeding the tolerances presentedinSection 6.2.3 shall invalidate the test.



### 4.2.3.4 Test tolerancesforthe low temperature test. During the testperiod for the LowTemperature Test. the operating conditions shall be within the tolerances specified in Section 6.2.1 ofthis Appendix.



### 4.3 Testingproceduresforairsource units whichprovide bothheating andcooling. The testing procedures for units which provide both heating and cooling shall be the same as those specifiedin Sections 4.1 and 4.2 ofthis Appendix. Also during the offperiod ofthe dry-coil cooling test (testD). the switch-overvalve shall remain in the cooling mode. unless the controls normally supplied with the unit are designed to reverse it. in which case the controls shall operate the valve. During the off·period ofthe cyclic heating test at 47° 

### F. the switch-overvalve shall remain in the heating mode. unless the controls normally supplied with the unit are designed to reverse it. in whichcase the controls shall operate the valve.



### 4.4 Testingproceduresfor watersource units whichprovide bothheatingandcooling. (Reserved)



### 5.0 Calculationsforperformancefactors. 5.1 Calculations of seasonalenergy efficiencyratios (SEER) in air-source units.

The testing data and results required to calculate the seasonal energy efficiency ratio (SEER) in Btu's per walt-hour shall include the following:

(i) Cooling capacities (Btu/hr) from tests A and Band. ifapplicable. the cooling capacity (Btu/hr) from test C and the total cooling done from test D (Btu·s). 

## Q

..k 

### (95F) Qllk

### (82F) QII'dry 

### Q.,.•• dry

(il) 

### Electrical powerinput to all components and controls (walts) from tests A. B. and ifapplicable the electrical power input to all components and controls (watts) from test C and the electrical usage (watthour) from testD. 

### E.,k (95F) 

### E.,k (82F) 

### E.,k. dry 

### E.,.•• dry

(iii) 

### Indoor air flow rate (SCFM) and external resistance to indoor air flow (inches ofwater).

(iv) Air temperature (0 

### F) Outdoor dry

### bulb Outdoorwetbulb Indoor dry

### bulb Indoorwetbulb

Where the .cooling capacities 

## Q

..k**(9~F).** 

### from test A. 

### Q..k (82). from test B. and 

### Q

... dry. from test C. are calculated using Ihe equations specified in section 3.7 

### ofASHRAE Standard 37-78. 

### The total cooling done, Q.,.., dry 

### from test D. is calculatedusing equation (1) below.

Units whichdo not have indoor air circulating fans furnished as part ofthe model shall have theirmeasured total cooling capacities adjusted by subtracting 1250Btu/ hrper 1.000 CFM ofmeasured indoor air flow and adding to the total steady-state electrical powerinput 365 walts per 1.000 CFM of measured indoor air flow.

Energy efficiency ratios from tests A, B. and C, EERA•

### EERa. EER

... dry respectively. are each calculated as the ratio ofthe total cooling capacity in Btu/hr to the total electrical powerinput in watts.

Units which do not have indoor air circulating fans furnished as part ofthe model shall adjust their totalcooling done and ener8l' used in one complete cycle for the effect ofcirculating indoor air equipment power. The value to be used for the circulating indoor air equipment power shall be 1250Btu/hrper 1.000 CFM ofcirculating indoor air. The energy usage required in one complete cycle required for indoor air circulation is theproduct ofthe circulating indoorair equipmentpower and the duration oftime in one cycle that the circulating indoor air equipmentis on. The total cooling done shall then be the measured cooling in one complete cycle minus the energy usage required for indoor air circulation in one complete cycle. The total electrical energy usage shall be the sum ofthe energy usage required for indoor air circulation in one complete cycle and the energy used by the re.maining equipment components (compressor(s). outdoor fan, crankcase heater. transformer(s). etc.) in one complete test cycle.

Energy efficiency ratio from tesfs D. 

### EER.". dry is calculated as the ratio cf the 

### total cooling done in Btu's to the tolal dectrical energy usage in walt-hours.



### 13

### A RI STANOAR 0 240-81

_

where

CD=Is the degradation coefficient described in 2.1.1 or as calculated in equation (4) above. (2) 

### .r 

## = f(tlme Indoorfan oft) [Tal (t)

- T a2 (t»)dt 

## J(time Indoor fan on)

The pr.eceding equations are then used in the following equation to calculate a degradation coefficient CD rounded to the nearest .01.

5.1.2 Method for calculating a SEER for units with single-speed compressors and multi-speed condenser fans. The seasonal 

### 14 BL(T/) Q:..'( T/)

X·-IXE:'-'(T;) n; PLFk-1 XN



### C1..-2 ( T;)

- BL(T;) Q:..2( T;)

### -C1.;I( T;)

Q(T/)_N·'(T)X!!:i

N -"".. { N E(T/)_E··'(T.)X!!:i

N

- .. I N E(T;)

N (3) (1) where

(1) PLF·-I= 1-ct-'(I-X.-I). Where CD the degradation coefficient as described in section 2.1.3 or as calculated above in equation (1). 5.1.3.2 When a unit must alternate bctween high (1:=2) and low (1:= 1) compres- sor speeds to satisfy the building cooling load at a temperature 

### T;, evaluate the following equations: The value of the degradation coefficient 

## ct- l for low compressor speed cycling and**~-.** for high speed on/off compr.essor cycling is determined as described in section 2.1.3, or as calculated above in equation (1). 5.1.3.1 Units operating at low compressor speed (1:= 1) for which the steady-state cooling capacity, Q:.-' (T;), is great-er than or equal to the building cooling load, BL (T;), evaluate the following equations:

(2) Q<;;) =X·-I

# X Q:.-'( T;)

# X'!jJ

where

Q(T,)

. . 

### = ratio 01 total cooling {Btu) III temperat.ure

bini to the number 01temperaturebin hours.
n; is the fractional number of hours In temperature 

### N bini from 6.1.2.

where

E(T;)

. . 

