1501 WILSON BOULEVARD ~. ARLINGTON, VIRGINIA 22209

1981

STANDARD for

.IIP;

...I'.

AIR-CONDITIONING

&REFRIGERATION

INSTITUTE

AIR-SOURCE UNITARY

HEAT PUMP

EOUIPMENT

I Standard 240 I

EE-RM-90-201 COMMENT OOR6
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 of conformance and to test the

equipment of any manufacturer making such claims. It is also understood that nonparticipants in the ARI Certification Program based on this standard shall have no right to 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, -by Air·Conditioning and Refrigeration Institute

Registered United States Patent and Trademark Office

EE-RM-90-201 COMMENT OOR6
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 of the 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 of Case 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

EE-RM-90-201 COMMENT OOR6
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

<-'

Z Standard Rating Conditions,

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

)

EE-RM-90-201 COMMENT OOR6
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 of the standard.

5.2 Part Load Rating. Systems which are capable of capacity reduction shall be rated at 100% and at each step

of capacity 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 Load Rating 7emperatures.

For all units

Air temperature entering indoor portion

of unit 80 F [26.7°C] dry bulb

67 F [19.4°C] wet bulb

For air-cooled units

Air temperature entering outdoor portion

of unit 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

of unit 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 of unloading. No manual adjustment of indoor and outdoor air quantities from those of the Standard

Rating Conditions shall be made. However, automatic adjustment of outdoor 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-load factor (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)

+ (PLF2 - PLF3) (EER2 ; EER3)

+ .

+ (PLF _ PLF) (EERn -] + EERn )

n-] n 2

+ (PLFn)(EERn )

where: PLF = Part-Load Factor determined from

Figure 1

n = Total number of capacity 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 of Ratings. Whenever application ratings are published or printed, they shall include, or be

accompanied by, the Standard Rating plus the Part Load

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

EE-RM-90-201 COMMENT OOR6
2

be expressed only ,in Btu/h [W] at the Standard

Rating Conditions specified in 5.1.3 plus Part Load

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 comply with 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 of this section, and shall

be such that any production unit, when tested, will meet

these ratings except for an allowance to cover testing

and manufacturing variations; the amount of allowance

to be minus 5 per cent.

June, 1987

EE-RM-90-201 COMMENT OOR6
June, 1987

PART LOAD FACTOR CURVE

1.0

./

/ Ii"'"

0.9 /

0.8

I

0.7 I

I

Ii:'

...J 0.6

0- J a::

f2 0.5 I

U I

0 0.4 If

(§

...J J

a:: I 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 of full-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

EE-RM-90-201 COMMENT OOR6
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 example calculations

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 - PLF2) \ 1 2 2

(

EER2 + EER3)

+ (PLF2 - PLF3 ) 2

+ .

+ (PLFn _ 1 - PLFn) (EERn - 12+ EERn)

+ (PLFn)(EERn)

where: PLF = Part-Load Factor determined from

Figure 1

n = Total number of capacity 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 % of full load

• 50% of full load

• 25% of full load

A3.1.2 Obtain part load factors 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

Enter the 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 x 7.4)

+ (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 calculation process see Figure A2 Example.

June, 1987

EE-RM-90-201 COMMENT OOR6
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:

0.5 I

() I Lt

0 0.4 I

(§ -- .... ...J J

a: I 0.3 g: /

) 0.2 J

/

0.1 /

40 60 80 100

..,/ , 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 of full-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

EE-RM-90-201 COMMENT OOR6
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 of the 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

EE-RM-90-201 COMMENT OOR6
A'RI STANDARD 240-81

AIR-SOURCE UNITARY HEAT PUMP EQUIPMENT

Section 1. Purpose

1.1 Purpose. The purpose of this standard is to 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 and Amendment. 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. nor to unitary heat pumps as defined in ARI

Standard 340, with capacities of 135,000 Btuh [40 kW]

or greater, 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 heat pump consists of one or more factory-made

assemblies which normally include an indoor conditioning 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 outlined in 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. These values apply to all units oflike

nominal size and type (identification) produced by the

same manufacturer. As used herein, the term "published

rating" includes the rating of all performance characteristics shown on the heat pump or published in specifications, advertising, or other literature controlled by the

manufacturer, at stated rating conditions.

3.2.1 Standard Rating. 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 of operating conditions

under which a single level of performance results, and

which causes only that level of performance 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

calculated from the capacity and power input values

obtained at Standard Rating Conditions.

3.5 Seasonal Energy Efficiency Ratio (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

total electric energy input in watt-hours during the same

period, as determined in Appendix A.

3.6 Coefficient of Performance (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 ofPerformance. A ratio

calculated from the capacity and power input values

(obtained in accordance with 3.6) at Standard Rating Heating Conditions.

3.7 Heating Seasonal Performance Factor (HSPF).

HSPF is the total heating output of a heat pump during

its normal annual usage period for heating divided by the

total electric power input during the same period, as

determined in Appendix A.

1

EE-RM-90-201 COMMENT OOR6
ARt STANDAR 0 240·81 _

3.8 "Shall", "Should", "Recommended", or "It Is 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 of this standard may be 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 of Testing for Rating Unitary

Air-Conditioning and Heat Pump Equipment (American Society of Heating, Refrigerating and AirConditioning Engineers, Inc.), and with the test methods

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 HSPF determined (as

an application rating) in accordance with Appendix A, at

the option of the 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 of the model number(s).

Standard Ratings of units which do not have indoor

air-circulating fans furnished as part of the model, i.e.,

split system with indoor coil 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 of Standard Capacity Ratings. These

ratings shall be expressed only in terms of Btu 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 of Measures of Energy 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 of the nearest 0.02.

