test report #7 system drop-in tests of r134a … cupronickel condenser tubes, and alternative copper...

Air-Conditioning, Heating, and Refrigeration Institute (AHRI) Low-GWP Alternative Refrigerants Evaluation Program (Low-GWP AREP) TEST REPORT #7 System Drop-In Tests of R134a Alternative Refrigerants (ARM-42a, N-13a, N-13b, R-1234ze(E), and OpteonTM XP10) in a 230-RT Water-Cooled Water Chiller Ken Schultz Steve Kujak Trane / Ingersoll Rand 3600 Pammel Creek Rd La Crosse, WI 54601 January 25, 2013 This report has been made available to the public as part of the author company’s participation in the AHRI’s Low-GWP AREP.

List of Tested Refrigerants’ Compositions (Mass%)

ARM-42a R-134a/R-152a/R-1234yf (7/11/82) N-13a R-134a/R-1234yf/R-1234ze(E) (42/18/40) N-13b R-134a/R-1234ze(E) (42/58) R-1234ze(E) R-1234ze(E) (100) OpteonTM XP10 R-134a/R-1234yf (44/56)

LowGWPAREPR134aW/CScrewChillerTestSummary – FinalReportcreated:19November2012

lastedited:19November2012page2of16

TraneMP_Report#1_external_121119.docx Ken Schultz•ThermalSystemsGroup

INTRODUCTION

Thisreportdocumentstestsrunonanominal230‐tonwater‐cooledscrewcompressor‐basedwaterchillerinTrane’sLaCrosse,Wisconsin,laboratory.Therefrigerantstestedarelistedbelow:

name supplier order begin testing

end testing

number of runs

R134a (#1) (self) 1 16‐May‐2012 23‐May‐2012 38

XP10 DuPont 2 29‐May‐2012 11‐Jun‐2012 24

N‐13a Honeywell 3 13‐Jun‐2012 20‐Jun‐2012 34

N‐13b Honeywell 4 25‐Jun‐2012 29‐Jun‐2012 33

R1234ze(E) Honeywell 5 06‐Jul‐2012 13‐Jul‐2012 40

ARM‐42a Arkema 6 20‐Aug‐2012 11‐Oct‐2012 67

R134a (#2) (self) 7 15‐Oct‐2012 16‐Oct‐2012 13

R1234yf Honeywell 8 Dec‐2012 ?

D4Y Daikin Daikincouldnotsupplyenoughrefrigerantforthechiller.

TestswithR134awererepeatedattheendasacheck;performanceverycloselyduplicatedtheoriginalbaselinedataset.TestswithR1234yfwillbeconductedif/whenHoneywellcansupplythevolumeofrefrigerantneeded.DaikinwasunabletoprovidesufficientvolumeofD4Yforthetestchillerusedhere.

TESTSETUP

Thechillertestedhereisanominal230‐ton“RTWD”dual‐circuitwater‐cooledscrewcompressor‐basedwaterchiller.Thespecificunittestedisapre‐productionprototypebuiltfordesignverificationtestinginthelaboratory.Thechillerunderwentseveralmodificationsduringprevioustesting,includingachangetohighliftcompressors,cupronickelcondensertubes,andalternativecopperevaporatortubes.PhotosofthechillerareshowninFigure1.Thechillerconsistsoftwoindependentrefrigerantcircuits.Tominimizetheamountofrefrigerantneeded,testsherewererunwithonlyonecircuit.Thecircuitadjacenttothechilledandcoolingwaterconnectionswasused.Thesecondcircuitwaschargedwithnitrogenat5psigtominimizeheattransferbetweenthewaterpasses.Theevaporatorusesfallingfilmtechnologyinconjunctionwithafloodedpool.Thecondenserincorporatesaliquidrefrigerantsubcooler.Thecompressorrunsatfixedspeed(noAFD).Primaryinstrumentationincluded:

Chilledwaterloopo volumeflowrate(magneticflowmeter)o inletandoutlettemperatures(dualRTD’sateachlocation)o absolutepressurescollocatedwithtemperaturemeasurementso water‐sidepressuredrop

Coolingwaterloopo volumeflowrate(magneticflowmeter)o inletandoutlettemperature(dualRTD’sateachlocation)o absolutepressurescollocatedwithtemperaturemeasurementso water‐sidepressuredrop

CompressorpowerinputThecollocatedtemperatureandpressuremeasurementsareusedtocomputetheinletandoutletenthalpiesofthewater.Heattransferrateiscalculatedastheproductofthewatermassflowrateandthedifferencebetweentheinletandoutletenthalpies.Thecompressor‐basedEERiscalculatedastheratioofthechilledwaterheattransferratetothecompressorpowerinput.




