ARI-550-590 Standar Untuk AC

ARI Standard 550/590

4100 N. FAIRFAX DR., SUITE 200 • ARLINGTON, VIRGINIA 22203

2003 Standard for

Performance RatingOf Water -ChillingPackages Using TheVapor Compression Cycle

Price $10.00 (M) $20.00 (NM) Copyright 2003, by Air-Conditioning, Heating and Refrigeration InstitutePrinted in U.S.A. Registered United States Patent and Trademark Office

IMPORTANT

SAFETY DISCLAIMER

AHRI does not set safety standards and does not certify or guarantee the safety of any products, components orsystems designed, tested, rated, installed or operated in accordance with this standard/guideline. It is stronglyrecommended that products be designed, constructed, assembled, installed and operated in accordance withnationally recognized safety standards and code requirements appropriate for products covered by thisstandard/guideline.

AHRI uses its best efforts to develop standards/guidelines employing state-of-the-art and accepted industrypractices. AHRI does not certify or guarantee that any tests conducted under its standards/guidelines will benon-hazardous or free from risk.

ARI CERTIFICATION PROGRAM PROVISIONS

Scope of the Certification Program

60 Hz PowerIncluded in Certification Program

Water-Cooled Air-Cooled

All compressor types All compressor typesRated up to 2000 tons [7034 kW] at ARI Standard RatingConditions

Rated up to 200 tons [ 703 kW] at ARI Standard RatingConditions

Hermetic & open type, electric motor driven Hermetic & open type, electric motor driven

Voltages up to 5000 volts Voltages up to 600 volts

Excluded from Certification Program


Condenserless chillers Condenserless chillers

Evaporatively cooled chillers Evaporatively cooled chillers

Chillers above 2000 tons [7034 kW] Chillers above 200 tons [703 kW]

Chillers with voltages above 5000 volts Chillers with voltages above 600 volts

Chillers powered by other than electric motor drives Chillers powered by other than electric motor drives

Chillers with motors not supplied with the unit by Secondary coolant ratings (other than water)

The manufacturer Free cooling

Secondary coolant ratings (other than water) Heat recovery & heat pump ratings

Free cooling

Heat recovery & heat pump ratings

ARI CERTIFICATION PROGRAM PROVISIONS (CONTINUED)

Scope of the Certification Program (Continued)

50 Hz PowerIncluded in Certification Program


Centrifugal & screw chillers with continuous unloadingRated 200 - 1000 tons [703-3517 kW] at ARI StandardRating Conditions

Hermetic & open type, electric motor driven Not applicable

Voltages up to 5000 volts

Excluded from Certification Program


Scroll & reciprocating compressor chillers

with step unloading

Condenserless chillers

Evaporatively cooled chillers Not applicable

Chillers below 200 tons [703 kW]

Chillers above 1000 tons [3517 kW]

Chillers with voltages above 5000 volts

Chillers powered by other than electric motor drives

Chillers with motors not supplied with the unit by

The manufacturer

Secondary coolant ratings (other than water)

Free cooling

Heat recovery & heat pump ratings

Certified Ratings

The Certification Program ratings verified by test are:

1. Capacity, tons [kW]2. Energy Efficiency, as applicable:

Power Input per Capacity, kW/ton [kW/kW] Energy Efficiency Ratio (EER), Btu/(Wh) Coefficient of Performance (COP), watts/watt [W/W]

3. Water pressure drop, psi or ft H2O [kPa]4. Integrated Part-Load Value (IPLV) (Section 5.4.1)5. Non-Standard Part-Load Value (NPLV) (Section 5.4.1)

Items 1- 5 are at Standard Rating Conditions (Section 5.2) and at non-standard Rating Conditions (Section 5.3) forboth full and part load (Section 5.4 for part-load performance requirements).

Note:

This standard supersedes ARI Standard 550/590-98 with addenda

TABLE OF CONTENTS

SECTION PAGE

Section 1. Purpose ..............................................................................................................................1

Section 2. Scope .................................................................................................................................1

Section 3. Definitions .........................................................................................................................1

Section 4. Test Requirements .............................................................................................................2

Section 5. Rating Requirements .........................................................................................................3

Section 6. Minimum Data Requirements for Published Ratings......................................................12

Section 7. Marking and Nameplate Data..........................................................................................13

Section 8. Conformance Conditions ...............................................................................................13

TABLES

Table 1. Standard Rating Conditions...............................................................................................4

Table 2. Heat Reclaim Standard Rating Conditions........................................................................5

Table 3. Part-Load Conditions for Rating .......................................................................................6

FIGURES

Figure 1. Part-Load Efficiency Curve...............................................................................................7

Figure 2. Air-Cooled Condenser Entering Air Temperature vs. % Load .........................................9

Figure 3. Allowable Tolerance Curves for Full and Part Load.........................................................9

Figure 4. IPLV and NPLV Tolerance Curve .................................................................................11

APPENDICES

Appendix A. References - Normative ...................................................................................................14

Appendix B. References - Informative .................................................................................................14

Appendix C. Method of Testing Water ChillingPackages Using the Vapor Compression Cycle - Normative..........................................15

Appendix D. Derivation of Integrated Part-Load Value (IPLV) - Normative ......................................24

TABLES FOR APPENDICES

Table D1. Group 1 Air-Cooled IPLV Data and Calculation ............................................................28

Table D2. Group 1 Water-Cooled IPLV Data and Calculation........................................................29

Table D3. Group 1 - 4 IPLV Summary ............................................................................................30

FIGURES FOR APPENDICES

Figure D1. Ton-Hour Distribution Categories...................................................................................25

Figure D2. Bin Groupings – Ton-Hours ............................................................................................26

Figure D3. Group 1 Ton-Hour Distribution Categories ....................................................................26

Figure D4. Group 2 Ton-Hour Distribution Categories ....................................................................26

ARI STANDARD 550/590-2003

1

PERFORMANCE RATING OF WATER-CHILLINGPACKAGES USING THE VAPOR COMPRESSION CYCLE

Section 1. Purpose

1.1 Purpose. The purpose of this standard is toestablish for Water-Chilling Packages using the vaporcompression cycle: definitions; test requirements; ratingrequirements; minimum data requirements for PublishedRatings; marking and nameplate data; and conformanceconditions.

1.1.1 Intent. This standard is intended for theguidance of the industry, including manufacturers,engineers, installers, contractors and users.

1.1.2 Review and Amendment. This standard issubject to review and amendment as technologyadvances.

Section 2. Scope

2.1 Scope. This standard applies to factory-madevapor compression refrigeration Water-Chilling Packagesincluding one or more hermetic or open drivecompressors. These Water-Chilling Packages include:

Water-Cooled, Air-Cooled, or Evaporatively-Cooled Condensers,

Air-Cooled or Water-Cooled Heat ReclaimCondensers,

Packages supplied without a Condenser.

Section 3. Definitions

All terms in this document follow the standard industrydefinitions in the current edition of ASHRAETerminology of Heating, Ventilation, Air Conditioningand Refrigeration unless otherwise defined in this section.

3.1 Bubble Point. Refrigerant liquid saturationtemperature at a specified pressure.

3.2 Compressor Saturated Discharge Temperature.For single component and azeotrope refrigerants, it is thesaturated temperature corresponding to the refrigerantpressure at the compressor discharge. For zeotropicrefrigerants, it is the arithmetic average of the Dew Pointand Bubble Point temperatures corresponding torefrigerant pressure at the compressor discharge. It isusually taken at or immediately downstream of thecompressor discharge service valve (in either case on thedownstream side of the valve seat), where dischargevalves are used.

3.3 Condenser. A refrigeration system componentwhich condenses refrigerant vapor. Desuperheating andsub-cooling of the refrigerant may occur as well.

3.3.1 Air-Cooled Condenser. A componentwhich condenses refrigerant vapor by rejectingheat to air mechanically circulated over its heattransfer surface causing a rise in the airtemperature.

3.3.2 Air-Cooled Heat Reclaim Condenser. Acomponent which condenses refrigerant vapor inthe process of rejecting the heat of condensation toair causing a rise in the air temperature. ThisCondenser may be a separate Condenser the sameas or a portion of the Air-Cooled Condenser.

3.3.3 Evaporatively-Cooled Condenser. Acomponent which condenses refrigerant vapor byrejecting heat to a water and air mixturemechanically circulated over its heat transfersurface, causing evaporation of the water and anincrease in the enthalpy of the air.

3.3.4 Water-Cooled Condenser. A componentwhich utilizes refrigerant-to-water heat transfermeans, causing the refrigerant to condense and thewater to be heated.

3.3.5 Water-Cooled Heat Reclaim Condenser.A component which utilizes refrigerant-to-waterheat transfer means, causing the refrigerant tocondense and the water to be heated. ThisCondenser may be a separate condenser, the sameas, or a portion of the Water-Cooled Condenser.

3.4 Dew Point. Refrigerant vapor saturationtemperature at a specified pressure.

3.5 Energy Efficiency.

3.5.1 Coefficient of Performance (COP). Aratio of the cooling capacity in watts [W] to theTotal Power Input, in watts [W] at any given set ofRating Conditions, expressed in watts/watt [W/W].

3.5.2 Energy Efficiency Ratio (EER). A ratio ofthe cooling capacity in Btu/h [W] to the TotalPower Input in watts [W] at any given set of RatingConditions, expressed in Btu/(Wh).


2

3.5.3 Heat Reclaim Coefficient of Performance(COPHR). A ratio of the Net Heat ReclaimCapacity (Btu/h) to the Total Power Input to theunit, W converted to Btu/h

3.5.4 Power Input per Capacity. A ratio of theTotal Power Input to the unit, in kW to the NetRefrigerating Capacity at any given set of RatingConditions, expressed in kW/ton [kW/kW].