5.1.3 Standard Rating Conditions. The conditions

of test for Standard Ratings shall include the following:

5.1.3.1 Stimdard Rating Temperatures.

a. Cooling (Not required for heating-only

units)

For all units

Air temperature entering indoor

portion of unit .. 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 of unit .. 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 of unit .. 70 F [21.1 0c] dry

bulb, 60 F

[l5.6°C] wet

bulb, max.

'For units or portions thereof intended to be installed only indoors,

this temperature may be changed to be the same as the air temperature entering the indoor portion of unit.

"tAll tests required to obtain Standard Ratings for single phase equipment rated less than 65,000 Stuh (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.

EE-RM-90-201 COMMENT OOR6
_________________________ A R I STAN DARD 240·81

Table 1-Classification of Unitary Heat Pumps

Types of Unitary 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

t A suffix of" -0" following any of the 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 of unit .. 47 F [8.3°C] dry

bulb, 43 F

[6.1°C] wet

bulb

c. Low Temperature Heating

Air temperature entering indoor

portion of unit .. 70 F [21.1 0c]

dry bulb, 60 F

[l5.6°C] wet

bulb, max.

'For units or portions thereof intended to be installed only indoors,

this temperature may be changed to be the same as the air temperature entering the indoor portion of unit.

Air temperature surrounding

unit 17 F [-8.3°C]

dry bulb*

Air temperature entering outdoor

portion of unit .. 17 F [-8.3°C]

dry bulb, 15 F

[-9.4°C]

wet bulb

5.1.3.2 Measures of Energy 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 of ARI

Standard 110 for Air-Conditioning and Refrigerating Equipment Nameplate Voltages.

3

EE-RM-90-201 COMMENT OOR6
ARI ST AN DAR 0 240-81 _

4

Standard Rating tests shall be performed at the

nameplate -rated voltage(s) and frequency.

For heat pumps with dual nameplate voltage ratings, Standard Rating tests shall be performed at

both voltages, or at the lower of the two voltages,

if only a single Standard Rating isto be published.

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] .of Standard 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] of rated

capacity) delivered when operating against

the minimum external resistance specified

in 5.1.3.7 or at a lower indoor-side air quantity if so specified by manufacturer.

b. Heat pumps which do not incorporate an

indoor fan, but are rated in combination

with a device employing a fan shall be rated

as described under a. above. For heat

pumps of this class which are rated for general use to be applied to a variety of heating

plants, the indoor side air quantity shall be

as specified by the manufacturer in his standard ratings, not to exceed 37.5 scfml1000

Btuh [0.06 tis per watt] of rated capacity or

the air quantity obtained through the indoor coil assembly when the pressure drop

across the indoor coil assembly and the 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 and dehumidifying under the 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, shall be employed in all other tests prescribed

herein without regard to resulting external static

pressure.

5.1.3.5 Outdoor-side Air 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 Requirements for Separated Assemblies.

All Standard Ratings for heat pumps in which the

outdoor section is separated from 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] of interconnection tubing on each line, of the size recommended by the manufacturer. Such heat pumps in

which the interconnection tubing is furnished as

an integral part of the machine not recommended

for cutting to length shall be tested with the complete length of tubing furnished, or with 25 feet

[7.62 m] of tubing, whichever is greater. At least

10 feet [3.05 m] of the interconnection tubing

shall be exposed to the outside conditions, with

the rest of the tubing exposed to the inside conditions. The line sizes, insulation, and details of

installation shall be in accordance with the manufacturer's published recommendations.

5.1.3.7 Minimum External Resistance. Indoor

air-moving equipment intended for use with field

installed duct systemsshall be designed to operate

against, and tested at not less than, the minimum

external resistance shown in Table 2 when delivering the rated capacity and air quantity 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 of the heap pump be in

place and that the net external resistances

specified above are available for the 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 determined by the methods prescribed

in 5.1. Application ratings in the defrost region shall

include net capacity and COP based upon a complete

defrost cycle.

EE-RM-90-201 COMMENT OOR6
_________________________ A R I ST ANDARD 240-81

Table 2. Minimum External Resistance

'Standard Capacity Ratings

(Thousands of Btuh)

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 of Ratings. Wherever application ratings are published or printed, they shall include, or be

accompanied by, the Standard Capacity Ratings and

their corresponding efficiency ratings, clearly designated

as such, including a statement of the 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

except for an allowance to cover testing 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

of this section in such a manner that 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 of unit .. 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 of this standard, at the

manufacturer's option. but not later than January I, 1982. In the

interim period, if the manufacturer does not elect the new test procedures, the requirements for this test are those shown in 6.2 of ARI

Standard 240-77.

"For units or portions thereof intended to be installed only indoors, this

temperature may be changed to be the same as the air temperature

entering the indoor portion of unit.

5

EE-RM-90-201 COMMENT OOR6
A RI ST AN DA R 0 240·81 _

6.2.1.2 Heating.

Air temperature entering indoor

portion of unit .. 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 test with a coolmg coIl aIr quantity 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 utilization voltages from

ARI Standard 110, Table 1, based upon the unit's

nameplate rated voltage(s). These voltages shall

be supplied at the unit's service connection and at

rated frequency. A lower or a higher voltage shall

be used, if listed 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 of unit.

tThis test will become effective on publication of this standard, at the

manufacturer's option, but not later than January 1, 1982. In the

interim period, if the manufacturer does not elect the 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 locked rotor. For the purpose of this 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-rotor current value of any motor shall

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 test is 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-rotor current 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

off for 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 of any of its 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 of restoration of power and

shall then operate continuously for one half hour.

EE-RM-90-201 COMMENT OOR6
_________________________ A RI STANDAR 0 240-81

Operation and resetting ofsafety devices prior to

establishment of continuous 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 of unit .. 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 of the 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 of the 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 of unit 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 of four 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 and dampers set to

produce condensate at the maximum rate, 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 of unit 80 F [26.7°C]

dry 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

6.6.2 Procedure. After establishment of the

specified temperature conditions, the heat pump

shall be started with its condensate collection pan

filled to the overflowing point 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, or blowing-off of moisture

from the unit casing.