Secondaryinstrumentationincludesvarioustemperatureandpressuremeasurementsalongtherefrigerantflowpath.Keymeasurementsincludethetemperatureandpressureatthecompressorsuctionanddischargealongwiththecondenserliquidleavingtemperatureandpressure.AlistofinstrumentationisincludedasAppendixA.

METHODOFTEST

ThemethodoftestisconsistentwithAppendixCofAHRIStandard550/590‐2011withoperatingconditionsgenerallyheldwithintightertolerances.Performanceisreportedhereasmeasured;noadjustmentsaremadeforfoulingallowance.Thecoolingcapacitiesreportedarecalculatedfromthemeasuredchilledwaterflowrateandthedifferencebetweentheenteringandleavingchilledwaterenthalpies.Theenthalpiesarecomputedfromthemeasuredwatertemperaturesandpressures(collocated).Therefore,thecapacitiesreportedherecorrespondtothe“grossrefrigeratingcapacity”definedinAHRIStandard550/590‐2011.ThermodynamicpropertiesofwaterarecomputedusingTrane’sinternalcode,whichisconsistentwiththe550/590equationstowellwithinexperimentalaccuracies.Thetestmatrixconsistedofthefollowingsteps:

1. Refrigerantchargesweepatbaselineoperating(boundary)conditionsof:–leavingchilledwatertemperature=44°F0.1°Fd(2s)–chilledwaterflowrate=550gpm2gpm–enteringcoolingwatertemperature=85°F0.1°Fd–coolingwaterflowrate=700gpm2gpmThechargeforfurthertestingwasselectedatmaximumEER(5lbmresolution)withconsiderationgiventotherefrigerantlevelinthecondenser/subcooler.

2. Loadlineat100%,90%,80%,70%,60%,minwith“baseline”flowrates:–leavingchilledwatertemperature=44°F0.1°Fd(2s)–chilledwaterflowrate=550gpm2gpm–enteringcoolingwatertemperature=85°F0.1°Fd–coolingwaterflowrate=700gpm2gpm

3. Loadlineat100%,90%,80%,70%,60%,minwith“standard”flowrates:–leavingchilledwatertemperature=44°F0.1°Fd(2s)–chilledwaterflowrate=2.4gpm/ton×tons@100%×2–enteringcoolingwatertemperature=85°F0.1°Fd–coolingwaterflowrate=3.0gpm/ton×tons@100%×2

4. Variationincoolingwaterenteringtemperaturewith–leavingchilledwatertemperature=44°F0.1°Fd(2s)–chilledwaterflowrate=510gpm2gpm–enteringcoolingwatertemperature=85°F0.1°Fd–coolingwaterflowrate=635gpm2gpm

Notethatthewaterflowrateswerebasedonfullchillercapacity(ie,asifbothcircuitswereactive).Runningthewaterflowratesbasedonthesinglecircuitcapacitywouldresultinverylowwatervelocitiesinthetubesandpoorwater‐sideheattransfercoefficients.Inhindsight,itmighthavebeenmoreappropriatetoelevatetheenteringcoolingwatertemperatureby5°FdorsotobemoreconsistentwithAHRI550‐590standardratingconditions.Intheend,consistentconditionswereusedthatprovideafaircomparisonamongthedifferentalternativerefrigerantstested.Figure2showstheenergybalanceclosureerrorsforallofthetestpointsrun.Energybalanceerrorsweregenerallylessthan1%.Thisdemonstratesthestabilityandaccuracyoftheprimarytestmeasurements.