3.6 Fouling Factor. The thermal resistance due tofouling accumulated on the heat transfer surface.

3.6.1 Fouling Factor Allowance. Provision foranticipated fouling during use specified inhft2ºF/Btu [m2ºC/W].

3.7 Net Heat Reclaim Capacity. A quantity defined asthe mass flow rate of the condenser water multiplied bythe difference in enthalpy of water entering and leavingthe heat reclaim Condenser, Btu/h [kW].

3.8 Net Refrigeration Capacity. A quantity defined asthe mass flow rate of the evaporator water multiplied bythe difference in enthalpy of water entering and leavingthe evaporator, Btu/h or tons [kW].

3.9 Part-Load Value (PLV). A single number figure ofmerit expressing part-load efficiency for equipment on thebasis of weighted operation at various partial loadcapacities for the equipment.

3.9.1 Integrated Part-Load Value (IPLV). Asingle number part-load efficiency figure of meritcalculated per the method described in thisstandard at Standard Rating Conditions.

3.9.2 Non-Standard Part-Load Value (NPLV).A single number part-load efficiency figure ofmerit calculated per the method described in thisstandard referenced to conditions other than IPLVconditions. (For units that are not designed tooperate at Standard Rating Conditions.)

3.10 Published Ratings. A statement of the assignedvalues of those performance characteristics, under statedRating Conditions, by which a unit may be chosen to fitits application. These values apply to all units of likenominal size and type (identification) produced by thesame manufacturer. The term Published Rating includesthe rating of all performance characteristics shown on theunit or published in specifications, advertising or otherliterature controlled by the manufacturer, at stated RatingConditions.

3.10.1 Application Rating. A rating based ontests performed at application Rating Conditions(other than Standard Rating Conditions).

3.10.2 Standard Rating. A rating based on testsperformed at Standard Rating Conditions.

3.11 Rating Conditions. Any set of operating conditionsunder which a single level of performance results andwhich causes only that level of performance to occur.

3.1.1 Standard Rating Conditions. RatingConditions used as the basis of comparison forperformance characteristics.

3.12 "Shall" or "Should". "Shall" or "should" shall beinterpreted as follows:

3.12.1 Shall. Where "shall" or "shall not" is usedfor a provision specified, that provision ismandatory if compliance with the standard isclaimed.

3.12.2 Should, "Should" is used to indicateprovisions which are not mandatory but which aredesirable as good practice.

3.13 Total Power Input. Power input of all componentsof the unit.

3.14 Water-Chilling Package. A factory-made andprefabricated assembly (not necessarily shipped as onepackage) of one or more compressors, Condensers andevaporators, with interconnections and accessories,designed for the purpose of cooling water. It is a machinespecifically designed to make use of a vapor compressionrefrigeration cycle to remove heat from water and rejectthe heat to a cooling medium, usually air or water. Therefrigerant Condenser may or may not be an integral partof the package.

3.14.1 Heat Reclaim Water-Chilling Package. Afactory-made package, designed for the purpose ofchilling water and containing a Condenser forreclaiming heat. Where such equipment isprovided in more than one assembly, the separateassemblies are to be designed to be used together,and the requirements of rating outlined in thisstandard are based upon the use of matchedassemblies. It is a package specifically designed tomake use of the refrigerant cycle to remove heatfrom the refrigerant and to reject the heat toanother fluid (air or water) for heating use. Anyexcess heat may be rejected to another medium,usually air or water.

Section 4. Test Requirements

4.1 Test Requirements. Ratings shall be established atthe Rating Conditions specified in Section 5. Ratingsshall be verified by tests conducted in accordance with thetest method and procedures described in Appendix C.


3

Section 5. Rating Requirements

5.1 Standard Ratings. Standard Ratings for all Water-Chilling Packages shall be established at the StandardRating Conditions specified in 5.2.

5.2 Standard Rating Conditions. Water-ChillingPackages shall be rated at conditions specified in Table 1.Heat Reclaim Water-Chilling Packages shall be rated atconditions specified in Table 2 and properly identified asthe Heat Reclaim Standard Rating. Standard Ratingsshall include a water-side Fouling Factor Allowance of0.00025 hft2ºF/Btu [0.000044 m2ºC/W] for theCondenser and 0.0001 hft2 ºF/Btu [0.000018m2ºC/W]for the evaporator.

5.3 Application Rating Conditions. ApplicationRatings should include the following range of RatingConditions or be within the operating limits of theequipment:

All Condenser Types:

Leaving chilled water temperature ......40.0 to48.0ºF [4.4 to 8.9ºC] in increments of 2ºF or less[1ºC or less].

Water-Cooled Condensers:

Entering condenser water temperature ......65.0 to105.0ºF [18.3 to 40.6ºC] in increments of 5ºF orless [3C or less].

Air-Cooled Condensers:

Entering Condenser air dry-bulb temperature......55.0 to 125.0F [12.8 to 51.7C] dry-bulb inincrements of 10F or less [6C or less].

Evaporatively-Cooled Condensers:

Entering Condenser air wet-bulb temperature......50.0 to 80.0F [10.0 to 26.7C] wet-bulb inincrements of 2.5F or less [1.4C or less].

5.4 Part-Load Rating. Water-Chilling Packages whichare capable of capacity reduction shall be rated at 100%and at each step of capacity reduction provided by therefrigeration system(s) as published by the manufacturer.Part-load ratings points shall be presented in one or moreof the following three ways:

a. IPLV- Based on the conditions defined inTable 3.

b. NPLV- Based on the conditions defined inTable 3.

c. Separate Part-Load Data Point(s) Suitable forCalculating IPLV or NPLV. In addition, otherpart-load points may also be presented.

5.4.1 Determination of Part- LoadPerformance. For Water-Chilling Packagescovered by this standard, the IPLV or NPLV shallbe calculated as follows:

a. Determine the part-load energyefficiency at 100%, 75%, 50%, and25% load points at the conditionsspecified in Table 3.

b. Use the following equation tocalculate the IPLV or NPLV.

0.12D+0.45C+0.42B+0.01A=orIPLV

NPLV 1a

For COP and EER:

where: A = COP or EER at 100%B = COP or EER at 75%C = COP or EER at 50%D = COP or EER at 25%

For kW/ton:

D

0.12+

C

0.45+

B

0.42+

A

0.01

1=

IPLV

NPLVor

1b

where: A = kW/Ton at 100%B = kW/Ton at 75%C = kW/Ton at 50%D = kW/Ton at 25%

5.4.1.1 For a derivation of equations 1aand 1b, and an example of an IPLV orNPLV calculation, see Appendix D. Theweighting factors have been based on theweighted average of the most commonbuilding types and operations usingaverage weather in 29 U.S. cities, withand without airside economizers.


4

Tab

le1.

Sta

nd

ard

Rati

ng

Co

nd

itio

ns

Air

-Co

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d

Co

nd

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rW

ater

Co

nd

ense

rF

ou

lin

gF

acto

rA

llo

wan

ce

0.0

h·

ft2

·ºF

/Btu

0.0

m2

·ºC

/W

En

teri

ng

Air

95

.0ºF

35.0

ºC

Ev

apo

rato

rW

ater

44

.0ºF

6.7

ºC

2.4

gpm

/to

n0

.04

3L

/sp

erk

W

Ev

apo

rato

rF

ou

ling

Fac

tor

All

ow

ance

0.0

001

h·

ft2

ºF/B

tu0

.00

0018

m2

·ºC

/W

Wit

ho

ut

Co

nd

ense

r

12

5.0

ºF51

.7ºC

10

5.0

ºF40

.6ºC

29

.92

inH

g1

01.

3k

Pa

Ev

apo

rati

vel

y-C

oo

led

0.0

ft2

·ºF

/Btu

0.0

m2

·ºC

/W

75

.0ºF

23.

9ºC

44

.0ºF

6.7

ºC

2.4

gpm

/to

n0

.04

3L

/sp

erk

W

0.0

001

h·

ft2

ºF/B

tu0

.00

001

8m

2·

ºC/W

10

5.0

ºF4

0.6

ºC

98

.0ºF

36.

7ºC

29

.92

inH

g10

1.3

kP

a

Wat

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oo

led

85

.0ºF

29.4

ºC

3.0

gpm

/to

n0

.05

4L

/sp

erk

W

0.0

002

5h

·ft

2·º

F/B

tu0

.00

004

4m

2·

ºC/

W

44

.0ºF

6.7

ºC

2.4

gpm

/to

n0

.04

3L

/sp

erk

W

0.0

001

h·

ft2

ºF/B

tu0

.000

018

m2

·ºC

/W

10

5.0

ºF40

.6ºC

98

.0ºF

36.7

ºC

29

.92

inH

g1

01.3

kP

a

En

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ng

Flo

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ate

Wat

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ide

Air

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lb

Wet

-Bu

lb

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g

Flo

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ate

Wat

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ide

Sat

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ted

Dis

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uid

Ref

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t

Bar

om

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ure


5

Tab

le2.

He

at

Recla

imS

tan

dard

Rati

ng

Co

nd

itio

ns

Air

-Co

ole

d

Co

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ense

rW

ater

Flo

wra

tesa

me

asin

stan

dar

dco

oli

ng

rati

ngs

En

teri

ng

Air

40

.0ºF

4.4

ºC

44

.0ºF

6.7

ºC

0.0

h·

ft2

·ºF

/Btu

Hea

tR

ecla

imC

on

den

ser

70

.0ºF

21.