*The wet-bulb temperature condition is not required when testing

air-source heat pumps which do not evaporate condensate.

**This test may be run i:oncurrentiy with the Insulation Efficiency Test

(See 6.5).

7

EE-RM-90-201 COMMENT OOR6
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 of the 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 Code for Mechanical 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 Heat Pumps (Underwriters' Laboratories,

Inc. Standard 559, 1975 (Rev. 1979).

Section 8. Voluntary Conformance

8.1 Conformance. Conformance with this standard shall

not be claimed or implied for unitary heat pumps coming

within the scope of this 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 M to Subpart B-Unifonn Test 1.10 "Cyclic Test" means a test where the 1.19 "Seasonal energy efficiency ratio

Method for Measuring the Energy indoor and outdoor conditions are held (SEER)" means the total cooling of a central

Consumption of Central Air Conditioners constant. but the unit is manually turned "on" air conditioner in Btu's during its normal

and "off' for specific time periods to simulate annual usage period for cooling divided by

1. Definitions part-load operation. the total electric power input in 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 of the efficiency loss due to the 1.20 "Sensible cooling" means the amount

done by a heat pump in a particular cycling of the unit. of cooling in Btu's perfonned by a unit over a

region in one year divided by the total 1.12 "Demand-defrost control system" period of time. excluding latent cooling.

electric power used 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 defrost function on the outdoor coil of the central air conditioner in 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 of performance is measured. 1.22 "Split system" means any central air

standard published in 1979 by the ARI and 1.13 "Design heating requirement (DHR)" conditioner in which one or more of the major

titled "Standard for Unitary Air-Conditioning is the amount of heating reqUired to maintain assemblies are separate from the others.

Equipment". a given indoor temperature at a particular 1.23 "Steady-state test" means a test in

1.4 "ARI Standard 240-77" means the test outdoor design temperature. which all indoor and outdoor conditions are

standard published in 1977 by the ARI and 1.14 "Dry-coil test" means a test held constant and the unit is in non-changing

titled "Standard for Air-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 evaporator coil of the increment over a dry-bulb temperature range

standard published in 1976 by the ARI and unit. of 65° F through 104' F for the cooling cycle

titled "Standard for Water-Source Heat 1.15 "Heating seasonal perfonnance and -25' F through 64° F for the heating

Pumps". factor (HSPF)" means the total heating output cycle.

1.6 "ASHRAE" means the American of a heat pump during its nonnal annual 1.25 '"Time-temperature defrost control

Society of Heating, Refrigeration and Air- usage period for 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 predetermined time interval whenever the

test standard published by ASHRAE in 1978 the ratio of the total heating done in a outdoor temperature drops below a level

and titled "Methods of Testing for Rating complete cycle of a specified time period. where frosting will occur. Unitary Air-Conditioning and Heat Pump consisting of an "on" time "off' time. to the 1.26 "Test condition tolerance" means the

Equipment." steady state heating done over the same maximum permissible variation of the

1.8 "Continuously recorded" means a period at constant ambient conditions. average of the test observations from the

method of recording measurements in 1.17 "Latent cooling" means the amount standard or desired test condition as

intervals no greater than 5 seconds. of cooling in Btu's necessary to remove water provided in 6.1.1, 6.2.1, 6.2.2, and 6.2.3 of this

1.9 "Cooling load factor (CLF)" means the vapor from the air passing over the indoor Appendix.

ratio of the total cooling done in a complete coil by condensation during a period of time. 1.27 '"Test operating tolerance" means the

cycle of a specified time period, consisting of 1.18 "Part-load factor (PLF)" means the maximum pennissible difference between the an "on" time and "off' time, to the steady- ratio of the 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 of this Appendix.

'Copied from Appendix M, pages 76707 thru 76723, Federal Register, Vol. 44, No. 249, Thursday, December 27,1979. This Appendix M is subject

to change by the U. S. Government. Only those portions of Appendix M pertaining to air-source heat pumps are to be used.

8

EE-RM-90-201 COMMENT OOR6
-----------------------__ AR I ST AN 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. Testing Required

2.1 Testing required for airsource cooling

only units with single speedcompressors.

two-speed compressors. two compressors. or cylinder unloading. 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 of 95° 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 of 82° F. Test D is a cyclic test

also conducted at an outdoor dry bulb

temperature of 82° F. In lieu of conducting

tests C and D, an assigned value of 0.25 may

be used for the degradation coefficient, CD.

2.1.1 Testing required for units with

single speed compressors and single speed

condenserfans. Test A and test B shall be

performed according to the test procedures

outlined in 4.1 of this Appendix. In addition.

the cyclic performance shall be evaluated by

conducting test C and D according to the

requirements outlined in 4.1 of this Appendix.

2.1.2 Testing required for units with

single speed compressors and multiple-speed

condenserfans. The test requirements for

multiple-speed condenser fan 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 twospeed compressors. two compressors. or cylinder unloading. The test requirements for

two-speed compressor units, two compressor

units. or units with cylinder unloading are the

same as described in 2.1.1 of this 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 twospeed compressors, two compressors, or cylinder unloading capable of varying the

sensible to total (SIT) capacity ratio. When a

unit employing a two-speed compressor, two

compressors. or cylinder unloading provides

a method of varying the ratio of the sensible

cooling capacity to the total cooling capacity.

(S/T), the test requirements are the same as

for two-speed compressor units as described

in 2.1.3 of this Appendix.

2.2 Testing required for airsource heating

only units with single speed compressors,

two-speed compressors. two compressors, or cylinder unloading. Four types of tests are

required to be performed: High Temperature,

Cyclic. Frost Accumulation. and Low

Temperature. In lieu of conducting the Cyclic

Test an assigned value of 0.25 may be used

for the degradation coefficient, CD.