## --w-= rat,o01Energyusage (watt·hr.) III temperature bini to the number oftemperaturebinhours.

(2) Xl-2=I-Xl-I
(3) Q<:;)=[Xl-'XQ:.-'(T;)
+X·-2X

### Q~;'(T;»)XN (4)

### E<:/)=[Xl-'XE~o-'(T;) +Xl-2X

### E~'-'(T;»)XN X"I=Load factor. BlAT;)= Bulldillgcooling**I~** (Btuthr) at tempera- tme (T;) from sectIOn 5.1.3. Q

..··'(T;)=Steady·state cooling capacity (BtU/hr) at temperatures (T;) from section 5.1.3.

(2) (1) 5.1.3.3 When a unit must cycle on and off at high compressor speed (k=2) in order to satisfy the huilding cooling load at a temperature 

### T;, evaluate the equations provided in section 5.1.3.1 replacing (1: = 1) data with the (k= 2) data. 5.1.3.4 When a unit operates continuously at high compressor speed (k= 2) at an outdoor temperature 

### T; evaluate the following equations: where

Q

..'(95 F) =Steady-stat. capacity measured from test A as outlined in 2.1.3. Q

..'(82 F)=Stelldy-state capacity measured from test B 811 outlined in 2.1.3. E••t( T;)

# =E

... (95 F)



# +E,,· (82 F)- 

## E,,· (95 F) [33-("X .)] 95-82 a :J CD=The degradation coellicient described in 2.1.2 or as calculated In equation (4) above. 5.1.3 Method for calculating a SEER for units with two speed compressors 01' two compressors, or cylinder unloading. The calculation procedure described in this section shall be basoo on the performance of test A and B at each of the compressor speeds for two-speed compressor units, subject to the conditions on condenser fan speed described in 3.1.3.

Units operating with two compressors shall have the SEER calculated in the same manner as two-speed compressor units. The superscripted index 1: = 1 (and the term "low-speed") designates the com- pressor that normally operates at an outdoor dry-bulb temperature of 82° F and 1=2 (and the term "high speed") denotes operation with both compressors.

In order to evaluate the steady-state capacity Q

...( T;), and power input, E".(T/), at temperature T; for each compressor speed, 1:=1, 1:=2, the results of tests A and B from 5.1 shall be userl in the following equation: 

### Q.l(T/) =Q"l (95 F)



# +Q.l (82 F) 

### -Q.l (95 F) [33- (5 X')] 95-82 :J

wben

where

Q..

....(95 F)=Steady«ate capacity measured from test A In 2.9 at the high compressor**~.** where PLF(0.5)=1-0.5XCD energy efficiency ratio (SEER) for units employing single-speed compressors and multi-speed condenser fans shall be based on the energy efficiency ratio obtained for test B and the method outlined in 2.1.2 of this Appendix to account for the perform- ance under cyclic conditions. The energy efficiency ratio for test B is obtained with the unit operating with the condenser fan speed which normally occurs at test B ambient conditions.

The seasonal energy efficiency ratio in Btu's/watt-hour shall be determined by the equation: SEER=PLF(O.5) X EERB where**EERB=:nevlne~iency** ratio determined from

PLF(O.5) =Part-load performance factor as determined from the equation:

E

..·(95 F)= Electrical power Input measured using test A as outlined in 2.1.3. E

..·(82 F)-Electrical power Input measured from U81ng test A as outlined in 2.1.3. The building cooling load BL (T;) for the four cases described in section 5.1.3.1 through 5.1.3.4 shall be obtained from the following equation: BL(T)= (5Xj) -3 X

### C1..-' (95 F) / 95-65 1.1 1 EER"o.dry C

D= _-=-E_E",R ••

:.;''''''

d",'.:...y 1-CLF (1)

(4)

The results of the cyclic and steadyI5tate dry-coil performance tests shall be used in the following (4) equations: 

### 60xVXC

...xr Qcn. dr7

## =[V

..'X (1+ W

..»)

where

T.I(/)=Dry bulb temperature of air entering the indoor coil (OF) at lim. (I). T

..(/)=Dry-bulb temperatureofair l.aving theIndoor coil roF) at time (I). (3) CLli'=

### Qoyo.d~ Q"dryXl' where CLF=cooling load factor. Q•• 0"=Totalsteady-statecoolingcapacityfromtest C (Btu/hr). 1'=Duration of time (hours) for one completa

cycle consisting of one compressor "on" time and one compressor "oft" time.

where
EER B=**~f~;" e':::Nr~~** **i~i.I~I~et.rmined** from PJ.F(O.5) = Part-load performance factor when cooling load lactor=O.5 as determined from the equation: PLF{O.5)=1-0.5XC D where

Q

.., . ...=Tota! coollng over a.eycle consisting ofone compresoor "oft"**~rIod** and one compresllOl'

. "on" period (Btu.). V=Indoor air flow rate (efm) at the dry-bulb temperature, humidity ratio, and pressure existing ill the region ofm
....urement. Cpo=Specific heat at constant pressure 01 alr- water mixture per pound 01 dry Illr, (Btujlb-°F). V.',=Specifie volmne of air-wat•.r mixture at t!'e same dry-bulb temperature, humIdIty ratIo, and pressure used in the d.tennination of the indoor air flow rate (ft'jlb). W.=Humidity ratio (lbjlb). and 

## r (hr.-OF), which is described by the equation:

where

EER

... 0",=Energy efficiency ratio from test C, (Btu! watt-hr). 5.1.1 Method for caiculating a SEER for units with single-speed compressor and single-speed condenser fans. The seasonal energy efficiency ratio for units employing single-speed compressors and single-speed condenser fans shall be based on the per· formance of test B and a method outlined in 2.1.1 and 3.1.1 of this Appendix to account for the cyclic performance.

The seasonal energy efficiency ratio in Btu's/watt-hour shall be determined by the equation: SEER

## =PLF(O.5) XEERB

### ARI STANDARD 240-81

where lating, and the average flow rate of indoor air circulated in ur'+,s of 1000 SCFM.