alternativerefrigerantsarealllowerthanforR134a,exceptforthethirdARM‐42adataset.2TheXP10HTC’sarejustslightlylowerthanforR134a.Theshell‐sideHTC’sforR1234ze(E)wereroughly30%lowerthanforR134a.Thisappearscontrarytorecentlypublishedsingle‐tubepoolboilingdata.3TheUoEforR1234ze(E)isalsonegativelyimpactedbythereducedtubein‐sideHTCduetothereductioninchilledwaterflowratewhenoperatingwithreducedcapacityatthestandardflowrates.N‐13aandN‐13bhadverypoorevaporatorperformance.Thiscouldpossiblybeattributabletothe~1°Fdglideassociatedwiththesetwoblends.Visualobservationsindicatedthatthebundlewettingappearedtobesimilarforallrefrigerants;therewerenoobviousindicationsofunusualdry‐outorcarryoverforanyoftherefrigerants.Thereweresomevariationsinoilfoamingbehaviorinthepoolsection(eg,thebubblesizeswerelargerforR1234ze(E),indicativeofthehighervaporspecificvolume),buttheywereminoranddidnotappeartoimpactevaporatorperformance.ThebundleaverageheattransfercoefficientsforthecondenserrelativetoR134aareshowninFigure10.Relativelymildtomoderatereductionsincondensershell‐sideheatcoefficientswereobservedforR1234ze(E),XP10,N‐13a,andN13b.Curiously,theN‐13blends(with~1°Fdglide)appearedtohavesufferedagreaterdegradationinevaporatorperformancethancondenserperformance.AfterseeingverypoorcondenserheattransferperformanceduringtheinitialtestsetwithARM‐42a(#1),arefrigerantsamplewascollectedfromthechillercondenservaporspace,appearingtoindicateanon‐condensablesconcentrationof1.5%vol.4Therefrigerantchargewasreclaimedbackintotheoriginaltwocylindersandthecylindervaporspaceventeduntilthenon‐condensablesconcentrationswere0.96%voland0.78%vol.5ThechillerwasthenrechargedwithARM‐42aandthetestsetrepeated(#2).Condenserperformanceimprovedmarginally,butwasstillquitepoor.Thecondenservaporspacewasagainsampled,thistimewithanon‐condensablesconcentrationof0.9%vol.Therefrigerantwasagainreclaimedintothecylinders.Samplestakenfromcylindersshowedanon‐condensablesconcentrationof~1.5%vol.Thecylinderswereagainventeduntilthenon‐condensablesconcentrationswere0.5%voland0.7%vol.ThechillerwasthenrechargedwithARM‐42aandthetestsetrepeatedathirdtime(#3).Condenserperformanceagaindidnotchange.Arefrigerantsampleextractedfromthecondenservaporspaceshowedanon‐condensablesconcentrationofonly0.3%vol.Whenreclaimedbackintothecylinders,thenon‐condensablesconcentrationwasmeasuredtobeonly0.6%vol.Asnotedabove,curiouslyduringthethirdARM‐42atestset,theevaporatorheattransferperformanceincreasedsignificantly.Thereasonforthisisunknown.ArepeatofthebaselinewithR134a(Oct)followingtheARM‐42atestsproducedresultsveryconsistentwiththeinitialbaselinetestset(May).ThecomparisonsshownherearebasedontheoverallbetterperformanceofthethirdARM‐42adataset.Thesourceofthenon‐condensablesfoundintheARM‐42atestsisunknown.Weareconfidentinourlaboratoryprocedureswithrespecttochillerevacuationandcharging.AdditionalprecautionsweretakenduringpreparationandchargingforthethirdtestofARM‐42atoensurenointroductionofairduringtheprocess.Theisentropicefficiencyofthecompressorcanbedeterminedfromthemeasuredtemperaturesandpressuresatthecompressorsuctionanddischargealongwiththerefrigerantthermodynamicpropertiesdescriptionprovidedbytherefrigerantsuppliers.Theresultsobtainedhereforthefull‐loadcapacitypointsrunwithstandardwaterflowratesareshowninFigure11.Thecompressorperformedsimilarlyforallrefrigerants,mostrunningslightlybelowR134a(∆η~0..0.02).TheN‐13bpointinFigure11issomewhatofanoutlier;thepart‐loadpointsallfellatorbelowtherespectiveR134apoints.2Morebelow.ThefirsttwoARM‐42adatasetsproducedevaporatorHTC’sthatfellbetweenXP10andR1234ze.