2.2.1 Testing required for units with

single speed compressors. Units with single

speed compressors shall be subjected

respectively to the High Temperature Test at

4r F described in section 3.2.1.1, the Cyclic

Test as described in section 3.2.1,2, the Frost

Accumulation Test 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 twospeed compressors. two compressors, or

cylinder unloading. 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 of operation requires

cycling "on" and "off' of the 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

which provide both heating and cooling. The

requirements for units which provide both

heating and cooling shall be the same as the

requirements in Section 2.1. and 2.2 of this

Appendix.

2.4 Testing required for water source units which provide both heating and cooling.

(Reserved)

3. Testing conditions

3.1 Testing conditions for airsource cooling only units with single speed

compressors, two-speed compressors, twa

compressors or cylinder unloading_ The test

room requirement and equipment installation

procedures are the same as those specified in

sections 11.1 and 11.2 of ASHRAE 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 or forced convection while the indoor

fan is "off'. This shall be accomplished by

installing dampers upstream and downstream

of the test unit to block the off period air

flow. Values of capacity for rating purposes

are to be rounded off to the nearest 100 Btu/

hour for 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 nellrest 500 Btu/hour for capacities

between 38,000 and 64,999 Btu/hour.

The following conditions listed in ARI

Standard 210.79 shall apply to all tests

performed in Section 3.1 of this Appendix:

5.1.3.4 Cooling Coil Air Quantity.

5.1.3.6 Requirements for Separated

Assemblies.

3.1.1 Testing conditions for units with single

speed compressors and single speed

condenserfans.

3.1.1.1 Steady state wet-coil performance

tests (Test A and Test B). Test A and test B

shall be performed with the air entering the

indoor side of the unit having a dry-bulb

temperature ofsoo F and a wet-bulb

temperature of 8r F. The dry-bulb

temperature of the air entering the outdoor

side of the unit shall be 95° F in test A and

82' F in test B. The temperature of the air

surrounding the outdoor side of the unit in

each test shall be the same as the outdoor

entering air temperature except for units or

sections thereof intended to be installed only

indoors, in which case the dry-bulb

temperature surrounding that indoor side of

t.1e unit shall be 80° F. For those units which

reject condensate to the condenser, located in

the outdoor side of the unit. the outdoor wetbulb temperature surrounding the outdoor

side of the unit shall be 75° F in test A and

65° F in test B.

3.1.1.2 Steady state dry coil performance

test (Test C) and cyclic dry coil performance

test (Test D). Test C and test D shall be

performed with the air entering the indoor

side of the unit having a dry-bulb

temperature ofsoo F and a wet-bulb

temperature which does not result in

formation of condensate on the indoor coil. (It

is recommended that an indoor wet-bulb

temperature of 57° F or less be used.) The

dry-bulb temperature of the air entering the

outdoor portion of the unit shall be 82° F. The

outdoor portion of the 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 D shall be

conducted by cycling the unit "on" and "ofr'

by manual or automatic operation of the

normal control circuit of the 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 of the indoor fan "on" and "off'

periods being governed by the automatic

controls which the manufacturer normally

supplies with the unit. The results of tests C

and D shall be used to calculate a

degradation coefficient, CD by the procedures

outlined in 5.1 of this Appendix.

9

EE-RM-90-201 COMMENT OOR6
ARI STANDARD 240-81

3.1.2 Testing conditions for units with

single speed compressors and multiple-speed

condenserfans. The condenser fan speed to

be used in test A shall be that speed which

normally occurs at an outdoor dry-bulb

temperature of 95" F, and for test B, the fan

speed shall be that which normally occurs at an outdoor dry-bulb temperature of 82" F. If

elected to be performed, tests C and D shall

be conducted at the same condenser fan

speed as in test B.

3.1.3 Testing conditions for units with

two-speed compressors, two compressors. or

cylinder unloading. The condenser fan speed

used in conducting test A at each compressor

speed shall be that which normally occurs at an outdoor dry-bulb temperature of 95" F. For

test B, the condenser fan speed at each

compressor speed shall be that which

normally occurs at an outdoor dry-bulb

temperature of 82" F. If elected to be

performed, tests C and D shall be conducted

at the low compressor speed with the same

condenser fan speed as used in test B. For

those two-speed units in which the normal

mode of operation involves cycling the

compressor "on" and "off' at high speed,

tests C and D shall also be performed with

the compressor operating at high speed and

at a condenser fan speed that normally occurs at test A ambient conditions. Units

consisting of two 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 of 82" F shall be operating.

In lieu of conducting tests C and D, an assigned value of 0.25 may be used for the

degradation coefficient, 4>, at each

compressor speed. If the assigned

degradation coefficient is used for one compressor speed it must also be used for thp

other compressor speed.

In the case of units 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 conditions for units with

two-speed compressors, two compressors, or

cylinder unloading capable of varying the

sensible to total (SIT) capacity ratio. The

mode of operation selected for controlling the

SIT ratio in the performance of test A and

test Bat each compressor speed shall be such

that it does not result in an operating

configuration which is not typical of a 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 control mode as used in test B when

performed at the low compressor speed.

Likewise, tests C and D shall also be

conducted at high compressor speed (two

compressors operating) and with the same S/

T control mode as in test A when performed

at the high compressor speed.

10

In the case of units with cylinder

unloading. the loaded and unloaded

conditions correspond to high and low

compressor speed on two-speed units

respectively.

3.2 Testing conditions for airsource

heating only units with single speed

compressors, two-speed compressors, two

compressors, or cylinder unloading. The

equipment under test shall be installed

according to the requirements of Section 11.2

of ASHRAE Standard 37-78 and Section

5.1.4.5 of ARI Standard 240-77. Test chamber

requirements are the same as given in Section

11.1 of ASHRAE 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 equipment is designed (either 115 or 230

volts and 60 hertz). Values of capacity for

rating purposes are to be rounded off to the

nearest 100 Btu/hour for 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/hour for

capacities between 38,000 and 64,999 Btu/

hour.