### 15 COPcyc(47) 

### COP•• (47) 1-HLF

Qcy.(47) 

## Q

.. (47)XT HLF 1 CD= 

### 60XVXC""xr QOEF(35) =[VnlX (1+ 

### Wn)] (1)

The actual heatmg done during the Cyclic Test, Qc,·c(47), shall be determined using the following equation: 

### 60XVXC""xr [Vn1

### X(l+W n)]

(2) where V=the flow rate during the on-period calculated in accordance with section 7.4 ofASHRAE Standard 37-78 in CFM, C••=Specific heat at constant pressure of air-water mixture per pound ofdry air, (Btu/lb-OF), V.'=Speeific volume ofair-water mixture at the same dry-bulb temperature, htunidity ratio, and· pressure used in the determination ofthe indoor air flow rate (ft'/lb). W.=IIumidity ratio (lb/lb). and 

## r (hr-OF), which is described by the equation: 

# f (time·indoorfan off) 

## r= ."

. [T a2(t)-T al(t)]dt It1me mdoorfau ou) where

T.t(t)=Dry-bulb temperature ofair entering the indoor coil (0F) at time (t). T.,(t) =Dry-bulb temperature of all' leaving the indoor eoil (OF) at time (f), The net heating, QOEF (35) in Btu's done during the test period shall be determined using the following equation:

CD=thecycliedegradationcoefficientronnded to the nearest .01 COP c••(47) as defined above COP

..(47) as defined above HLF is the heating load factor calculated as follows: i7=the average oftlte air flow rate ealculated at fom or more time interVals throughout the heating**~?r~Jf~1ei~:a:~dt~_~~:tation** iu section U C••=Specifie heat at constant pressure of air-water mixture per pound ofdry air, (Btu/lb-OF). V.'=Specilic voltune ofair-water mixture at the same dry-bUlb temperature, humidity ratio, and pres- sure used in t.he determination of tlte indoor air flow rate (ft'/Ib), W.=Humidity ratio (lb/lb), and 

### r (hr.-OF), which is described by the equation: 

# fftimC ofuext defrost termination) 

## r= (time ofdefrost termination

(3) where

T.'(t)=Dry-bulb temperature of air enteriug the indoor eoil (OF) at time (f). T.'(t) =Dry-bulb temperature ofairleavingtheindoor eoil (0F) at time (f). The cyclic degradation coefficient shall be calculated as follows:

where Units not having- an indoor fan as part of the model tested shall add 1250 Btu/hI' per 1,000 SCFM of indoor air handled to the measured capacity to obtain the total heating capacity, 

## Q

..(l7), 

### Q

.. (47) or 

### Q

.. (62), and add 365 watts per 1,000SCFM of indoor air handled to the measured power to obtain the total power input, 

## E

..(17), 

## E

..(47), or 

## E

..(62), to the unit.
The coefficients of performance (COP) for the High Temperature Tests COP••(62) or COP

..(47), and Low Temperature Test, COP

..(17), are calculated as the ratio of the heating capacity in Btu/hI' to the product of 3,413 and the power inputs to the indoor fan in watts and the power inputs to the remaining equipment com- ponents (including all controls) in watts.

Units which do not have indoor air circulating fans furnished as part of the model shall have their total heating done (Qcyc(47» and energy used Ecyc(47) in one complete cycle adjusted for the effect of circulating indoor air equipment power. For units tested without an indoor fan as pal1 of the model, Qcyc(47) shall he increased by a quantity of heat equal to the product of 1250 Btu/hr per 1,000 SCF:YI, the length ofthe on-period ofthe test cycle in hours, and the flow rate of indoor air circulated in units of 1,000 SCFM. The total energy usage, 

### Ecy.(47), shall be the sum of the energy usage required for air circulation during the test cycle and the energy used by the remaining equipment components (including all controls) during the test cycle. Units not having 

### an indoor fan as part ofthe model tested, shall set the energy required for indoor air circulation equal to the quantity given by the product of 365 watts per 1000 SCFM, the length of the on-period ofthe test cycle in hours, and the rate of indoor air circulated in units of 1000 SCFM.

The cyclic coefficient of performance, COPcyc(47) is calculated as the ratio of the total heating done (Qcyc(47» in Btu's to the product of 3.413 Btu/watt-hour and the total energy usage (E.y.(47» in watt hours. The net heating· capacity, QOEF(35) (Btu/hI'), is the total net heating done over the test peri!>d (inclurling any credit for the indoor fan heat) divided hy the total length of the test period, in hours. For units with "demand defrost control system", the net heating capacity, QDEF(3.'i), shall be multiplied hy an enhancement factor of 1.07 to compensate for improved performance not measured in the Frost Accumulation Test. FOl' units tested without indoor fans, the value determined for cJOEF(35) helow shall be increased by a quantity of heat equal to the prorluct of 1250 Btu/hi' pel' 1000 SCFM, the length of time in hours during the Frost Accumulation Test that there was indoor air circulating, and the average flow rate of indoor ail' circulated in units of 1000 SCFM.

The total energy usage, EDEF(35) shall he the sum of the energy usage required for indoor-air circulation during the test period and the energy used hy the remaining equipment components during the test period. Units not having an indoor fan as part of the model tested, shall set the energy required for indoor air circulation equal to the quantity given hy the product of 365 watts per 1000 SCFM, the length of time in hours during the Frost Accumulation Test that there was indoor air eircuE(T;) 

## 1r

as determined at each temperature bin according to the applicable conditions described in sections 5.1.3.1 through 5.1.3.4 as follows: 

# 1::, Q(T;) . 1 

### N SEER=<..1=,..=-

__ 

# 1::, E(T;) j=1 N 5.1.4 Method for calculating a SEER for units with two spe€dcompressor, two com- prcssor or cylinder unloading capable of**varyin~** the sensible to total capacity (S/T) ratio. Multi-speed compressor and twospeed compressor units capahle of varying the sensible to total capacity ratio (SIT) shall have the seasonal energy efficiency ratio determined as described in section 5.1.3. For such units, the mode of operation selected to determine the steady-state capacities Q•• k(95), 

### Q

..k(82), E"k(95), E

..k(82), and power inputs at each com- pressor speed k= 1, k=2, for tests A and B is outlined in section 2.10. and 5.1.3.5 Calculate the SEER in Btu's/ watt-hr. using the values for the terms Q(T;) 

### l{

5.2 Calculation of Heating Seasonal Performance Factors (HSPF) for AirSource Units, The testing data and results required to calculate the heating seasonal performance factor (HSPF), in Btu's per watt-hr, shall include thc following: (i) Heating capacities (Btu,hI') from the indoor air enthalpy method fOJ the High Temperature Tests, and the total heating done (Btu's) for the cyclic and frost accumulation tests. 