1ºC

95

.0ºF

35

.0ºC

29

.92

inH

g10

1.3

kP

a

Ev

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ng

rati

ngs

38

.0ºF

3.3

ºC

44

.0ºF

6.7

ºC

0.0

h·

ft2

·ºF

/Btu

29

.92

inH

g1

01

.3k

Pa

Wat

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75

.0ºF

23

.9ºC

Flo

wra

tesa

me

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stan

dar

dco

oli

ng

rati

ng

s

44

.0ºF

6.7

ºC

0.0

002

5h

·ft

2·º

F/B

tu

10

5.0

ºF4

0.6

ºCo

ro

r9

5.0

ºF3

5.0

ºC

12

0.0

ºF4

8.9

ºCo

ro

r1

05

.0ºF

40

.6ºC

29

.92

inH

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1.3

kP

a

Tem

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6

Table 3. Part-Load Conditions for Rating

IPLV NPLVEvaporator (All Types)100% load LWT0% load LWTFlow Rate (gpm)F.F.A.

244.0 ºF44.0 ºF32.4 gpm/ton0.0001 h · ft2 · ºF/Btu

6.7 ºC6.7 ºC0.043 L/s per kW0.000018 m2 · ºC/ W

2Selected LWTSame as 100% load3Selected gpm/tonAs Specified

2Selected LWTSame as 100% load3[L/s per kW]As Specified

1Water-Cooled Condenser100% load EWT75% load EWT50% load EWT25% load EWT0% load EWTFlow rate (gpm) [L/s]F.F.A.

285.0ºF75.0 ºF65.0 ºF65.0 ºF65.0 ºF33.0 gpm/ton0.00025 h · ft2 · ºF/Btu

29.4 ºC23.9 ºC18.3 ºC18.3 ºC18.3 ºC0.054 L/s per kW0.000044 m2 · ºC/ W

2Selected EWT4

4

4

65.0 ºF3Selected gpm/tonAs Specified

2Selected EWT4

4

4

18.3 ºC3L/s per kWAs Specified

1Air-Cooled Condenser (Use Figure 2)100% load EDB75% load EDB50% load EDB25% load EDB0% load EDBF.F.A.

95.0 ºF80.0 ºF65.0 ºF55.0 ºF55.0 ºF0.0 hft2ºF/Btu

35.0 ºC26.7 ºC18.3 ºC12.8 ºC12.8 ºC0.0 m2ºC/W

No Rating Requirements

1Evaporatively-Cooled Condenser100% load EWB0% load EWBF.F.A.

75.0 ºF50.0 ºF0.0 hft2ºF/Btu

23.9 ºC10.0 ºC0.0 m2ºC/W


Air-Cooled Without Condenser100% load SDT0% load SDT

125.0 ºF55.0 ºF

51.7 ºC12.8 ºC


Water and Evaporatively-CooledWithout Condenser100% load SDT0% load SDT

105.0 ºF65.0 ºF

40.6 ºC18.3 ºC


1 If the unit Manufacturer’s recommended minimum temperatures are greater than those specified in Table 3, then those maybe used in lieu of the specified temperatures.

2 Corrected for Fouling Factor Allowance by using the calculation method described in C6.33 The flow rates are to be held constant at full load values for all part-load conditions.4 For part-load entering condenser water temperatures, the temperature should vary linearly from the selected EWT at 100%

load to 65.0 ºF at 50% loads, and fixed at 65.0F for 50% to 0% loads.

SDT - saturated discharge temperatureLWT - leaving water (liquid) temperatureEWT - entering water (liquid) temperatureEDB - entering air dry-bulb temperatureEWB - entering air wet-bulb temperatureF.F.A. - Fouling Factor Allowance


7

5.4.1.2 The IPLV or NPLV ratingrequires that the unit efficiency bedetermined at 100%, 75%, 50% and 25% atthe conditions as specified in Table 3. Ifthe unit, due to its capacity control logiccan not be operated at 75%, 50%, or 25%capacity then the unit shall be operated atother load points and the 75%, 50%, or25% capacity efficiencies shall bedetermined by plotting the efficiencyversus the % load using straight linesegments to connect the actualperformance points (Figure 1). The 75%,50%, or 25% load efficiencies shall then bedetermined from the curve. Extrapolationof data shall not be used. An actual chillercapacity point equal to or less than therequired rating point must be used to plotthe data. For example, if the minimumactual capacity is 33% then the curve canbe used to determine the 50% capacitypoint, but not the 25% capacity point.

If a unit cannot be unloaded to the 25%,50%, or 75% capacity point, then the unitshall be run at the minimum step ofunloading at the condenser entering wateror air temperature based on Table 3 for25%, 50% or 75% capacity points asrequired. The efficiency shall then bedetermined by using the followingequation:

InputPowerTotalMeasuredC

CapacityCoolingMeasuredEER

D 2

where CD is a degradation factor toaccount for cycling of the compressor forcapacities less than the minimum step ofcapacity. CD should be calculated usingthe following equation:

1.13+LF)0.13(-=CD

where LF is the load factor calculatedusing the following equation:

capacity)unitload(Part

capacity)unitload(Full100

FL%

=LF

where % FL is the % of full load atstandard rating points, i.e. 75%, 50%,and 25%.

Part-Load unit capacity is the measuredor calculated unit capacity from whichStandard Rating points are determinedusing the method above.

5.4.1.3 Sample Calculation. Thefollowing is an example of an IPLVcalculation:

Part-Load Values Provided

Step Capacity(tons)

Input(kW)

EER

3 (full) 100.0 92.3 13.00

2 72.1 57.4 15.07

1* 41.3 31.3 15.83

1** 41.8 33.3 15.06

* Minimum possible unit capacity at load conditions.** Performance at minimum step at 25% load

conditions

Using the above data the part-load EER valuecan be calculated.

Part-Load Values Provided

Point Load% Capacity

(tons)

EER

A 100% 100 13.00

B 75% 75 14.85

C 50% 50 15.62


8

Because the unit cannot unload to 25%capacity, the following additionalcalculations are required to determine point“D”, using the minimum capacity datapoint listed above that was determined atthe minimum step of capacity at theconditions of a 25% capacity.

0.60=41.8

(100)x(0.25)=LF

CD = (-0.13 x 0.60) + 1.13 = 1.05

hW

Btu14.35=

1000x33.3x1.05

12000x41.8=EER

Using the A, B, C and D efficiencies theIPLV can then be calculated as follows:

IPLV (EER) = (0.01 x 13.00) + (0.42 x14.85) + ( 0.45 x 15.62)+ (0.12 x 14.35)

=15.12 Btu/(Wh)

5.5 Fouling Factor Allowances. When ratings arepublished, they shall include those with Fouling Factors asspecified in Table 1. Additional ratings, or means ofdetermining those ratings, at other Fouling FactorAllowances may also be published.

5.5.1 Method of Establishing Clean and FouledRatings from Laboratory Test Data.

5.5.1.1 A series of tests shall be run inaccordance with the method outlined inAppendix C to establish the unit’sperformance.

5.5.1.2 Evaporator water-side andcondenser water-side or air-side heattransfer surfaces shall be consideredclean during testing. Tests will beassumed to reflect Fouling Factors of 0.0hft2 F/Btu [0.0 m2C/W].

5.5.1.3 To determine the capacity of theWater-Chilling Package at the ratedfouling conditions, the procedure definedin C6.3 shall be used to determine anadjustment for the evaporator and orcondenser water temperatures.

5.6 Tolerances.

5.6.1 Allowable Tolerances. The allowabletest tolerance on capacity, tons [kW], EER, COP,Power Input per Capacity kW/ton [kW/kW] andheat balance shall be determined from thefollowing equation:

Tolerance %

)FL%xDT

E(+)FL%x(0.07-10.5=

FL

DTFL = Difference between entering andleaving chilled water temperature atfull load, F [C]

E = 1500 for IP, [833.3] for SI units

See Figure 3 for graphical representation only.


9


10

5.6.2 Full Load. To comply with this standard,published or reported Net Refrigeration Capacityshall be based on data obtained in accordance withthe provisions of this section, and shall have a NetRefrigeration Capacity and full load efficiency ofnot less than 100 % of its ratings within theallowable tolerance. The allowable tolerance shallbe determined by the equation specified in 5.6.1.

Water pressure drop in the evaporator andCondenser shall not exceed 115 % of the ratedpressure drop at the specified water flow rate.