3.2.1 Testing conditions for units with

single speed compressors.

3.2.1.1 High temperature test conditions.

The High Temperature Test at 47" F shall be

conducted at an outdoor dry-bulb

temperature of 47" F and an outdoor wet-bulb

temperature at 43" F. The High Temperature

Test at 62" F shall be conducted at an outdoor

dry-bulb temperature of 62° F and an outdoor

wet-bulb temperature of 56.5° F. For both

tests, the dry-bulb air temperature entering

and surrounding the indoor portion of the unit

shall be 70° F and a maximum wet-bulb

temperature of 60° F. The duration of the tests

shall be for a minimum of If1! hour.

3.2.1.2 Cycling test conditions. 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 indoor fan shall cycle "on" and "off', as the compressor cycles "on" and "off', except

that the indoor fan 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 indoor unit due to natural or forced convection while the indoor fan is

"off:' This shall be accomplished by

installing dampers upstream and downstream

of the test unit to block the off period airflow.

3.2.1.3 Frast accumulation test conditions.

The dry-bulb temperature and the resultant

dew-point temperature of the air entering the

outdoor portion of the unit shall be 35° F and

30° F respectively. The indoor dry-bulb

temperature shall be 70° F and the maximum

indoor wet-bulb temperature shall be 60° F.

The Frost Accumulation Test requires that

the unit undergo a defrost prior to the actual

test. The test then begins at defrost

termination and ends at the next defrost

termination. Defrost termination occurs when

the controls normally installed within 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 either the heating or defrost portion of the test

3.2.1.4 Low temperature test conditions.

The Low Temperature Test shall be

conducted at a dry-bulb temperature entering

the outdoor portion of the unit of 17" F and a

wet-bulb temperature of 15° F. The air

entering the indoor portion of the unit shall

have a dry-bulb temperature of 70° F and a maximum wet-bulb temperature of 60° F.

3.2.1.5 Additional testing conditions. All

tests shall be conducted at the indoor-side air

quantities specified in Sections 4.1.4.3 and

5.1.4.6 and Table 2 of ARI Standard 240-77.

The following conditions listed in ARI

Standard 240-77 shall apply to all tests

performed in Section 3.2 of this Appendix.

5.1.4.4 Outdoor-Side Air Quantity: and

5.1.4.5 Requirements for Separated

Assemblies.

In all tests, the specified dry-bulb

temperature entering the outdoor portion of

the unit also applies to the air temperature

surrounding the outdoor portion of the unit.

Similarly, models where portions are intended to be installed indoors shall have

the air temperature surrounding that portion

of the unit the same as the indoor air

temperature.

3.2.2 Testing conditions for units with

two-speed compressors, two compressors or cylinder unloading. The testing conditions for

two-speed compressors, two compressors, or cylinder unloading shall be the same as those

for single speed units as described in 3.2.1.

3.3 Testing conditions for airsource units

which provide both heating and cooling. 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 conditions for water source units which provide both heatiIlg and cooling.

{Reserved)

4.0 Testing procedures. 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

hea ters, etc.) delivered to the unit.

4.1 Testing procedures for airsource cooling only units with single speed

compressors, two-speed compressors, two

compressors, or cylinder unloading. All

steady-state wet- and dry-coil performance

tests on single package units shall

simultaneously employ the Air-Enthalpy

Method (Section 3 of ASHRAE Standard 37-

78) on the indoor side and one other method

consisting of either the Air-Enthalpy Method or the Compressor Calibration Method

(Section 4 of ASHRAE Standard 37-78 on the

outdoor side. AIl steady-state wet- and dryEE-RM-90-201 COMMENT OOR6
coil performance tests on split systems shall

simultaneously employ the Air-Enthalpy

Method or the Compressor Calibration

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 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 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 air flows meet the

requirements of Sections 5.1.3.4, 5.1.3.5, and

5.1.3.7 of ARI Standard 210.79.

4.1.1 Test operating procedures.

4.1.1.1 Steady-state wet-coil performance

tests (Test A and Test B). 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 of this 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 of Section 12 of the ASHRAE

Standard 37-78. The test room reconditioning

apparatus and the equipment under test shall

be operated until equilibrium conditions are

attained.

4.1.1.2 Steady-state and cyclic 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 of Sections 12.1.5, 12.1.6, 12.1.7,

of ASHRAE 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 hour before da ta 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 of ASHRAE

Standard 37-78. When the Air-Enthalpy

Method is used on the outdoor side for test C,

the requirements of this section shall apply to

both the preliminary test and the regular

equipment test; the requirements of Section

3.6 of ASHRAE 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 2 complete "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 in 4.1.3 of this

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 of ASHRAE

Standard 37.78. For the cyclic dry-coil

performance tests, the dry-bulb temperature

of the air entering 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 of indicated value and have a

response time of 2.5 seconds or less.

Response time in the time required for the

instrumentation to obtain 63 percent of the

final steady-state temperature difference

when subjected to a step change in

temperature difference of 15" F or more.

Electrical measurement devices [watt-hour

meters) used during all tests shall be accurate

to within ±0.5 percent of indicated 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 of ASHRAE

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" F of the 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 of this Appendix. Variation in

the test conditions greater than the tolerances

prescribed in 8.1.1 of this 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

of the 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 Testing procedures for air source heating only units with single speed

ARI STANDARD 240-81

compressors. two-speed compressors. two

compressors. or cylinder unloading.