## Q

.. (47) or 

## Q

.. (62). 

## Q

.. (17). Qcyc(47). QOEF(35). (ii) Electrical power input to all com- ponents (watts) for the steady state tests, and the electrical usage (watt-hours) for' the cyclic and frost accumulation tests



## .8

..(47) or 

## E

.. (62). 

## E

.. (17). Ecyc(47). EOEF(35). (iii) Indoor air flow rate (SCFM) and**~xternal** resistance to indoor air flow (inches of water). (iv) 

### Air temperature (OF) Outdoor dry bulb Outdoor wet bulb or dew point Indoor dry bulb and Indoor wet bulb. (v) Data as specified in Table II of ASHRAE Standard 37-78. Where the heating capacities 

### Q

.. (47), 

## iJ

..(62) and 

## Q

.. (l7) and the indoor air flow rate are calculated using the equations specified in section 3.8.1 and 7.4 of ASHRAE standard 37-78. The total heating done, Qcyc(47) and Q(OEF35) are calculated using the equations below.

### ARI STANDARD 240-81

where where

Q

.. (4;) is the heat pump capacity measured during the High Temperature Test @ 4;0 F TOD is the outdoor design temperature given in section 0.2.4

for region 

### V =

# {2<i:.-'( 47)

2.2/1,;'(47) X as defined in 5.2.1 j n; lit as defined in**~.2.1** Tj as defined in 5.2.1

where (e) =0.;; is a correction lactor which tends to improve the agreement between calculated and measured building loads (DJiR)=the minimum and maximum design healing requirement which the heat pump is likely to enconntE>T when installed in 8 residence. rounded off to the nearest standardized DHRin section 6.2.(j in Btu's per hour ancl BL(T;) is tbp bllilding load at temperature 

### T;, in Btulhr, calculated by: BL( T;)

## =(6~5~**:£~)** X{C)

### X (DHR) where Q

.. (47) and 

## E

..{47) and QDEF(35) and 

### E

..{47) and 

## Q

..(17) and 

### E

.. (17) are the capadties (in 

### Btu/hr) and powers (in watts), measu·red during the High Temperature Test, the Frost Accumulation test, and thE: Low Temperature Test, respectively.

'For each of the six regions specified in sec- tion 6.2.5, calculate the heating seasonal performance factors and seasonal operating costs corresponding to the standardized maximum and minimum design heating requirements and for all other standardized design heating re- quirements (see section 6.2.6) between the maximum and the minimum. 5.2.2 Calculation of the heating seasonal performance factor (HSPF) for air source heat pumps with a two-speed compressor, two compressors, or cylinder unloading. For each climat.ic region listed in section 6.2.4, and for design heating requirements equal to both the standardized minimum and maximum design heating requirements defined below, calculate the HSPF defined as:

where

where (minimum design heating requiremel!tj

### Q~;-')(47)**(65~OTOD).** for regions I,



## = II, III, IV, and 

### VI**Q~-')(** 47), for region V

(maximum design heating requirement) (65- 

### TOD) • 60 • for regIOns I, 

### II, III, IV and 

### YI

where



### Q

.. ('-2)**(~;)** is the heat pump capacity measured during the high temperature perfonnance test at 4;oF, with the unit operating at the high compressor speed or with both compressors in operation, in Btu!hr TOD is the ontdoor design temperature gi

..en in section li.2.4 in degrees 0F. and

17°F<T;<45°F (E,,(47) -E,,(7» 

## E (17)+ X(T;-17)

.. 30' (QDEF(35) 

## -Q

.. (7» Q . (17) 

# + X (T;-17)

'" 18' (Q,,(47)-Q

.. 07» Q,,(l7)+

### 3~(T;-17),

T;?45°F or**T;~17°F** 

### (EDEF(35)

- 

## E .,(17)) 

### E ·**(1~)+** X(T;-17)

.. I 18' 

### 17°F<Ti

### <45°F 

## o·**T,.~ToFF**



### ,
or Q(T;) <1 (3.413)(E( T,.» 1**TOFF<T;~ToN** 

## 2; 6( T,.) 

## = Q(T,.) and >1 (3.413)(E( T,.»

- 1- T,.>T oN 

### , and maximum design heating requirement

{ . (65- 

### TOD) •

2Q

..(47) 60 • for regIOns I,



## = II, III, IV, and VI 2.2Q

.. (47), for region V

and

## Q(T~) >1 (3.413)(E(T i» - 

# jBL(Ti)

. X(T i)= Q(.T i) ;Q(T;)?BL(T,.) 1; Q(T;)**~BL(Ti)** PLF(X)=I-C D(l-X(Tj» RH( T;)

### [BL(T;)-Q(T;)X(T;)6(T;)]~ N 3.413

E(T;)=

TOFF=the outdoor temperature that the compressor is automatically shut off al (II no Sitch lempera· turf' exists, Tj is always greater than Torr and**To~.l To~=the**  outdoor temperatnre that the compressor is automatically turned on (il applicable) il designed lor low temperature automatic shut· off. Cll=dcgradation lactor detennined described in section 5.2 and 2.2.l. In using the above equation to calculate HSPF, the heat pump capacity in Btu/hr, 

### Q, ane! the power in watts, 

## It, shall be olJtained as follews:

Q(T;) = whe;-e (Cl =0.77 is a correction laclor which tends to impro\'e the agret'ment belween calculated and measured b"ild,ng loads WlfR)=the minimmn and ma,imum design**heat!n~** requirement which the heat pump is like1r to enCollntf'T whe-n installed in a residN!t'e. rounded offto the nearest standardized D H R in section ij.2G in Btn/hr RH(T i) N where

are defined by the following equations:

where

Q

.. ,(47) as defmed aboye Q

..(4;) as defined above .=Duration of time (hour.<) for one complete

cycle**consistin~** oronecompressor "on" time aud one compressor Hoff" time.