Full Load Example in EER (in IP Units only forclarity):

Rated Full Load Performance

Rated Capacity = 100 tonsRated Power = 92.3 kWEvaporator DTFL = 10F

)hW(

Btu13.0=

1000W/kWkW x92.3

hBtu/ton12000xtons100=EER

Allowable Test Tolerance =

100%x10

1500+100%)x(0.07-10.5

= 10.5 - 7 + 1.5 = 5%

Min. Allowable Capacity =

tons95=100x

100

tons5tons100

Min. Allowable EER =

)hW(

Btu12.35=

)hW(

Btu13.0x

100

5-100

Max. power at min. capacity =

kW92.3=

1000x)hW(

Btu12.35

hBtu/ton12000xtons95

Full Load Example in kW/ton (in IP Units only forclarity):

Rated full load performance

Rated capacity = 100 tonsRated power = 70 kWCooling DTFL = 10ºF

ton

kW0.70=apacityCperInputPowerTotal

Allowable Test Tolerance:

100)x(10

(1500)+100)x(.07-10.5=Tolerance

= 10.5 – 0 7 + 1.5 = 5%

= 95 tons

70.100

)5100(/. xtonkWallowableMax

= .735 kW/ton

Max. power at min. capacity

= .735 x 95 = 69.825 kW

5.6.3 Part-Load. The tolerance on part-loadEER shall be the tolerance as determined from5.6.1.

Part-Load Example in EER (in IP Units only forclarity):

Rated Part-Load Performance

Power at 69.5% Rated Capacity = 59.6 kW69.5% Rated Capacity = 69.5 tonsCooling DTFL = 10.0F

)hW(

Btu14.0=

1000x59.6

12000x69.5=EER

Allowable Test Tolerance =

%5.69x10

1500%)5.6907.0(5.10

= 10.5 - 4.87 + 2.16 = 7.8%

100x100

)5100(capacityallowable.Min

ARI STANDARD 550/590 2003

11

Min. Allowable EER =

EER12.91=14.0x

100

7.8-100

Part-Load Example in kW/ton (in IP Units only forclarity):

Rated Part-Load Performance

50% capacity = 50 tons50% power = 35 kWTotal Power Input per Ton = 0.70 kW/tonFull Load DTFL = 10ºF

Allowable Test Performance

Tolerance = 10.5 - (.07 x 50) +

= 10.5 - 3.5 + 3 = 10%

Max. allowable Total Power Input per Ton

=

= 0.77 kW/ton

5.6.4 IPLV and NPLV Tolerances. Theallowable tolerance on IPLV and NPLV shall bedetermined by the following equation:

Allowable Percent ToleranceFLDT

355.6

See Figure 4

The single number IPLV or NPLV, calculated forthe part-load conditions, shall not be less than therated IPLV or NPLV, less the allowable tolerance.

50x10

(1500)

.70x100

10%)+(100


12

Section 6. Minimum Data Requirements forPublished Ratings

6.1 Minimum Data Requirements for PublishedRatings. As a minimum, Published Ratings shall includeall Standard Ratings. All claims to ratings within thescope of this standard shall include the statement "Ratedin accordance with ARI Standard 550/590." All claims toratings outside the scope of the standard shall include thestatement "Outside the scope of ARI Standard 550/590."Wherever Application Ratings are published or printed,they shall include a statement of the conditions at whichthe ratings apply.

6.2 Published Ratings. Published Ratings shall state allof the standard operating conditions and shall include thefollowing.

6.2.1 General.

6.2.1.1 Refrigerant designation inaccordance with ANSI/ASHRAEStandard 34.

6.2.1.2 Model number designationsproviding identification of the Water-Chilling Packages to which the ratingsshall apply.

6.2.1.3 Net Refrigeration Capacity, tons[kW].

6.2.1.4 Total Power Input to chiller, bhpor kW, as applicable.

6.2.1.5 Energy Efficiency, expressed asEER, COP or kW/ton.

6.2.1.6 Evaporator Fouling Factor,h · ft2 · ºF/Btu [m2 · ºC/ W], as stated inTable 1.

6.2.1.7 Chilled water entering andleaving temperatures, ºF [ºC] (as stated inTable 1), or leaving water temperature andtemperature difference, ºF [ºC].

6.2.1.8 Evaporator water pressure drop(inlet to outlet), psi or ft H2O [kPa].

6.2.1.9 Chilled water flow rate, gpm[L/s].

6.2.1.10 Nominal voltage, V, andfrequency, Hz, for which ratings are valid.

6.2.2 Water-Cooled Condenser Packages.

6.2.2.1 Condenser water pressure drop(inlet to outlet), psi or ft H2O [kPa].

6.2.2.2 Any two of the following:

Entering condenser water temperature, ºF[ºC]Leaving condenser water temperature, ºF[ºC]Water temperature rise through thecondenser, ºF [ºC]

6.2.2.3 Condenser water flow rate, gpm[L/s].

6.2.2.4 Condenser Fouling Factor,h · ft2 · ºF/Btu [m2 · ºC/ W], as stated inTable 1.

6.2.3 Air-Cooled Condenser Packages.

6.2.3.1 Entering air dry-bulbtemperature, ºF [ºC] (as stated in Table 1).

6.2.3.2 Power input to fan(s), kW [kW].

6.2.4 Evaporatively-Cooled CondenserPackages.

6.2.4.1 Entering air wet-bulbtemperature, ºF [ºC] (as stated in Table 1).

6.2.4.2 Power input to fan(s) andpump(s), kW [kW].

6.2.4.3 Condenser spray pump powerconsumption, kW [kW].

6.2.4.4 Statement of Condenser FoulingFactor Allowance on heat exchanger,h · ft2 · ºF/Btu [m2 · ºC/ W].

6.2.5 Packages without Condenser (for use withRemote Condensers).

6.2.5.1 Compressor saturated dischargetemperature, ºF [ºC] (as stated in Table 1).

6.2.5.2 Liquid refrigerant temperatureentering chiller package, ºF [ºC] (as statedin Table 1).

6.2.5.3 Condenser heat rejectioncapacity requirements, Btu/h [kW].

ARI STANDARD 550/590 2003

13

6.2.6 Heat Reclaim Condenser(s).

6.2.6.1 Heat Reclaim Capacity, MBtu/h[kW].

6.2.6.2 Water pressure drop, psi or ftH2O [kPa] or air pressure drop, in H2O[kPa].

6.2.6.3 Entering and leaving heat reclaimCondenser air or water temperatures, ºF[ºC] (stated in Table 2).

6.2.6.4 Heat reclaim Condenser air flowrate, cfm [m3/s] or heat reclaim Condenserwater flow rate, gpm [L/s].

6.2.6.5 Fouling Factor, h · ft2 · ºF/Btu[m2 · ºC/ W], as stated in Table 1 (forwater heat reclaim Condensers only).

Section 7. Marking and Nameplate Data

7.1 Marking and Nameplate Data. As a minimum, thenameplate shall display the following:

a. Manufacturer's name and locationb. Model number designation providing complete

identificationc. Refrigerant designation (in accordance with

ANSI/ASHRAE Standard 34d. Voltage, phase and frequency

Nameplate voltages for 60 Hertz systems shall includeone or more of the equipment nameplate voltage ratingsshown in Table 1 of ARI Standard 110. Nameplatevoltages for 50 Hertz systems shall include one or more ofthe utilization voltages shown in Table 1 of IEC StandardPublication 60038.

Section 8. Conformance Conditions

8.1 Conformance. While conformance with thisstandard is voluntary, Conformance shall not be claimedor implied for products or equipment within thestandard’s Purpose (Section 1) and Scope (Section 2)unless such product claims meet all of the requirements ofthe standard and all of the testing and rating requirementsare measured and reported in complete compliance withthe standard. Any product that has not met all therequirements of the standard cannot reference, state, oracknowledge the standard in any written, oral, orelectronic communication.


14

APPENDIX A. REFERENCES - NORMATIVE

A.1 Listed here are all standards, handbooks and otherpublications essential to the formation andimplementation of the standards. All references in thisappendix are considered as part of the standard.

A1.1 ANSI/ASHRAE Standard 30-1995,Method of Testing Liquid Chilling Packages, 1995,American Society of Heating, Refrigeration, andAir-Conditioning Engineers, Inc. ASHRAE, 25West 43rd Street, 4th Fl., New York, NY, 10036,U.S.A./1791 Tullie Circle, N.E., Atlanta, Georgia,30329, U.S.A.

A1.2 ANSI/ASHRAE Standard 34-2001 withAddenda, Number Designation and SafetyClassification of Refrigerants, 2001, AmericanSociety of Heating, Refrigeration, and Air-Conditioning Engineers, Inc., ASHRAE, 25 West43rd Street, 4th Fl., New York, NY, 10036,U.S.A./1791 Tullie Circle, N.E., Atlanta, Georgia,30329, U.S.A.

A1.3 ANSI/ASHRAE Standard 41.1-86 (RA2001), Measurements Guide - Section onTemperature Measurements, 2001, AmericanSociety of Heating, Refrigeration, and Air-Conditioning Engineers, Inc. ASHRAE, 25 West43rd Street, 4th Fl., New York, NY, 10036,U.S.A./1791 Tullie Circle, N.E., Atlanta, Georgia,30329, U.S.A.

A1.4 ARI Standard 110-2002, Air-Conditioningand Refrigerating Equipment Nameplate Voltages,2002, Air-Conditioning and Refrigeration Institute,4100 North Fairfax Drive, Suite 200, Arlington,VA 22203, U.S.A.

A1.5 ASHRAE Terminology of HeatingVentilation, Air Conditioning and Refrigeration,Second Edition, 1991, American Society ofHeating, Refrigeration, and Air-ConditioningEngineers, Inc. ASHRAE, 1791 Tullie Circle,N.E., Atlanta, Georgia, 30329, U.S.A.

A1.6 ASME Standard PTC 19.2-1987,Instruments and Apparatus, Part 2, PressureMeasurement, 1987, American Society ofMechanical Engineers. ASME, 345 East 47thStreet, New York, NY 10017, U.S.A.

A1.7 IEC Standard Publication 60038, IECStandard Voltages, 1983, InternationalElectrotechnical Commission, rue de Varembe,P.O. Box 131, 1211 Geneva 20, Switzerland.

A1.8 ISA Standard RP31.1, RecommendedPractice Specification, Installation, andCalibration of Turbine Flowmeters, 1977,Instrument Society of America, ISA, 67 AlexanderDrive, P.O. Box 12277, Research Triangle Park,NC 27709, U.S.A.

APPENDIX B. REFERENCES - INFORMATIVE

None.