4.2.1 Test operating procedures. 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 Test procedure for high

temperature test. When the outdoor AirEnthalpy 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

outdoor portion of the unit. The test roam

apparatus and test units must be operated for

at least one hour with 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 of the test. When the

outdoor Air-Enthalpy Method is used as a

second test then a preliminary test must be

conducted for a minimum of 30 minutes with

4 or more sets of data 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 of the test. frost may accumulate on

the outdoor coil. If the 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 of the test. the unit shall be

defrosted and the test restarted. Only the

results of this 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 of this Appendix.

4.2.1.2 Test procedures for the cyclic test.

The cyclic test shall follow the High

TemperatureTest and by cycled "on" and

"off" as specified in 3.2.1.2 until steadily

11

EE-RM-90-201 COMMENT OOR6
ARI ST AN DAR 0 240-81 _

repeating ambient conditions are achieved

for both the indoor and outdoor test

chambers, but for not less than 2 complete

"ofr'/"on" cycles. Without a break in 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

outdoor test room ambient conditions shall

remain within the tolerance specified in

section 6.2.2. of this Appendix. If. prior to the

High Temperature Test. the unit underwent a

defrost t:ycle to rid the outdoor coil of any

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

of this Appendix. Attention should be given

to prevent defrost after the cycling process

has begun.

4.2.1.3 Test procedures for the frost

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 of this

Appendix. The test room reconditioning

equipment and the unit under test shall be

operated for at least '/2 hour prior to the start

of a "preliminary" tesl period. The

preliminary test period and the test period

itself are to be conducted within the test

tolerances given in section 4.2.3.3 of this

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. For units 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 of a defrost cycle

which automatically occurs and shaH end at

the termination of the next automaticolly

occurring defrost cycle. For units 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 of this defroat

cycle and ends at the termination of the next

automatically occurring defroat cycle. If the

unit bas not unde1'8one a defrost after 12

hours. then the teata ahall be concluded and

the results calculated for thia 12-hour period.

For units which turn the Indoor fan off during

defrost the indoor supply duct shall be

blocked during all defrost cycles to prevent

natural or forced convection through the

indoor unit. During defrost, resistance heaters

12

normally installed with the unit shall be

prevented from operating.

4.2.1.4 Test procedures for the low

temperature test. Where applicable. the High

Temperature Test preparation and

performance requirements shall also be used

in the Low Temperature Test. The test room

reconditioning equipment shall first be

operated in a steady-state manner for at least

one-half hour 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 of its own defrost controls. The defrost

controls are to remain at the same setting as

specified in 4.2.1.3. At a time no earlier than

10 minutes after defrost termination, the test

shall start. Test duration is one-half hour. For

all units, defrost should be prevented during

the one-half hour test period.

4.2.2 Test instrumentation,

4.2.2.1 Test instrumentation for the high

temperature test. The indoor air flow rate

shall be determined as described in Section

7.1 through 7.4 of ASHRAE Standard 37-78.

This requires the construction of an air

receiving chamber and discharge chamber

separated by partition in which one or more

no;!:;!:les are located. The receiving chamber is

connected to the indoor air discharge side of

the test specimen through a short plenum.

The exhaust side of the air flow rate

measuring device contains an exhaust fan

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 of indicated

value and having minimum scale divisions

not exceedin~~ :.0 percent of the reading.

Static pressu;,e and temperature

measurements must be taken at the nozzle

throat in order to obtain density of the air.

The areas of the 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 of two places through the

nozzle throat. one at the outlets and the

others in the straight section near the ra·dius.

Th!! energy usage of the 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 of the quantity measured.

Measurements of the 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 continuously recorded

with instrumentation having a total system

accuracy within ±O.3" F of indicated value

and a response time of 2.5 seconds or less.

Temperature measurements are to be made

upstream of the static pressure tap on the

inlet and downstream of the static pressure

taps on the outlet. The indoor and outdoor

dry-bulb temperatures shall be continuously

recorded with instrumentation which will

result in an error no greater than ±0.3° F of

indicated value. The outdoor wet-bulb

temperature shall be continuously recorded.

Static pressure measurements in the ducts

and across the unit shall be made in

accordance with Section 8 of ASHRAE

Standard 37-78 using equipment which will

result in an error no greater than ±0.01 inch

of water. Static pressure measurements shall

be made and recorded at 5 minute intervals.

All other data not continuously recorded

shall be recorded at 10 minute intervals.

4.2.2.2 Test instrumentation for the

cycling test. The air flow rate during the onperiod of the Cyclic Test 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 of this Appendix.

4.2.2.3 Test instrumentation for the frost

accumulation test. The air flow rate for the

Frost Accumulation 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 of indicated value.

The outdoor dew point temperature shall be

determined with an error no greater than

±O.5° F of indicated 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) of the 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 of recording 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 of the

High Temperature Test described in section

4.2.2.1 of this Appendix.

4.2.3 Test tolerances.

4.2.3.1 Test tolerances lor the high

temDerature test. All tests shall be conducted

within the tolerances specified in Section

6.2.1. Variation greater than those given shaH

invalidate the test. The heating capacity

results by the indoor Air Enthalpy Method

shall agree within 6 percent of the value

determined by any other simultaneously

EE-RM-90-201 COMMENT OOR6
_________________________ A RI ST AN DAR D 240-81

conducted capacity test in order for the test

to be valid.

4.2.3.2 Test tolerances for the cyclic test.

The test condition tolerances and test

operating tolerances for the on-period portion

of the test cycle are specified in SectioI1 6.2.2.

Variation exceeding any specified test

tolerance shall invalidate the test results.

4.2.3.3 Test tolerances for the frost

accumulation test. Test condition and test

operating tolerances for Frost Accumulation

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 unit is operating in the

heating mode. In determining whether the

test condition tolerances are met. only the

heating portion of the test period shall be

used in calculating the average values.

Variations exceeding the tolerances

presented in Section 6.2.3 shall invalidate the

test.

4.2.3.4 Test tolerances for the low

temperature test. During the test period for

the Low Temperature Test. the operating

conditions shall be within the tolerances

specified in Section 6.2.1 of this Appendix.