{ . (65-ToD) 

### _ Q

..(47) 60 ,for regions I,

- II, III, IV, and VI 

### Q

..(47), for region V 

# W BL(T;)

_ J -[ ni X(T i)

.

### ~N PLF(X) 6(T;)E(T;) 

# +L: RH(T;)] j N

j= 1,2,3•...• n corresponds to thej'b tempera·

turebin. n=total number of non·zero temperature bins

in the climatic region. Tj= Wi-5;) is the representative temperatnre of thejIb bin, (OF). X=indicaled the**Quantit~·** following the srmbol ; is to be summed overall temperature bins. RH(Tj)=snpplementary resistance heat term at

N temperature T; required in thosecases where lhe Imll pump automalically turns off (Ti< Tou) or when it is np.eded to meet the balance ofthe building healing requirements. n' (walts). i=isthenumberofhours in thej" temperature

• bIn dIVIded by N=X n; and IS referred to lIS

• I the ufractional hours lnjtb temperaturebin". 3.413=i5 a conversion factor which converlS watt hours to Btu. BLlTj)=buHding load at temperature Tio (Btuthr).

6(Tj)=heat pump low temperature c"t-out factor. X( T;) = heat pump healing load lactor. PLF(X)=heatpump part load factor.

The quantities BLCT,.), 6(T i), X (T,.), PLF(X) and

( 65-T) BL< T;) = 65- T: D (C)(DHR)

where (minimum design heating requirement)

5.2.1 Calculation of the heating seasonal**performan~e** factor (HSPF) for air- source heat pumps with single speed compressors. For each climatic region listed in section 6.2.4, ancl for design heating requirements equal to both the st.andardized minimum and maximnm design he!lting requirements defined below, calculate the USPF defined 

### as: 'HSPF

'These items have been corrected in accordance with a leller from the Department ofEnergy, dated December 7, 1980. 

### 16

### ARI STANDARD 240-81

E(T;)



### N RH(Tj ) N**~.-I** (17) 

### (tl;;, (47)-**Q~.='(17»** 

## + X(T;-17). 30**T;~400** 

### F**Q~-I** (17) (Q!i.·H35)

-**~.-I** (17» X (T·-17) 

## + 18 I ; 170 F 5, Tj

# <4'0° F .**Q~-I** (47)**(~-'\62)** - e;'(47»



# +**---,:-::-X.:..(~T~,!..... -_4.:..:7~)**  . 15 I



### Qk-I (T;) 

## = Ek-2( Tj)Xk-2( Tj)

## a" (T j)!!..N j E(T f) 

## -W-= PLFk-2


### lJBL( T j )[I-

### 0"( Tj )] 3.413 

### Case IH.-Units cycling on and off at high compressor speed or cycling both com- pressors on and off together (k=2) in order to satisfy the building heating load at temperature 

### T j • Qk-I( T,)<BL(T,) <Qk-2(

### Tj ) NOTE: The sllp€rscript(k=1) and (k=2) refer to the heat pump operating at low speed or single compressor operation and high speed or two compressor operation respectively. E{N

T/) is theheat ptunp electricalenergyusageinthe jt. temperature bin divided by the total number ofbin hours and is evaluated according to the four possible cases of heat pump operation denoted below in watta. RH(T/) as defined in 5.2.1 and is evaluated according

N to the four possible cases ofheat pump opera- tion denoted below (in watts). Calle I.-Units operating at low compressor speed or with a single compressor, i.e., k= 1, for which the building heating load, BL( T;) is less than or equal to the heating capacity, Qk-I( T;). BL(T;) 5, Qk-I(T;) Ek-I(T;)Xk-I(T;)&'{T;) PLFk-1 N Q;;'(17) 

## (Q;;'(47)

- 

### Q;,-'(17» X(T·-17) 

# + 30 ' i

b":;'(17)**(E~-'(** 

### 47)

-**E~-'(17»**



# + --:-.,i-X.:..('-T..!-j_-_l......;.7) • 30 ' 

### (E;.-'(47)

-**E~-'** (17» 

# + --.-:::-X...:....:...(T-,,<...·-_1_7..:.)

. 30 I 

### T;<17° 

### F E;;'(17) (Et':H35)

- £;.-1(17» 

# + --...;;.X...:....:...(**T=-,!...·-_1::..:7~)** . 18 I (troeH35)

- 

### il.;'( 17» X (T;-17), 

# + 18 I 

### 17° F<Tj 

### <45° F
£;;'(47) 

## (E;.-'{62)

- 

## E;'-'(47» 

# +**~X...:....:...(**T-,,<...·-_4..::.7..:.)

. 15 I

E;;'(17) (E\)"H35)

- E:.-'(17» 

# + -:-;:;-X.:...;(:...;:T..!..;_-..::.1:...:.7)

. 18 ' 

### 17° F<Tj

# <45° F 

### ip-2 (T j ) = Q;;'(17)



# E<J') =Ek-2(Tj)Xk-2(T;)o"(T j)

# N

RH(T j) N [BL(Tj)_Qk-2(

### Tj )Xk-2( T;)o"( Tj)]

# N

3.413 Xk-2(Tj ) 

## = 1.0 0; T j 5, TOFF

. or**Qk-2~** Tj) 

# <1 (3.413) (Ek-2( T;)

## ~; TOFF

## <'Tj 5, TON d Qk-2( T;) 

## > 1
an (3.413)(Ek-2( T;» 

## {o; Tj5, 

### TOFF 6"(T j)=

## ~; TOFF<Tj5,ToN
1; Tj>T oN 

### Case IV.-Units operating continuously at high compressor speed or with hoth com- pressors in continuous oper:l.tion (k=2) in order to satisfy the building heating load at temperature 

### T j• BL(Tj )**~Qk-2(** Tj)

1;**Tj~** TON d Qk-2(Tj) 

### > 1
an (3.413)(j,jk-2(T j» Where in each of the above cases X{T;) = heat pump heatlug load factor. PI,F=heat pnmp part load factor (not required for cases II and IV.) 6"{T;) = heat pump low temperatnre cllt-ont factor. Toll as defined in 5.2.1. Too as defined in 5.2.1. Co>-'=the part load degradation laclor described in section 2.2.1 and 5.2 for the nnit cY"ling at high compressor .peed 01' with both com· pressors simnltaneonsly cycling (if applica- ble).