15

APPENDIX C. METHOD OF TESTING WATER-CHILLINGPACKAGES USING THE VAPOR COMPRESSION CYCLE -

NORMATIVE

C1. Purpose. The purpose of this appendix is toprescribe a method of testing for Water-Chilling Packagesusing the vapor compression cycle and to verify capacityand power requirements at a specific set of conditions.

Testing shall occur where instrumentation and loadstability is provided.

Testing shall not be conducted in field installations wheresteady state conditions are difficult to achieve andprovisions for measurement are not made.

C2. Definitions. Definitions for this appendix areidentical with those in Section 3 of this standard.

C3. Test Methods.

C3.1 Test Method.

C3.1.1 The test will measure net coolingcapacity (tons of refrigeration) and energyrequirements, at a specific set ofconditions.

C3.1.2 To confirm that steady-stateconditions have been established at thespecific set of conditions and within thetolerances set forth in C6.2.1, three sets ofdata shall be taken, at a minimum of five-minute intervals. To minimize the effectsof transient conditions, test readingsshould be taken as simultaneously aspossible.

C3.1.3 The test shall include ameasurement of the net heat removedfrom the water as it passes through theevaporator by determination of thefollowing:

a. Water flow rate, gpm [L/s]b. Temperature difference

between entering andleaving water °F, [°C]

C3.1.4 The heat removed from thechilled water is equal to the product of thechilled water flow rate, the watertemperature difference, and the specificheat of the water defined by equation C6.

C3.1.5 If supplied with the Water-Chilling Package, the test shall include

simultaneous determination of the heatreclaim Condenser capacity by obtainingthe data as defined in C5.1.6 for Water-Cooled Heat Reclaim Condensers andC5.1.7 for Air-Cooled Heat ReclaimCondensers.

C3.1.5.1 For Water-CooledHeat Reclaim Condensers, theheat reclaim capacity shall bedetermined by obtaining thefollowing data:

a. Fluid flow rate, gpm [L/s]b. Temperature difference

between entering andleaving water °F, [°C]

The heat rejected through theheat reclaim Condenser is equalto the product of the heat reclaimCondenser water flow rate, thewater temperature difference, andthe specific heat of water asdefined by equation C7.

C3.1.5.2 For Air-Cooled HeatReclaim Condensers, the heatreclaim capacity shall bedetermined by obtaining thefollowing data:

a. Heat Reclaim Condenser airflow rate, standard cfm[m3/s] (for air)

b. Heat reclaim Condenser airtemperature differencebetween entering andleaving air

The heat rejected through theAir-Cooled Heat ReclaimCondenser is equal to the productof the heat reclaim Condenserairflow rate, the air temperaturedifference, and the specific heatof moist air as defined byequation C8.

C3.1.5.3 The test shall includethe determination of thecompressor power requirement.This power shall be determined

ARI STANDARD 550/590- 2003

16

by measurement of electricalinput to the motor drive (seeC7.1.4). For motors supplied byothers, the determination ofcompressor shaft horsepowerinput shall be outlined in the testprocedure. For Air-Cooled orEvaporatively-CooledCondensers, the test shall includethe determination of theCondenser fan and Condenserspray pump power requirements.

C3.1.5.4 Non-Electric Drive.Where turbine or engine drive isemployed, compressor shafthorsepower input shall bedetermined from steam, gas, oroil consumption, at measuredsupply and exhaust conditionsand prime mover manufacturer'scertified performance data.

C3.1.6 Test Verification.

C3.1.6.1 For the case ofWater-Cooled Condensers, inaddition to the determination ofnet heat removed and energyinput required, data shall betaken to prepare a heat balance(C6.4.1) to substantiate thevalidity of the test.

C3.1.6.2 For Air-Cooled andEvaporatively- CooledCondensers, it is impractical tomeasure heat rejection in a test;therefore, a heat balance cannotbe calculated. To verify testaccuracy, concurrent redundantinstrumentation method (C6.4.2)shall be used to measure watertemperatures, flow rates, andpower inputs.

C3.1.6.3 For heat reclaimunits with Air-CooledCondensers or Water-CooledCondensers, where the capacityis not sufficient to fully condensethe refrigerant, the concurrentredundant instrumentationmethods (C6.4.2) shall be used.

C3.1.6.4 For heat reclaimunits with Water-CooledCondensers that fully condense

the refrigerant, the heat balancemethods (C6.4.1) shall be used.

C3.2 Condition of Heat Transfer Surfaces.

C3.2.1 Tests conducted in accordancewith this standard may require cleaning(in accordance with manufacturer'sinstructions) of the heat transfer surfaces.The as tested Fouling Factors shall then beassumed to be 0.0 h ft2 F/Btu [0.0 m2 C/W].

C4 Instrumentation.

C4.1 Accuracy of instruments selected shall bein accordance with ANSI/ASHRAE Standard 30.

C4.2 Temperature measurements shall be madein accordance with ANSI/ASHRAE Standard 41.1.

C4.3 Flowmeters shall be constructed andinstalled in accordance with the applicable portionof ANSI/ASHRAE Standard 30. Turbine flowmeters may be also used in accordance with ISAStandard RP31.1.

C4.4 Scales for analog meters shall be such thatreadings will be at least one-third of full scaledeflection. All instruments, including gauges andthermometers shall be calibrated over the range oftest readings.

C4.5 Pressure measurements shall be made inaccordance with ASME Power Test Code PTC19.2.

C5 Measurements.

C5.1 Data to be Recorded During the Test.

C5.1.1 Test Data. Compressor/Evaporator (All Condenser Types):

a. Temperature of waterentering evaporator, F [C]

b. Temperature of waterleaving evaporator, F [C]

c. Chilled water flow rates,gpm [L/s]

d. Power input to compressorelectrical power, kW [kW]

Steam consumption ofturbine, lb/h [kg/h]

Steam supply pressure, psig[kPa]


17

Steam supply temperature,ºF [ºC]Steam exhaust pressure, psigor in Hg vac [kPa], or

Gas consumption of turbineor engine, therms or ft3/h,[m3/s] and calorific value,Btu/ft3, [J/L], or

Fuel consumption of dieselor gasoline, gal/h [L/s] andcalorific value, Btu/gal [J/L]

e. Evaporator water pressuredrop (inlet to outlet), psi or ftH2O [kPa]

f. Electrical power input tocontrols and auxiliaryequipment, kW [kW] (if notincluded in d)

C5.1.2 Water-Cooled Condenser).

a. Temperature of waterentering the Condenser, F[C]

b. Temperature of waterleaving the Condenser, F[C]

c. Condenser water flow rate,gpm [L/s]

d. Condenser water pressuredrop (inlet to outlet), psi or ftH2O [kPa]

C5.1.3 Air-Cooled Condenser.

a. Dry-bulb temperature of airentering the Condenser, F[C]

b. Condenser fan motor powerconsumption, kW [kW]

c. Barometric pressure, in Hg[kPa]

C5.1.4 Evaporatively-CooledCondenser.

a. Wet-bulb temperature of airentering the Condenser, F[C]

b. Condenser fan motor powerconsumption, kW [kW]

c. Condenser spray pumppower consumption, kW[kW]

d. Barometric pressure, in Hg[kPa]

C5.1.5 Without Condenser.

a. Discharge temperatureleaving compressor, F [C]

b. Discharge pressure leavingcompressor, psig [kPa]

c. Liquid refrigeranttemperature entering theexpansion device, F [C]

d. Liquid pressure entering theexpansion device, psig [kPa]

C5.1.6 Water-Cooled Heat ReclaimCondenser.

a. Temperature of heat reclaimentering Condenser water,F [C]

b. Temperature of heat reclaimleaving Condenser water, F[C]

c. Heat reclaim Condenserwater flow rate, gpm [L/s]

d. Heat reclaim Condenserwater pressure drop (inlet tooutlet), psi or ft H2O [kPa]

C5.1.7 Air-Cooled Heat ReclaimCondenser.

a. Dry-bulb temperature of airentering the heat reclaimCondenser, F [C]

b. Dry-bulb temperature of airleaving the heat reclaimCondenser, F [C]

c. Heat reclaim Condenserstandard air flow rate, cfm,[m3/s]

d. Barometric pressure, in Hg[kPa]

C5.1.8 If chilled water is used to removeheat from any other source(s) within thepackage, the temperature and flowmeasurements of chilled water must bemade at points so that the measurementreflects the net package cooling capacity.

C5.1.9 If Condenser water is used tocool the compressor motor or for someother incidental function within thepackage, the temperature and flowmeasurements of condenser water must bemade at points, so that the measurementreflects the gross package heat rejection.


18

C5.2 Auxiliary Data to be Recorded forGeneral Information.

C5.2.1 Nameplate data including make,model, size and refrigerant, sufficient tocompletely identify the water chiller. Unitvoltage and frequency should be recorded.

C5.2.2 Compressor driver or input rpmfor open-type compressors.

C5.2.3 Ambient temperature at test site,F [C].

C5.2.4 Actual voltage, V, and current,Amps, for each phase of all electric motordrives.

C.5.2.5 Motor, engine or turbinenameplate data.

C5.2.6 Pressure, in H2O [kPa],temperature, F [C] and exhaust pressure,in H2O [kPa] for steam turbine nameplatedata.

C5.2.7 Fuel gas specification for gasturbine drive, including pressure, in H2O[kPa].

C5.2.8 Heat balance for C6.4.

C5.2.9 Date, place, and time of test.

C5.2.10 Names of test supervisor andwitnessing personnel.

C6 Test Procedure.

C6.1 Preparation for Test.

C6.1.1 The Water-Chilling Package,which has been completely connected inaccordance with the manufacturer'sinstructions and is ready for normaloperation, shall be provided with thenecessary instrumentation.