3EvanRooyenandJRThome,“POOLBOILINGONENHANCEDBOILINGTUBESWITHR‐134a,R‐236faANDR‐1234ze”,ECI8thInternationalConferenceonBoilingandCondensationHeatTransfer,EcolePolytechniqueFédéraledeLausanne,3‐7June2012,Lausanne,Switzerland.

4Thenon‐condensablegaseselutedfromtheGCcolumnatthetimeindicativeofbeingair.

5Theconcentrationsarebelowthe1.5%volupperlimittypicalofmostrefrigerantslistedinAHRIStandard700.




considerationwillneedtobegiventodesignofthecondensercoilforair‐cooledchillerproductsusingR1234ze(E).AllofthealternatefluidssufferedtosomeextentwithregardtoheattransferperformancerelativetoR134a.ThepoorperformanceofARM‐42ainthecondenserremainspuzzlingatthispoint.Furtherstudyofbothevaporation/boilingandcondensingbehavioroftheserefrigerantsonenhancedtubesiswarranted.Theconsistencybetweencalculatedsaturationandmeasuredtemperatures,alongwithgeneralagreementamongthecompressoradiabaticefficienciesandsuctionvolumeflowrates,indicatesthattherefrigerantpropertiesdescriptionsprovidedarereasonablyaccurate.

NOMENCLATURE

BL “baseline”operatingconditionsasdescribedinMethodofTestsection

CAP Capacity

Chrg refrigerantcharge

COP CoefficientofPerformance;seeEER

EB Energybalanceclosureerror

EER EnergyEfficiencyRatio=coolingcapacitydividedbyelectricalpowerinputtothecompressor[Btu/W·hr]

°Fd temperaturedifferenceinFahrenheit

FC,FC’s “foulingchecks”;essentiallyrepeatpointstakenataspecificoperatingcondition

HTC heattransfercoefficient

hoC’, , shell‐sideheattransfercoefficientinthecondenserbundle

hoE, , shell‐sideheattransfercoefficientintheevaporatorbundle

Pmsrd measuredpressure

q"C averageheatfluxinthecondenser

q"E averageheatfluxintheevaporator

QChW, heattransferratecomputedfrommeasurementsofthechilledwater

QClW, heattransferratecomputedfrommeasurementsofthecoolingwater

Std “standard”operatingconditionsasdescribedinMethodofTestsection(inparticular,standardevaporatorchilledwaterflowis2.4gpm/maxtonandstandardcondensercoolingwaterflowis3.0gpm/maxton)

∆TappC,dTappCapproachtemperatureinthecondenser(condensersaturationleavingcoolingwatertemperature)

∆TappE,dTappEapproachtemperatureintheevaporator(leavingchilledwaterevaporatorsaturationtemperature)

∆Tsc refrigerantsubcoolingleavingthecondenser/subcooler(refrigerantsaturationtemperatureactualtemperature)

Tmsrd measuredtemperature

Tsat saturationtemperature

UoC, , overallheattransfercoefficientinthecondenserbundle

UoE, , overallheattransfercoefficientintheevaporatorbundle

Wcmpr, compressorpowerconsumption

x refrigerantqualityinthetwo‐phaseregion

ηCmpr adiabaticefficiencyofthecompressor

T&Pmeasurementstationsforcoolingandchilledwaterloops.