. Co (>-,) = the part load**d~daLion** lactor described in secLion 2.2.1 and 5.2 for the nnit cycling at low compressorspeed or with the singlecom- =rthatIlonnally operatesat low heating &"( 

### Tj ) = 

### Case II.-Units alternating betweenhigh speed or two compressor operation (k=2) anel low speed or single compressor operation (k= 1) to satisfy the building heating load at temperature 

### T;. Qk-I( T;)< BL( T;)<(;k-2( T;) E<;j) =[Ek-I(T,)Xk-l(Tj) 

# +Ek-2( Tj)Xk-2(

### Tj )]&'( T,) ;:.
RH(T,) 

# W BL(Tj)[I-&'(T f)] N 3.413 Qk-2( Tj )

- BL(T,) Xk-I(

### Tj ) Qk-2(

### Tj ) 

## _Qi-I( Tj ) 

### X11-2 ( 

### T,) = 

### 1-X 10-1 ( 

### T,) 

# 1 0; Tj5, TOFF 6'(T,)

## ~; TOFF< T j

### 5: TOM 1; Tj>ToN RH(T;) 

# N BL(T;)[I-&'(T;)] N 3.413 Xk-I( T.)

## = !3L( T;)

, Qk-I(T;) PLFk-1

## =**l-C~'-'(** 

### l-Xf-') 

# 1 0; Tj5, TOFF &'(T;)=

## ~; TOFF<Tj5,ToN 1; T,>ToN



### 17

### ARI STAN DAR 0 

### 240-81

_

For each of the six regions specified in section 6.2.5, calculate the heating s('ason81 performance factors and seasonal operating costs correspon(ling to the standsl'dized maximum and minimum design heating requirement!! and for all othl'r standardized design heating rl'quit'emE'!nts {see section 6.2.6) between the maximum and the minimum. 

### 5.3 Calculations of the Actual Repruenlatir'e Regional Annual Performance Factor3 for Air Source Central Air Conditioner3 (Heal Pump3) Which PrQl'we Both Heatillg and Cooling. 5.3.1 Calculation of actual regional annnal performance factors (APFA) for a pSI-tirular location and for each standardized design heating requirement. (CLH A ) (Q,,l(95F» 

## + (HLHd(DHR)(C) (CLH A ) (Q,,l(95F» (SEER) 

# +(HLH,f) (DHR)(C) (HSPF)
where (eLH A) Is th. adna! eaollnl( load hOllrs for the

parti.nlar loration, determin.d from Ihe

• map In SPC'lion ti.1.3. (Q

...(95F» i. defined in 5.1. (DHR) Is Mtlned In 5.2.2. (C) Is defined in 502.2. (HLH A) i. 1he 8<'lI1al h

....tll1l( load hOllrs for the

parti.ular loration d.ttrmined from Ihe map in section fi.2.5. (SRF.R) i. Ihe seasonal .nergy effiden.y

...Uo determined in section 5.1. (lTSPF) Is the heatinl( .......,nal performall•• faclol'3 as delerminfd ill seetion 5.2 ror (,8•.'h stand- ardized design healing rtqnirpmelll within Ih. parti."lar location', rpgion or for Ihe 8<1"a! design heati", reqnir.m.nl If known. where the particular location'!! region is determinecl from the map in section 6.2.;', and, the standardized design hE'!ating re- quirements within the r('gion are determined in sections 5.2 and 6.2.6. 5.3.2 .calculation of representativE'! re- gionnl nnnual p('lformanrc factors (APFR) for padl rf'gion and for each standardized design heating re- quirement. (CLHR) (Q"k(95F» 

## +(HLH R ) (DHR) (C) (CLHR) (Q"k(95F» SEER 

# +(HLHR)(DHR)(C) HSPF (Q...(ll5F» 1.0 deOned In 6.1. (DHR) is deOned in 5.2.2. (C) Iadellned in 6.2.2.



### 18 where (CLH.) II tbe rep"""ntaUve eoo1Inl load hOUJ'll tor each heaU", load hours region, as deter- mined in section 6.3. (HLH.) Is the representative heating load hours for each region as delermined in aection 6.2.6. (SEER) II the seasonal energy emeieney

...110 as delermJned in _lion 6.1. (HSPF) I. Ihe heating seasonal performance factor as delennined in ,ection 5.2 for each region and for eeeh standardized design heaU", re- quirement within each region. where the regions are listed in section 6.2.5 and, the standal-dized design heating re- quirements within the regions are determined in sections 5.2 and 6.2.6. 1i.4 Calculation3 ofSeasonal Energy Efficiency Ratio lor Water Source V"it3 Which Prot'tde Both Heating and Cooling. (Reserved) 1i.5 Calculation of Heating Seasonal Performance Factor for Water Source Vnii3 Which Prot'ide Both Heating and Cooling. (Reserved) 5.6 Calculatio/l of Annual Performance Factor For Water Sot/rce Units Which Provide Both Healing and Cooling. (Reserved)

# -

6.0 Reference Material
6.1 Coolinq reference material 6.1. 2 

### -Distribution of fractional hours in temperature bins to be used for calculation

of the SEER for 2-speed compressor and 2- compressor units
-Test operating and test condition tolerance for cyclic dry-coil tests

Test operating tolerance (total observed

range) 1 ••••• 65 to 69 ••. 67 .214 2 ••••• 70 to 74 •.. 72 

### .231 3 .•••• 75 to 79 .•• 77 

### .216 4••••• 80 to 84 .•. 82 .161 5 .••.. fl5 to 89

... fl7 .104 6 ••••• 

### 90 to 94

... 92 .052 7 .•••• 95 to 99

... 97 .018 8 •••.• 100 to 104. 102 .004 6.1.1



### Readings, remarks

Outdoor dry-bulb air temperature, Fahrenheit: Entering ••••.••••••••• " ••••• Indoor dry-bulb air temoerature, Fahrenheit: Entering •••••••••••••.••••.•• Indoor wet-bulb air temperature, Fahrenheit: Bntering .•••.•...•••...••..•. After the 1st 30 Sec after
comnressor startup. External resistance to airflow, inches water•... Nozzle nressure drops, percent of reading .••••••• Electrical voltage inputs to the test unit, percent. 2.0