C6.1.2 The test shall not be started untilnon-condensables have been removedfrom the system.

C6.1.3 At the manufacturer’s option,Condenser and cooler surfaces may becleaned as provided in C3.2.1.

C6.2 Operations and Limits.

C6.2.1 Start the system and establish thetesting conditions in accordance with thefollowing tolerances and instructions.

C6.2.1.1 Evaporator (AllCondenser Types)

a. The chilled water flow rate,gpm [L/s], shall not deviatemore than + 5% from thatspecified.

b. The individual readings ofwater temperature leavingthe evaporator shall not varyfrom the specified values bymore than 0.5F [0.3C].Care must be taken to insurethat these water temperaturesare the average bulk streamtemperatures.

c. The leaving chilled watertemperature shall be adjustedby an increment calculatedper C6.3 corresponding tothe specified field foulingallowance required for test.

d. Part-load tests for Water-Chilling Packages whichhave continuous capacitymodulation must be takenwithin + 2% of the full loadtons at the specified partload capacity.

e. For water chillers withdiscrete steps of capacitycontrol, the part-load testsshall be taken as close aspractical to the specifiedpart- load capacity as perTable 3.

C6.2.1.2 Water-CooledCondenser.

a. The water flow rate, gpm[L/s], through the Condensershall not deviate more than +5% from that specified.

b. The individual readings ofwater temperatures enteringthe refrigerant Condensershall not vary from thespecified values by morethan 0.5F [0.3C]. Caremust be taken to insure thatthese water temperatures are


19

the average bulk streamtemperatures.

c. The entering condensingwater temperature shall beadjusted by an incrementcalculated per C6.3corresponding to thespecified Fouling FactorAllowance.

C6.2.1.3 Air-CooledCondenser, Including HeatReclaim.

a. The average entering air dry-bulb temperature to theCondenser shall not varyfrom the specified values bymore than 1.0F [0.6C].

b. For heat reclaim Air-CooledCondensers the Condenserair flow rate shall not deviatefrom that required for test bymore than + 5%.

C6.2.1.4 Evaporatively-Cooled Condenser.

a. The entering air wet-bulbtemperature shall not varyfrom the values required fortest by more than 0.5F[0.3C].

C6.2.1.5 Chiller WithoutCondenser.

a. The saturated dischargetemperature shall not varyfrom the values required fortest by more than 0.5F[0.3C].

b. The liquid refrigeranttemperature shall not varyfrom the specified values bymore than 1.0F [0.6C].

C6.2.1.6 Miscellaneous.

a. For electrically drivenmachines, voltage andfrequency at the unitterminals shall bemaintained at the nameplatevalues within tolerances of +10% on voltage and + 1% onfrequency.

b. For steam-turbine drivenmachines, steam conditions

to the turbine, andCondenser pressure orvacuum, shall be maintainedat nameplate values.

c. For gas-turbine or gas-engine operating machines,gas pressure to turbine orengine, and exhaust back-pressure at the turbine orengine shall be maintained atnameplate values.

d. In all cases, the governor, ifprovided, shall be adjustedto maintain rated compressorspeed.

C6.3 Method for Simulating Fouling FactorAllowance at Full Load and Part-Load Conditions.

C6.3.1 Obtain the log mean temperaturedifference (LMTD) for the evaporatorand/or Condenser using the followingequation at the specified Fouling FactorAllowance (ffsp).

C1

R = Water temperature range= absolute value (twl - twe), F[C]

S = Small temperature difference= absolute value (ts - twl), F [C]

C6.3.2 Derivation of LMTD:

1ws

wes

1wswes

tt

ttln

ttttLMTD

1wtst

ttttln

tt=

we1w1ws

we1w

The Incremental LMTD (ILMTD) isdetermined using the following equation:

)A

q(spff=ILMTD C2

S

R+1ln

R=LMTD


20

C6.3.3 The water temperature needed tosimulate the additional fouling, TDa, cannow be calculated:

TDa = Ssp - Sc C3a

1-ezR

-spS=TDa C3b

where:

ILMTD-LMTD

R=Z

1e

R=S zc

Ssp = Small temperature difference asspecified, F [C]

Sc = Small temperature difference astested in cleaned condition, F[C]

The water temperature difference, TDa, isthen added to the Condenser enteringwater temperature or subtracted from theevaporator leaving water temperature tosimulate the additional Fouling Factor.

C6.3.4 Example-Condenser FoulingInside Tubes (in I.P Units for clarity):

Specified Fouling Factor Allowance,ffsp =0.00025 h ft2 F/BtuCondenser load, q = 2,880,000 Btu/h

Specified Condenser leaving water temp,Twl = 95F

Specified Condenser entering water temp,Twe = 85 F

Inside* tube surface area, Ai = 550 ft2

*(Since fouling is inside tubes in thisexample)

Saturated condensing temperature,ts = 101 F

Ssp = ts - twl = 101 - 95 = 6 F

R = twl - twe = 95 - 85 = 10 F

R/S)+1(ln

R=LMTD

10.2=10/6)+(1ln

10=

ffsp = 0.00025

= 1.31

where:

1-e

10-6.0=

aTD 1.125

= 6.0 - 4.8 = 1.2F

The entering Condenser watertemperature for testing is then raised 1.2Fto simulate the Fouling Factor Allowanceof 0.00025 h ft2 F/Btu. The enteringcondenser water temperature will be 85 +1.2 or 86.2F.

C6.4 Test Verification:

C6.4.1 Heat Balance-SubstantiatingTest.

C6.4.1.1 Calculation of HeatBalance. In most cases, heatlosses or heat gain caused byradiation, convection, bearingfriction, oil coolers, etc., arerelatively small and may or maynot be considered in the overallheat balance.

Omitting the effect of the smallheat losses and gains mentionedabove, the general heat balanceequation is as follows:

qev + Winput = qcd + qhrc

)A

q(ff sp=ILMTD

550

2,880,0000.00025=

1-ezR

-Ssp=a

TD

ILMTD-LMTD

R=Z

1.125=1.31-10.2

10=Z


21

where:

Winput = compressor workinput as defined in C6.4.1.2through C6.4.1.4

C6.4.1.2 In a hermeticpackage, where the motor iscooled by refrigerant, chilledwater or condenser water, themotor cooling load will beincluded in the measuredcondenser load, hence

Winput = electrical power inputto the compressor motor, Btu/h[kW]

C6.4.1.3 In a package usingan open-type compressor withprime mover and external geardrive:

Winput = qprime mover -qgear

where:

Winput = Power input to thecompressor shaft,Btu/h [kW]

qprime mover = Power delivered byprime mover, Btu/h[kW]

qgear = Friction loss inthe gear box, Btu/h[kW]

The value of qprime mover shall bedetermined from the power inputto prime mover using certifieddata from the prime movermanufacturer.

The value of qgear shall bedetermined from certified gearlosses provided by the gearmanufacturer.

C6.4.1.4 In a package usingan open-type compressor withdirect drive and the prime movernot furnished by themanufacturer:

Winput = power input to thecompressor shaft, Btu/h [kW]

For determination of Winput forturbine or engine operated

machines, the turbine or enginemanufacturer's certified powerinput/output data shall be used.

In the case of motor drive:

Winput = power measured atmotor terminals plus power toauxiliaries as in C.7.1.4.

C6.4.1.5 Percent HeatBalance. Heat balance, in %, isdefined as:

100x

q+q

q+q-W+q

hrccd

hrccdinputev

C4

For any test of a liquid cooledchiller to be acceptable, the heatbalance (%) shall be within theallowable tolerance calculatedper 5.6 for the applicableconditions.

C6.4.2 Concurrent RedundantVerification Test for Air-Cooled orEvaporatively- Cooled Condensers.

C6.4.2.1 CapacityCalculation Method. Calculatethe capacity of the cooler usingone set of instrumentation. Alsocalculate the capacity of thecooler using the redundant set ofinstrumentation. For a valid test,these two calculated values mustagree within the tolerancespecified in Section 5.6. Thetested capacity of the machineshall be the average of these twovalues.

C6.4.2.2 Power CalculationMethod. The power measured bythe two sets of instruments mustbe within 2% at all loads. Thetested power of the machine shallbe the average of the twomeasured powers.

C6.4.2.3 EfficiencyCalculation Method. Efficiencyshall be calculated using themeasured (averaged) values andmust comply within thetolerances of 5.6.


22

C7 Calculation of Results

C7.1 Capacity and Power.

C7.1.1 The capacity, tons, shall beobtained by the following equation:

C5

The capacity, Btu/h [kW], shall beobtained from the following equation:

qev = cmw (te - tl) C6

C7.1.2 Water-Cooled Heat ReclaimCondensers. If used, the Water-CooledHeat Reclaim Condenser capacity Btu/h[kW] shall be calculated using thefollowing equation.

ttmc=q elwhrc C7

C7.1.3 Air-Cooled Heat ReclaimCondensers If used, the Air-Cooled HeatReclaim Condenser capacity (Btu/h) shallbe calculated using the followingequation.

ttcfm08.1=q elhrchrc C8

where:

13.5

60x.2440=1.08

0.244 = Specific heat of moist air at70F and 50% rh (Btu/F lbdry air)

60 = min/hr13.5 = Specific volume of moist air at

70F db and 50% rh (ft3/lb dryair)

The capacity (kW) shall be calculatedusing the following equation.