nottested

nottested

nottested

nottested

nottested

nottested

nottested

nottested

Appendix A – Instrumentation List

ID # ** Description Units Type Measurement Accuracy

1 EVAP WATER FLOW GPM SI: m³/h Rosemount Magnetic ± 0.5% of Rdg

2 EVAP Unit water delta Press psid SI: kPa∙diff Rosemount 1151 ± 0.054 PSID

3 Evap unit water press ‐ ent psia SI: kPa∙abs Sensotec DS – 250 psia ± 0.125 PSIA

4 Evap unit water press ‐ lvg psia SI: kPa∙abs Sensotec DS – 250 psia ± 0.125 PSIA

5 COND WATER FLOW GPM SI: m³/h Rosemount Magnetic ± 0.5% of Rdg

6 Cond Unit Water Delta Press psid SI: kPa∙diff Rosemount 1151 ± 0.054 PSID

7 Cond Unit Water Press ‐ ent psia SI: kPa∙abs Sensotec DS – 250 psia ± 0.125 PSIA

8 Cond Unit Water Press ‐ lvg psia SI: kPa∙abs Sensotec DS – 250 psia ± 0.125 PSIA

100 Evap Shell Press (1) ‐ Ckt #1 psia SI: kPa∙abs Sensotec DS – 250 psia ± 0.125 PSIA

105 Evap Shell Press (2) ‐ Ckt #1 psia SI: kPa∙abs Sensotec DS – 250 psia ± 0.125 PSIA

110 Comp Suct Refrig Press ‐ Ckt #1 psia SI: kPa∙abs Sensotec DS – 250 psia ± 0.125 PSIA

115 Comp Disch Refrig Press ‐ Ckt #1 psia SI: kPa∙abs Sensotec DS – 500 psia ± 0.25 PSIA

125 Cond Top Shell Press Loc 1 ‐ Ckt # 1 psia SI: kPa∙abs Sensotec DS – 500 psia ± 0.25 PSIA

126 Cond Top Shell Press Loc 2 ‐ Ckt # 1 psia SI: kPa∙abs Sensotec DS – 500 psia ± 0.25 PSIA

130 Lvg Subcooler Refrig Press ‐ Ckt 1 psia SI: kPa∙abs Sensotec DS – 500 psia ± 0.25 PSIA

137 Ent Evap Refrig Press Ckt #1 psia SI: kPa∙abs Sensotec DS – 250 psia ± 0.25 PSIA

215 Comp Disch Temp ‐ Ckt #1 °F SI: °C Type T TC ± 1.0 F

240 Ent Evap Refrig Temp Ckt #1 °F SI: °C Type T TC ± 1.0 F

250 Comp Suct Refrig Temp Ckt #1 °F SI: °C Type T TC ± 1.0 F

251 Line Lvg Oil Separator T Ckt #1 °F SI: °C Type T TC ± 1.0 F

330 Evap RI probe Temp ‐ Loc 1 ‐ Ckt 1 °F SI: °C Type T TC ± 1.0 F



400 ENT EVAP WATER TEMP LOC 1 °F SI: °C 100 Ω RTD ± 0.1 F

401 ENT EVAP WATER TEMP LOC 2 °F SI: °C 100 Ω RTD ± 0.1 F

402 LVG EVAP WATER TEMP LOC 1 °F SI: °C 100 Ω RTD ± 0.1 F

403 LVG EVAP WATER TEMP LOC 2 °F SI: °C 100 Ω RTD ± 0.1 F

405 ENT COND WATER TEMP LOC 1 °F SI: °C 100 Ω RTD ± 0.1 F

406 ENT COND WATER TEMP LOC 2 °F SI: °C 100 Ω RTD ± 0.1 F

407 LVG COND WATER TEMP LOC 1 °F SI: °C 100 Ω RTD ± 0.1 F

408 LVG COND WATER TEMP LOC 2 °F SI: °C 100 Ω RTD ± 0.1 F

410 Evap Sat RTD ‐ Ckt #1 °F SI: °C 100 Ω RTD ± 0.1 F

417 Lvg subcooler refrigerant RTD ‐ Ckt #1 °F SI: °C 100 Ω RTD ± 0.1 F

420 Compressor VOLTAGE AB ‐ Ckt # 1 V SI: V

421 Compressor VOLTAGE AC ‐ Ckt # 1 V SI: V

422 Compressor VOLTAGE CB ‐ Ckt # 1 V SI: V

423 Compressor CURRENT A ‐ Ckt # 1 A SI: A ~0.5% of Rdg w/ CTs

424 Compressor CURRENT B ‐ Ckt # 1 A SI: A ~0.5% of Rdg w/ CTs

425 Compressor CURRENT C ‐ Ckt # 1 A SI: A ~0.5% of Rdg w/ CTs

426 Compressor Power ‐ Ckt # 1 W SI: W ~0.5% of Rdg w/ CTs

427 Compressor Power ‐ Frequency ‐ Ckt # 1 Hz SI: Hz