4.3 Testing procedures for airsource

units which provide both heating and cooling.

The testing procedures for units which

provide both heating and cooling shall be the same as those specified in Sections 4.1 and

4.2 of this Appendix. Also during the offperiod of the dry-coil cooling test (test D). the

switch-over valve 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 of the cyclic

heating test at 47° F. the switch-over valve

shall remain in the heating mode. unless the

controls normally supplied with the unit are designed to reverse it. in which case the

controls shall operate the valve.

4.4 Testing procedures for watersource

units which provide both heating and cooling.

(Reserved)

5.0 Calculations for performance factors.

5.1 Calculations ofseasonal energy

efficiency ratios (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. if applicable. 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 power input to all

components and controls (walts) from tests

A. B. and if applicable the electrical power

input to all components and controls (watts)

from test C and the electrical usage (watthour) from test D.

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

of water).

(iv) Air temperature (0 F)

Outdoor dry bulb

Outdoor wet bulb

Indoor dry bulb

Indoor wet bulb

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 of ASHRAE

Standard 37-78. The total cooling done, Q.,..,

dry from test D. is calculated using equation

(1) below.

Units which do not have indoor air

circulating fans furnished as part of the

model shall have their measured total cooling

capacities adjusted by subtracting 1250 Btu/

hr per 1.000 CFM of measured indoor air flow

and adding to the total steady-state electrical

power input 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 of the total

cooling capacity in Btu/hr to the total

electrical power input in watts.

Units which do not have indoor air

circulating fans furnished as part of the

model shall adjust their total cooling done

and ener8l' used in one complete cycle for the

effect of circulating indoor air equipment

power. The value to be used for the

circulating indoor air equipment power shall

be 1250 Btu/hr per 1.000 CFM of circulating

indoor air. The energy usage required in one complete cycle required for indoor air

circulation is the product of the circulating

indoor air equipment power and the duration

of time in one cycle that the circulating

indoor air equipment is 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 of the 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

EE-RM-90-201 COMMENT OOR6
A RI ST ANOAR 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 Indoor fan oft) [Tal(t) - Ta2 (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·-IXQ:.-'( T;) X'!jJ

where

Q(T,) . . = ratio 01 total cooling {Btu) III temperat.ure bin i to the number 01 temperature bin hours.

n; is the fractional number of hours In temperature N bin i from 6.1.2.

where

E(T;) . . --w- = rat,o 01 Energy usage (watt·hr.) III temperature bin i to the number of temperature bin hours.

(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;) = Bulldillg cooling 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

P LF(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

CD = _-=-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 temperature of air l.aving the Indoor

coil roF) at time (I).

(3) CLli'= Qoyo.d~

Q"dry Xl'

where

CLF=cooling load factor.

Q•• 0" = Totalsteady-state cooling capacity from test C

(Btu/hr). 1'= Duration of time (hours) for one completa cycle consisting of one compressor "on" time and one compressor "oft" time.

where

EERB=~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)=1-0.5XCD

where

Q.., . ...= Tota! coollng over a.eycle consisting of one 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 of m....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

EE-RM-90-201 COMMENT OOR6
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) =[Vnl X (1+ Wn )]

(1)

The actual heatmg done during the

Cyclic Test, Qc,·c( 47), shall be determined

using the following equation:

60XVXC""xr

[Vn1X(l+Wn)]

(2)

where

V=the flow rate during the on-period calculated in

accordance with section 7.4 of ASH RAE Standard 37-78 in CFM,

C••=Specific heat at constant pressure of air-water

mixture per pound of dry air, (Btu/lb-OF),

V.'=Speeific volume of air-water mixture at the same dry-bulb temperature, htunidity ratio, and·

pressure used in the determination of the indoor

air flow rate (ft'/lb). W.=IIumidity ratio (lb/lb).

and r (hr-OF), which is described by the

equation:

f

(time·indoor fan off)

r= ." . [Ta2(t)-Tal(t)]dt It1me mdoor fau ou)

where

T.t(t) = Dry-bulb temperature of air 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 = the cyclie degradation coefficient ronnded to the nearest .01

COPc••(47) as defined above

COP..(47) as defined above

H LF 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 of dry air, (Btu/lb-OF).

V.'=Specilic voltune of air-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:

f

ftimC of uext defrost termination) r=

(time of defrost termination

(3)

where

T.'(t)=Dry-bulb temperature of air enteriug the indoor eoil (OF) at time (f).

T.'(t) = Dry-bulb temperature of air leaving the indoor

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 of the on-period of the 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 of the 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 of the 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€d compressor, 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.

EE-RM-90-201 COMMENT OOR6
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

T j 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 t he heat pump is likely to enconntE>T when installed in 8 residence.

rounded off to the nearest standardized DHR in 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 0 F.

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

2; TOFF<T;~ToN

6( T,.) = Q(T,.) and >1

(3.413)(E( T,.» -

1-, T,.>ToN

and

maximum design heating requirement

{

. (65- T OD ) •

2Q..( 47) 60 • for regIOns I,

= II, III, IV, and VI

2.2Q ..(47), for region V

and Q(T~) >1

(3.413)(E(Ti

» -

j

BL(Ti) .

X(Ti)= Q(.Ti) ;Q(T;)?BL(T,.)

1; Q(T;) ~BL(Ti)

PLF(X)=I-CD(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 bel ween 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 off to the nearest standardized D H R in section ij.2G in Btn/hr

RH(Ti )

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~ or one compressor "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

WBL(T;) _ J

-[ ni X(Ti ) .

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

+L: RH(T;)]

j N

j=1,2,3•...• n corresponds to the j'b tempera· ture bin.

n=total number of non·zero temperature bins

in the climatic region.

Tj= Wi-5;) is the representative temperatnre of the jIb bin, (OF).