2.0

(* )

0.05


### 2.0
2.0 Test condition tolerance (variation of average from specified test condition)

0.5

0.5

(* )



### 0.02 Bin temperature range (degrees Fahrenheit)

Bin No., j: 

### Representative temperature

bin fol' (degrees Fahrenheit) Fraction (\f' 

### total temDerature bin hours**n/!'~**

\0 

### * Shall at no time exceed that value of the wet-bulb temoerature which results in the oroduction of condensate by the indoor coil at the dry-bulb temperature existinq for the air enterina the indoor portion**o~** 

### the unit. 

# > ::u


## en -.of 

# » Z C 

# » ::u 

## c I'\)


### o 

# . Q)



# ....

# » J:J
CJ) -I 

# » Z C 

# » J:J C N 01:00 

### o I CD -" 

### Distribution of Actual Coolinq Load Hours**(CJ~II1\)** 

### '1'hroughout the 

## uni lcd States

Hours Load (;.1.3



### Cooling



# ..**~68** "It



## o 6.000 6.600 2.300 6.000 6.600 6.000



# - A'aska Cana' Zone Guam Hawaii Puerto Rico Samoa Virgin 's'and

_ N 

### oBeatins Reference Katerial 6.2
6.2.1 Test operatins end test condition tolerencs for 6.2.2 rut. nneruin, aAlitaat**~o~** tglu.anc

.. &or th

...n-per1od portion of. c.yclic. .0"rfo'Clllanca.

Steady-State High Temp.ratur. T.st tat 47"F (8.3"C) or 62"F (16.7"C)] and Lov Temp.raturs Test [at 17"' (-8.J"C)] Indoor dry-bulb, ., T ••t Operating Toler.nc••* (Appl1.' after the l.t j6 sec. after compr•••

## or start-up) Test Condition**Tf.)ler.ncew~**

Tut Op.ratina* tol.t.nc. Test**Conditionv~** Tolerance Enterina Leavina
Indoor v.t-bulb, ., 2.0 0.5

** Te.t Condition Toleranc. i. the maximum permi.s.ble variation of the avera,e valu. of the mea.urement from the sc·.ndard or de.ired te.t condition. 

### * T ••t Op.r.tina Tol.rence i. the m.ximum p.rmi•••ble variation**~! an~**  mea'urement. Wh.n .xpr••••d e. a p.rc.nt.a., the m.ximum allowable ••riation i. the .pacified p.rcental. of the averale v.lue.**~.O** --- .. T ••t Condition Toleranc. i. the**~ximum** permi••abl. v.ri.tion of the .verage .elus of the

....ur.m.nt from the .t.ndard or de.ired t••t condition. * T.st Operatina Tol.ranc. is the maximUM p.rmi••abl. v.ri.tion of .ny m.asure- ment. When .xpr••••d ••• percenta,., the m.ximu= .llow.ble variation i. the sp.cified p.rcentaa. gf the avera,. v.lue.



# » :D
(J) -l 

# » Z C 

# » :D 

### C I\) 

# • o 

## • CD



# .... .02 1.0 0.5

.05 2.0

2.0 1.0

2.0 Enterina Leavina Ent.riDe Leavinl Encerina Leavinl

El.ctric.l volt.le, % Outdoor dry-bulb, .,

Outdoor v.t-bulb, .,

txt.rnal r••i.tanc. to air-flow, inch.s of Vat.r

.02 O.S

0.3 0.5



## .os 1.0 1.0 1.0 1.0 2.0 2.0

2.0 2.0 Indoor dry-bulb, ., Ent.rina Leavina
Indoor vet-bulb, ., Enterina L.avina
Outdoor dry-bulb, ., Enterina Leavina
Outdoor v.t-bulb, ., Enterin, Leavina
Ext.rnal r••i.tanc. to air flow, inch•• of vat.r
El.ctrical volta,., 

### %

N



# ....El••rricd volUI., % 2.0
1 T

..r Op.rarilll Tol.rallc. h tb

...xi_ p
.....i

...ble variarioll of .IIY

.....un-

..lIr. llh.1I .llpra

..ed '" • perc.llul., the

..xi

.."", IUow.bl. veriatioll ia the Ip.cified perc.llul. of the

....nl. vdu.. T

..t Opentiol Tol.nn•• Duri"l B

..rilll IppU" 

# "".11 the h.ar PlaP I.e ill tb. bearilll

..d•••llcept for the fir.r 5 .illut.1 .fter t.e-ill.tiOD of I defro.r cycl.. T.lt Op.rltiol Tol.r.oc. Durial Dalron .ppU•• durilll • dafro.t eycl. Illd durilll tb. fint 5 llioutu aft.r tb. t.raill.riOIl of • dafrolt cycl. 

# "".11 the haar plap ia Operltiol ia tb••••tilll eod••
2 Tut COllditioll Tol.rallc. ia the**"ll~** ,. ....i

...bl. variltioll of rh. Iverag. value of the un
..llt froe tb. IUllderd or d.lirad t.lt cOllditioa. T

..t COlldiriOll Toler c••ppU•• 0II1y "".Il tb. b••t puIlp ia operltiol io the

...tial eod•• :I ltot .ppUc.bl. dur1q d.fro.t U the adoor fall 1a off,. T•• t opel"at1uI aad test condition tol.rances for frost**.cc~1.t1oD** c••c.