4355 l ehrc hrcq = cfm t t C9

where:

36004355 = 1.021 x

0.844

1.021 = Specific heat of moist air at21.1C and 50% rh (kJ/kgK kg dry air)

3600 = sec/hr0.844 = Specific volume of moist air at

21.1C db and 50% rh (mt3/kgdry air)

C7.1.4 Power consumption shall bedetermined as follows:

C7.1.4.1 For motor drivencentrifugal and rotary screwcompressors where the motor issupplied by the manufacturer,the compressor power inputshall be measured as close aspractical to the compressormotor terminals. If a frequencyconversion device or motorstarter is furnished as part of thecompressor circuit, thecompressor power input shall bemeasured at the input terminalsof the frequency converter ormotor starter. For remotestarters or frequency converters,line losses shall be subtracted.If the Water-Chilling Packagebeing tested is not equippedwith the starter or frequencyconverter furnished for it, then astarter or frequency converter ofsimilar type shall be used forthe test.

C7.1.4.2 Power consumptionof auxiliaries shall be measuredduring normal operation of thepackage and included in totalpower consumption.

C7.1.4.3 For open-typecompressors, where the motorand/or gear set is not suppliedby the manufacturer, or forengine or turbine drives, thecompressor shaft input shall be

12,000

ltetwmc=Capacity


23

determined as stated in C6.4.1.3or C6.4.1.4 .

C7.1.4.4 For Air-Cooled orEvaporatively-CooledCondensers, the additionalCondenser fan and Condenserspray pump power consumptionshall be measured as close aspractical to the motors.

C7.1.4.5 Validity of Test.Calculate the heat balance foreach of the three test points(C3.1.2). All three heatbalances must be within thetolerance specified in 5.6. Thenaverage the data taken from thethree test points and calculatecapacity and power input per C7using averaged data forreporting purpose.

C8 Symbols and Subscripts. The symbols andsubscripts used are as follows:

Symbols:

A = Total heat transfer surface, ft2 [m2]for evaporator or Condenser

c = Specific heat of water at averagewater temperature, Btu/lb F[kJ/kg K]

cfm = Air flow rate, ft3/min [m3/s]e = Base of natural logarithmff = Fouling Factor Allowance

h · ft2 · ºF/Btu [m2 · ºC/ W]m = Mass flow rate, lb/h [kg/s]q = Capacity in Btu/h [kW]

R = Water temperature range, F [C]= Absolute value (twl- twe,), F [C]

S = Small temperature difference= Absolute value (ts-twl,), F [C]

t = Temperature, F [C]ts = Saturated vapor temperature for

single component or azeotroperefrigerants and for zeotropicrefrigerants it is the arithmeticaverage of the dew point andbubble point temperaturescorresponding to refrigerantpressure., F [C]

Subscripts:

a = Additional foulingc = Cleancd = Condensere = Enteringev = Evaporatorf = Fouled or foulinghrc = Heat reclaimi = Insidel = Leavingo = Outsides = Saturationsp = Specifiedw = Water


24

APPENDIX D. DERIVATION OF INTEGRATED PART LOADVALUE (IPLV) - NORMATIVE

D1 Purpose. This appendix is intended to show thederivation of the Integrated Part-Load Value (IPLV).

D2 Scope. This appendix is for equipment covered bythis standard. The IPLV equations and procedure areintended to provide a consistent method for calculating asingle number part-load performance figure of merit forWater-Chilling Packages. The equation was derived toprovide a representation of the average part-loadefficiency for a single chiller only. However, it is best touse a comprehensive analysis that reflects the actualweather data, building load characteristics, operationalhours, economizer capabilities and energy drawn byauxiliaries such as pumps and cooling towers, whencalculating the chiller and system efficiency. Thisbecomes increasingly important with multiple chillersystems because individual chillers operating withinmultiple chiller systems are more heavily loaded thansingle chillers within single chiller systems.

D3 Equation and Definition of Terms.

D3.1 The energy efficiency of a chiller iscommonly expressed in one of the three followingratios:

a. Coefficient of Performance, COPb. Energy Efficiency Ratio, EERc. Total Power Input per Capacity

kW/ton [kW/kW]

These three alternative ratios are related as follows:

COP = .293 EER EER = 3.413 COPkW/ton = 12/EER EER = 12/(kW/ton)kW/ton = 3.516/COP COP = 3.516/(kW/ton)

The following equation is used when an efficiencyis expressed as EER [Btu/(Wh)] or COP [W/W]:

D0.12+C0.45+B0.42+A0.01=IPLV D1a

where:

*A = EER or COP at 100% capacity*B = EER or COP at 75% capacity*C = EER or COP at 50% capacity*D = EER or COP at 25% capacity

The following equation is used when the efficiencyis expressed in Total Power Input per Capacity,kW/ton:

D1b

where:

*A = kW/ton at 100% capacity*B = kW/ton at 75% capacity*C = kW/ton at 50% capacity*D = kW/ton at 25% capacity

The IPLV or NPLV rating requires that the unitefficiency be determined at 100%, 75%, 50% and25% at the conditions as specified in Table 3. Ifthe unit, due to its capacity control logic can not beoperated at 75%, 50%, or 25% capacity then theunit can be operated at other load points and the75%, 50%, or 25% capacity efficiencies should bedetermined by plotting the efficiency versus the %load using straight line segments to connect theactual performance points. The 75%, 50%, or 25%load efficiencies can then be determined from thecurve. Extrapolation of data shall not be used. Anactual chiller capacity point equal to or less thanthe required rating point must be used to plot thedata. For example, if the minimum actual capacityis 33% then the curve can be used to determine the50% capacity point, but not the 25% capacitypoint.

If a unit cannot be unloaded to the 25%, 50%, or75% capacity point, then the unit should be run atthe minimum step of unloading at the condenserentering water or air temperature based on Table 3for the 25%, 50% or 75% capacity points asrequired. The efficiency shall then be determinedby using the following equation:

WC

Btu/h=EER

measuredD

measured

D2

where CD is a degradation factor to account forcycling of the compressor for capacities less thanthe minimum step of capacity. CD should becalculated using the following equation:

1.13+LF)(-0.13=CD D3

The load factor LF should be calculated using thefollowing equation:

_________________________* at operating conditions per Tables 1 and 3

D

0.12+

C

0.45+

B

0.42+

A

0.01

1=IPLV


25

capacity)unitLoad(Part

capacity)unitload(Full100

Load%

=LF

D4

where:

%Load is the standard rating point i.e. 75%,50% and 25%.

Part-Load unit capacity is the measured orcalculated unit capacity from which standardrating points are determined using the methodabove.

D3.2 Equation Constants. The constants 0.01,0.42, 0.45 and 0.12 are based on the weightedaverage of the most common building types, andoperating hours, using average USA weather data.To reduce the number of data points, the ASHRAEbased bin data was reduced to a design bin andthree bin groupings as illustrated in Figure D1.

D3.3 Equation Derivation. The ASHRAETemperature Bin Method was used to create fourseparate NPLV/IPLV formulas to represent thefollowing building operation categories:

Group 1 - 24 hrs/day, 7 days/wk, 0F andaboveGroup 2 - 24 hrs/day, 7 days/wk, 55F andaboveGroup 3 - 12 hrs/day, 5 days/wk, 0F andaboveGroup 4 - 12 hrs/day, 5 days/wk, 55F andabove

Figure D1. Ton-Hour Distribution Categories

The following assumptions were used:

a. Modified ASHRAE Temperature BinMethod for energy calculations wasused.

b. Weather data was a weighted averageof 29 cities across the U.S.A,specifically targeted because theyrepresented areas where 80% of all

chiller sales occurred over a 25 yearperiod (1967-1992).

c. Building types were a weightedaverage of all types (with chillerplants only) based on a DOE study ofbuildings in 1992 [DOE/EIA-0246(92)].

d. Operational hours were a weightedaverage of various operations (withchiller plants only) taken from theDOE study of 1992 and a BOMAstudy (1995 BEE Report).

e. A weighted average of buildings(with chiller plants only) with andwithout some form of economizer,based upon data from the DOE andBOMA reports, was included.

f. The bulk of the load profile used inthe last derivation of the equation wasagain used, which assumed that 38%of the buildings’ load was averageinternal load (average of occupied vs.unoccupied internal load). It varieslinearly with outdoor ambient andmean Condenser wet-bulb (MCWB)down to 50F DB, then flattens outbelow that to a minimum of 20%load.

g. Point A was predetermined to be thedesign point of 100% load and 85FECWT/95F EDB for IPLV/NPLV.Other points were determined bydistributional analysis of ton-hours,MCWB’s and EDBs. ECWTs werebased upon actual MCWBs plus an8F tower approach.

The individual equations thatrepresent each operational type werethen averaged in accordance withweightings obtained from the DOEand BOMA studies.

The load line was combined with theweather data hours (Figure D2) tocreate ton-hours (Figure D3) for thetemperature bin distributions. Seegraphs below:


26

Figure D2. Bin Groupings

A more detailed derivation of theGroup 1 equation is presented here toillustrate the method. Groups 2, 3,and 4 are done similarly, but notshown here. In the chart below, notethat the categories are distributed asfollows:

Figure D3. Group 1 Ton-Hour DistributionCategories

Point A = 1 bin for Design BinPoint B = 4 bins for Peak BinPoint C = 4 bins for Low BinPoint D = all bins below 55F for

Min Bin

See Table D1 for Air Cooled andTable D2 for water cooledcalculations. The result is averageweightings, ECWT’s (or EDB’s), and% Loads.

The next step would be to begin againwith Group 2 Ton Hour distributionas below. Note Group 2 is Group 1,but with 100% Economizer at 55F.