X=indicaled the Quantit~· following the srmbol ; is to be summed over all temperature bins.

RH(Tj) =snpplementary resistance heat term at

N temperature T; required in those cases where

lhe Imll pump automalically turns off

(Ti< Tou) or when it is np.eded to meet the balance of the building healing requirements. n' (walts).

i=isthenumber of hours in thej" temperature • bIn dIVIded by N=X n; and IS referred to lIS • I

the ufractional hours lnjtb temperature bin".

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)=heat pump part load factor.

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

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

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 of Energy, dated December 7, 1980.

16

EE-RM-90-201 COMMENT OOR6
ARI STANDARD 240-81

E(T;)

N

RH( T j )

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( T j) Xk-2( T j)a" (Tj) !!..Nj

E(Tf )

-W-= PLFk-2

lJB L( T j)[I- 0"( T j )]

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 Tj •

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{NT /) is the heat ptunp electrical energy usage in the

jt. temperature bin divided by the total

number of bin 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 of heat 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 (Tj ) =

Q;;'(17)

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

RH(Tj)

N

[BL( T j) _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;)

~; T OFF<' Tj 5, TON

d Qk-2( T;) >1

an (3.413)(Ek-2( T;»

{

o; T j 5, TOFF

6"(Tj )= ~; TOFF<Tj5,ToN

1; Tj>ToN

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 Tj •

BL( T j ) ~Qk-2( T j )

1; Tj~ TON

d Qk-2( T j ) > 1

an (3.413)(j,jk-2(Tj »

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 compressor speed or with the single com- =rthat Ilonnally operates at low heating

&"( T j ) =

Case II.-Units alternating between high

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( T j )

+Ek-2( T j)Xk-2( Tj )]&'( T,) ;:.

RH(T,) WBL(Tj)[I-&'(Tf )]

N 3.413

Qk-2( T j ) - BL( T,) Xk-I( Tj )

Qk-2( Tj ) _Qi-I( T j )

X 11-2 ( T,) = 1-X 10-1 ( T,)

1

0; Tj5, TOFF

6'( T,) ~; T OFF < T j 5: TOM

1; Tj>ToN

RH(T;) NBL(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

EE-RM-90-201 COMMENT OOR6
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.

(CLHA ) (Q,,l(95F»

+(HLHd(DHR)(C)

(CLHA ) (Q,,l(95F»

(SEER)

+(HLH,f) (DHR)(C)

(HSPF)

where

(eLHA) 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. (HLHA) 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»

+(H LHR ) (DH R) (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) Ia dellned 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 of Seasonal 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)

EE-RM-90-201 COMMENT OOR6
-

6.0 Reference Material

6.1 Coolinq reference material

6.1. 2 -Distribution of fracti

temperature bins to be us

of the SEER for 2-speed 

compressor 

-Test operating and test condition

tolerance for cyclic dry-coil tests

Test

operating

tolerance

(total

observed

range) 1 ••••• 65 to 69 ••. 67 

2 ••••• 70 to 74 •.. 72 

3 .•••• 75 to 79 .•• 77 

4 ••••• 80 to 84 .•. 82 

5 .••.. fl5 to 89 ... fl7 

6 ••••• 90 to 94 ... 92 

7 .•••• 95 to 99 ... 97 

8 •••.• 100 to 104. 102 

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)

\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.
Distribution of Actual Coolinq Load Hours (CJ~

'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

o
Beatins Reference Katerial 6.2

6.2.1 Test operatins end test condition tolerencs for

6.2.2 rut. nneruin, aAlitaat ~o~tglu.an

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 Tole

(Appl1.' after the 

sec. after compr••

start-up)

Tut Op.ratina*

tol.t.nc.

Test Conditionv~

Tolerance

Enterina

Leavina

Indoor v.t-bulb, .,

2.0 

** 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••ab

.elus of the ....ur.m.nt from the .t.ndard or de.

* T.st Operatina Tol.ranc. is the maximUM p.rmi••ab

ment. When .xpr••••d ••• percenta,., the m.ximu

the sp.cified p.rcentaa. gf the avera,. v.lue.

.05

1.0

2.0

2.0

2.0

Encerina

Leavinl

Ent.riDe

Leavinl

Enterina

Leavina

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

0.5

O.S

0.3

.os

2.0

2.0

1.0

1.0

2.0

2.0

1.0

1.0

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

'l1ltd.but1oa of fraet10llal hours ia temperatu

10.d hours .nd outdoor del1gn t ....peratu.... fa... 

cliJUt1c regionl

6.2.4

• '.eU1c Co..t R.g10n

Region I II III 

Buting Lo.d Boun. BLR 750 1250 1750 

Outdoor DOIign Teperaturo

ToO for the region 37 27 17 

Fraetional Rours:

Bin , T1 (OF)

j • 1 62 .291 .ZlS .153 

2 57 .239 .189 .142 

3 52 .194 .163 .138 

4 47 .129 .143 .137 

5 42 .081 .112 .135 

6 37 .041 .088 .118 

7 32 .019 .OS6 .092 

8 27 .OOS .024 .047 

9 22 .001 .OOS .021 

10 17 0 .002 .009 

11 12 0 0 .OOS 

12 7 0 0 .002 

13 2 0 0 .001 

14 -3 0 0 0 

15 -8 0 0 0 

16 -13 0 0 0 

17 -18 0 0 0 

18 -23 0 0 0 

.02

0.5

1.0

0.7

Telt Condition Tol ...n.e(2)

(He.tlnl POttlO" v::;lYJ

4.0(3)

10.0

2.0

1.0

2.0

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

HI

Alask

Hawa

Terr

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

EE-RM-90-201 COMMENT OOR6
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

Z Standard Rating Conditions,

:::; a) Cooling 80 67 95 751 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 95 751

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 87 691

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

EE-RM-90-201 COMMENT OOR6