Outdoor dew-poillt. OF
Eouriol 1. 5 Lo.nol 

### J> 

## ::a
(f) 

### J> Z C 

### J> 

## ::a C I\) oI:lo 

### o 

## , Q)



## ..... 'l1ltd.but1oa of fraet10llal hours ia temperature b1l1l, h.IUtl 10.d hours .nd outdoor del1gn t

....peratu

.... fa

... the diffennt cliJUt1c regionl 6.2.4

• '.eU1c Co

..t R.g10n Region I II III IV V VI Buting Lo.d Boun. BLR 750 1250 1750 2250 2750 

# I 2750·
Outdoor DOIign Teperaturo 

# I ToO for the region 37 27 17 5 -10 30 Fraetional Rours: Bin , T1 (OF) j • 1 62 .291 .ZlS .153 .132 .106 .113 2 57 .239 .189 .142 .111 .092**.20~** 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 .OS6 .092 .126 .102 

# I .034 8 27 .OOS .024 .047 .087 .094 .008 9 22 .001 .OOS .021 .055 .074 .003 10 17 0 .002 .009 .036 .055 0 11 12 0 0 .OOS .026 .047 0 12 7 0 0 .002 .013 .038 0 13 2 0 0 .001 .006 .029 0 14 -3 0 0 0 .002 .018 0 15 -8 0 0 0 .001 .010 0 16 -13 0 0 0 0 .005 0 17 -18 0 0 0 0 .002 0 18 -23 0 0 0 0 .001 0 .02 1.0 0.5

0.7 Telt Condition Tol

...n.e(2)

(He.tlnl POttlO" v::;lYJ

4.0(3)

10.0 2.0

2.0 1.0**Tut~ftl** Operatinl Tolerallee(1) Dut'lnl KeatlD, C.urul., DeT'to.t

Enterial Le••illl '.2.3

brenod r
..hulle. to .i.-flov, ill.b

.. of v.ter .05 lDdoor**d~bulb,** 

### or
Ellt.rilll Le

...illl
Illdoor ver-bulb, 

### or
Ent.dlll Le.villl
Outdoor dry-bulb, 

### or N N

# - -

6.2.5 Actual heating load hours (ULHA) 

### and regional heating load hours (IlLHi 

### for the United StQtes



### 2500



# » JJ


## en -f 

# » Z C 

# » JJ 

## c II,) .I:lo C I CD



# ... 3500 HLH 

# o HLH 

# IV

HI

Alaska Hawaii and

- Territories TtIlS map IS

### ,easonilll~ aCWlale '01

### /II~ paIlS o' the UfIIled Slilics bUI is

### Ilecessar'i~**hl!Jh~** ,yeneraliled. and cOllsequenltt /101 100 aCCUlale in mounlilinous ,eglOlIS. ""l1Iculi:/tt 

### iI Ihe Rockies 

### ]. ,

# ~""'1500 II 3000 

# VI

VI

Region**HL~** 

## Regional Heating Load Hours

I 750 II 1250 

### III 1750

IV 2250

V 2750 VI 2750

N W

### A RI STAN DA R 0 240-81

_



## 6.2.6 Standard Design Heating Requirements (Btu/hr)



## 5,000 25,000 50,000 90,000 10,000 30,000 60,000 100,000 15,000 35,000 70,000 110,000 20,000 40,000 80,000 130,000

6.3 Representative Cooling Load Hours (CLHR ) for Each Heating Load Hours Region

Region CLHR In.HR



## I 2400 750
II 

## 1800 1250


## III 1200 1750



## IV 800 2250



## V 400 2750


## VI 200 2750



## 6.4 Ground Water Temperature Map (Reserved)

(FR Doc. 79-3M293 Filed 12-17-79: 8:45 ami
BILLING CODE**64S0~1-e**



### 24

# ADDENDUM TO ARI STANDARDS 240-81 AIR-SOURCE UNITARY HEAT PUMP EQUIPMENT 210/240-84 UNITARY AIR-CONDITIONING AND AIR-SOURCE HEAT PUMP EQUIPMENT
PART-LOAD RATING CONDITIONS FOR NON-DOE COVERED SYSTEMS WHICH ARE CAPABLE OF CAPACITY CONTROL SHALL BE RATED AT EACH STEP OF CAPACITY REDUCTION PROVIDED BY THE SYSTEM, AND ALLOWED BY THE CONTROLS, AT THE CONDITIONS SHOWN IN THE FOLLOWING TABLES. 

### TABLE 1. FOR TWO SPEED, TWO COMPRESSORS, OR OTHER EQUIPMENT CAPABLE OF CAPACITY CONTROL
Indoor Outdoor Unit

Unit Air Enterina Water Air Entering Air Cooled Evaporative Cooled Cooled Water Temp DB WB DB WB DB WB IN OUT TEST F F F F F F 

### F F CJ Standard Rating Conditions, Z 

## :::; a) Cooling 

### 80 67 95 75 1 

### 95 75 85 95 

### 0 65 1 

### * 0 b) Cooling 

### 80 67 82 80 67 75 0 Standard Rating Conditions 

### 70 60 47 43



## - - - 

## - CJ (High Temperature Heating) (max) Z High Temperature Heating 

### 70 60 62 56.5



## - - - - i= Steady State (max) <t 

### w Standard Rating Conditions ::J: Low Temperature Heating 

### 70 60 17 15



### - - - 

## - (Integrated) (max)

NOTES: *SAME WATER FLOWRATE AS OBTAINED IN TEST ABOVE, 'THE WET BULB TEMPERATURE CONDITION IS NOT REQUIRED WHEN TESTING AIR-COOLED CONDENSERS WHICH DO NOT EVAPORATE CONDENSATE.



### TABLE 2. FOR INFINITELY VARIABLE CAPACITY CONTROL EQUIPMENT Entering Air Indoor Unit Outdoor Unit DB WB DB WB TEST 

### F F 

### F F Standard Rating Conditions,

Maximum compressor 

### A 

### 80 67 95 75 1 speed, steady state 

### CJ B 

### 80 67 82 65 1 Z Minimum Compressor 

## :::; a 

### 80 67 82 65 1 

### 0 speed, steady state 

### 0 b 

### 80 67 67 53.5 1 

### 0 Intermediate cooling, steady state, variable compressor speed2 

### 80 67 87 69 1 

### CJ Maximum compressor speed 

### 70 60 47 43 Z 

### 70 60 17 15 

### i= <t Minimum compressor speed 

### 70 60 62 56.5 

## w ::J: 

### 70 60 47 43

NOTES:

1 NOT REQUIRED iF CONDENSATE IS NOT REJECTED TO OUTDOOR COIL 2COMPRESSOR SPEED lS SELECTED TO PROVIDE CAPACITY EQUIVALENT TO 67% THE CAPACITY IN TEST A