Figure D4. Group 2 Ton-Hour DistributionCategories

After creating similar tables as inTables D1 and D2 for Groups 2, 3,and 4, the resulting GroupIPLV/NPLV equations are in TableD3.

The next step is to determine the % ofeach group which exists in buildingswith central chiller plants, so that onefinal equation can be created from thefour. From the DOE and BOMAstudies, using goal seeking analysis, itwas determined that:

Group 1 - 24.0%Group 2 - 12.2%Group 3 - 32.3%Group 4 - 31.5%

This calculates to the following newequation:IPLV equation (kW/ton):

D5

D

0.124+

C

0.446+

B

0.416+

A

0.014

1=IPLV


27

A = kW/ton @ 100% Load and85F ECWT or 95F EDB

B = kW/ton @ 76.1% Load and75.6F ECWT or 82.1FEDB

C = kW/ton @ 50.9% Load and65.6F ECWT or 65.8FEDB

D = kW/ ton @ 32.2% Load and47.5F ECWT or 39.5FEDB

Rounding off and rationalizing:

A = kW/ton @ 100% Load and85F ECWT or 95F EDB

B = kW/ton @ 75% Load and75F ECWT or 80F EDB

C = kW/ton @ 50% Load and65F ECWT or 65F EDB

D = kW/ton @ 25% Load and65F ECWT or 55F EDB

After rounding off and applying therationale of where the manufacturers’and the current test facilitiescapabilities lie, the final equation D1bis shown in Section D3.1.

D

0.12+

C

0.45+

B

0.42+

A

0.01

1=IPLV


28

Ch

ille

r

Des

Bin

To

n-H

rs

37 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 37

0.9

%

95

.0

10

0%

A

C/S

DB

H

36

08

0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0

36

08

Pea

kB

in

To

n-H

rs

0

11

1

25

6

39

7

53

9

0 0 0 0 0 0 0 0 0 0 0 0 0 0 0

13

03

30

.9%

81

.8

75

.7%

B

DB

H

0

11

100

26

513

42

653

60

450

0 0 0 0 0 0 0 0 0 0 0 0 0 0 0

14

071

5

Lo

wB

in

To

n-H

rs

0 0 0 0 0

57

0

47

9

39

3

29

6

0 0 0 0 0 0 0 0 0 0 0

17

38

41

.3%

65

.4

50

.3%

C

DB

H

0 0 0 0 0

67

353

60

345

53

500

44

678

0 0 0 0 0 0 0 0 0 0 0

22

562

8

Min

Bin

To

n-H

rs

0 0 0 0 0 0 0 0 0 24

7

20

4

18

3

16

3

14

0

84

49

28

16 9 9

11

32

26

.9%

38

.6

31

.9%

D

DB

H

0 0 0 0 0 0 0 0 0

35

595

27

835

23

375

19

425

15

178

82

23

41

18

19

43

85

0

30

0

11

8

13

695

8

Co

oli

ng

Lo

ad%

10

0%

92

%

85

%

77

%

69

%

61

%

54

%

46

%

38

%

36

%

35

%

33

%

32

%

30

%

28

%

27

%

25

%

23

%

22

%

20

%

DB

HT

ota

l

Wei

gh

tin

g:

ED

BºF

:

Lo

ad:

To

tal

To

n-H

rs

37

11

1

25

6

39

7

53

9

57

0

47

9

39

3

29

6

24

7

20

4

18

3

16

3

14

0

84

49

28

16 9 9

42

10

DB

H

36

08

11

100

26

513

42

653

60

450

67

353

60

345

53

500

44

678

35

595

27

835

23

375

19

425

15

178

82

23

41

18

19

43

85

0

30

0

11

8

50

715

5

To

tal

Ho

urs

37

12

0

30

3

51

7

78

0

92

9

89

4

85

6

77

7

67

8

58

6

55

0

51

8

46

7

29

9

18

3

11

1

68

40

47

86

70

OA

DB

97

.5

92

.5

87

.5

82

.5

77

.5

72

.5

67

.5

62

.5

57

.5

52

.5

47

.5

42

.5

37

.5

32

.5

27

.5

22

.5

17

.5

12

.5

7.5

2.5

57

.9

Av

erag

eD

B(º

F)

97

.5

92

.5

87

.5

82

.5

77

.5

72

.5

67

.5

62

.5

57

.5

52

.5

47

.5

42

.5

37

.5

32

.5

27

.5

22

.5

17

.5

12

.5

7.5

2.5

57

.9

Ou

tsid

eT

emp

(ºF

)

95

-99

90

-94

85

-89

80

-84

75

-79

70

-74

65

-69

60

-64

55

-59

50

-54

45

-49

40

-44

35

-39

30

-34

25

-29

20

-24

15

-19

10

-14

05

-09

00

-04

To

tal

Table D1. Group 1 Air-Cooled IPLV Data and Calculation


29

Ch

ille

r

Des

Bin

To

n-H

rs

37 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 37

0.9

%

85

.0

10

0%

A

C/S

CW

H

29

60

0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0

29

60

Pea

kB

in

To

n-H

rs

0 11

1

25

6

39

7

53

9

0 0 0 0 0 0 0 0 0 0 0 0 0 0 0

13

03

30

.9%

81

.8

75

.7%

B

CW

H

0

94

80

23

331

39

292

57

720

0 0 0 0 0 0 0 0 0 0 0 0 0 0 0

12

982

3

Lo

wB

in

To

n-H

rs

0 0 0 0 0 57

0

47

9

39

3

29

6

0 0 0 0 0 0 0 0 0 0 0

17

38

41

.3%

65

.3

50

.3%

C

CW

H

0 0 0 0 0

65

959

59

898

53

928

45

843

0 0 0 0 0 0 0 0 0 0 0

22

562

8

Min

Bin

To

n-H

rs

0 0 0 0 0 0 0 0 0 24

7

20

4

18

3

16

3

14

0

84

49

28

16 9 9

11

32

26

.9%

47

.1

31

.9%

D

CW

H

0 0 00

00 0 0 0 0 0

37

290

30

472

26

950

23

310

19

147

11

960

73

20

44

40

27

20

16

00

18

80

16

708

9

Co

oli

ng

Lo

ad%

10

0%

92

%

85

%

77

%

69

%

61

%

54

%

46

%

38

%

36

%

35

%

33

%

32

%

30

%

28

%

27

%

25

%

23

%

22

%

20

%

CW

HT

ota

l

Wei

gh

tin

g

EC

WT

ºF

Lo

ad

To

tal

To

n-H

rs

37

11

1

25

6

39

7

53

9

57

0

47

9

39

3

29

6

24

7

20

4

18

3

16

3

14

0

84

49

28

16 9 9

42

10

CW

H

29

60

94

80

23

331

39

292

57

720

65

959

59

898

53

928

45

843

37

290

30

472

26

950

23

310

19

147

11

960

73

20

44

40

27

20

16

00

18

80

52

550

0

To

tal

Ho

urs

37

12

0

30

3

51

7

78

0

92

9

89

4

85

6

77

7

67

8

58

6

55

0

51

8

46

7

29

9

18

3

11

1

68

40

47

86

70

CW

H

80

79

77

76

74

71

67

63

59

55

52

49

45

41

40

40

40

40

40

40

60

.0

MC

WB

(sy

)

72

71

69

68

66

63

59

55

50

45

41

37

32

27

22

17

13 8 4 1

49

.3

Av

erag

eD

B(º

F)

97

.5

92

.5

87

.5

82

.5

77

.5

72

.5

67

.5

62

.5

57

.5

52

.5

47

.5

42

.5

37

.5

32

.5

27

.5

22

.5

17

.5

12

.5

7.5

2.5

57

.9

Ou

tsid

eT

emp

(ºF

)

95

-99

90

-94

85

-89

80

-84

75

-79

70

-74

65

-69

60

-64

55

-59

50

-54

45

-49

40

-44

35

-39

30

-34

25

-29

20

-24

15

-19

10

-14

05

-09

00

-04

To

tal

Table D2. Group 1 Water-Cooled IPLV Data and Calculation


30

Group 1 % Load ECWT EDB Weight Group 2 % Load ECWT EDB Weight

A 100.0% 85.0 ºF 95.0 ºF 0.95% A 100.0% 85.0 ºF 95.0 ºF 1.2%

B 75.7% 75.5 ºF 81.8 ºF 30.9% B 75.7% 75.5 ºF 81.8 ºF 42.3%

C 50.3% 65.3 ºF 65.4 ºF 41.3% C 50.3% 65.3 ºF 65.4 ºF 56.5%

D 31.9% 47.1 ºF 38.6 ºF 26.9% D N/A N/A N/A 0.0%

IPLV =

.269/D+.413/C+.309/B+.009/A

1 IPLV =

0.0/D+.565/C+.423/B+.012/A

1

Group 3 % Load ECWT EDB Weight Group 4 % Load ECWT EDB Weight

A 100.0% 85.0 ºF 95.0 ºF 1.5% A 100.0% 85.0 ºF 95.0 ºF 1.8%

B 75.7% 75.6 ºF 82.2 ºF 40.9% B 76.4% 75.6 ºF 82.2 ºF 50.1%

C 50.3% 65.8 ºF 66.0 ºF 39.2% C 51.3% 65.8 ºF 66.0 ºF 48.1%

D 31.9% 47.7 ºF 40.0 ºF 18.4% D N/A N/A N/A 0.0%

IPLV =

.184/D+.392/C+.409/B+.015/A

1 IPLV =

0.0/D+.481/C+.501/B+.018/A

1

Table D3. Group 1 - 4 IPLV Summary

ARI-550-590 Standar Untuk AC

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