428 Compressor Power ‐ Power Factor ‐ Ckt # 1 None SI: NONE

480 Evap RI probe ‐ loc 1 ‐ ckt 1 % SI: %



496 Leaving Oil Separator RI Probe ‐ ckt 1 % SI: %

500 BAROMETRIC PRESS FROM METROLOGY psia SI: kPa∙abs ± 0.0157 PSIA

600 Chiller : Liquid Level Setpoint in SI: mm N/A

601 Circuit 1 : Refrigerant Liquid Level in SI: mm N/A

602 Circuit 2 : Refrigerant Liquid Level in SI: mm N/A




AppendixB

DataPointsCollectedatFull‐LoadCapacityWhenRunningattheStandardOperatingConditions

(InsertthepagesfromTraneMP_Report#1_DataForms.pdffollowingthispageinthePDF.)

Appendix B

Data Points Collected at Standard Operating Conditions

Low GWP AREP SYSTEM DROP‐IN TEST DATA FORM page 1

Manufacturer: Trane

Basic Information

Alternative Refrigerant XP10 DuPont

Alternative Lubricant Type and ISO Viscosity POE – 68

Baseline Refrigerant R134a

Baseline Lubricant Type and ISO Viscosity POE – 68

Make and Model of System RTWD water‐cooled chiller (running first of two refrigerant circuits

Nominal Capacity and Type of System 230 nominal tons (preproduction prototype for lab verification)

Comparison Data Base Alt. SI Units Base Alt. IP Units Ratio

Mode (heating/cooling) cooling

Compressor Type screw compressor (high lift version)

Compressor Displacement m³/hr cfm

Nominal Motor Size kW hp

Motor Speed (60 Hz) Hz

Expansion Device Type electronic expansion valve

Lubricant Charge L gal

Refrigerant Charge 81.6 81.6 kg 180 180 lbm 1.000

Composition (at Cmpr Suct)

6.7 6.7 °C 43.98 44.00 °F 0.02

1928 1927 L/min 509.3 509.2 gpm 1.000

Flow rate (tons × 2) 5.2 5.2 L/min∙kW 2.41 2.41 gpm/ton 1.002

29.5 29.5 °C 85.0 85.1 °F 0.0

2409 2409 L/min 636 636 gpm 1.000


Capacity 371.9 371.2 kW 105.7 105.5 tons 0.998

Power to Compressor 86.0 89.6 kW 86.0 89.6 kW 1.043

COP or EER (compressor only) 4.33 4.14 [] 14.76 14.13 Btu/W∙hr 0.957

Refrigerant Mass Flow Rate 8,596 9,961 kg/hr 18,950 21,960 lbm/hr 1.159

Refrig Flow @ Cmpr Suction 518.2 514.3 m³/hr 305.0 302.7 cfm 0.992

Other System Changes

The unit tested has non‐standard evaporator tubes (alternate high performance design).

The unit tested has non‐standard condenser tubes (90/10 cupronickel).

Only one of two refrigerant circuits was run due to limited availability of some refrigerants.

System Data Base Alt. Ratio

Degradation Coefficient

Seasonal Energy Efficiency Ration – SEER

Heating Seasonal Performance Factor – HSPF

12 3.1

Chilled

Water

Leaving Temp

Flow rate

Cooling

Water

Entering Temp

Flow rate

08‐Nov‐2012

Appendix B



Type of System: RTWD wc Water Chiller Alternate Refrigerant: XP10

Water Side Data Base Alt. SI Units Base Alt. IP Units Ratio | Diff

Evaporator (shell & tube)

fluid

flow rate 1928.0 1927.4 L/hr 509 509 gpm 1.000

T entering 9.4 9.4 °C 48.9 48.9 °F 0.0°F

T leaving 6.7 6.7 °C 44.0 44.0 °F 0.0°F

pressure drop 121 114 kPa 17.5 16.5 psid 0.945

Condenser (shell & tube)

fluid

flow rate 2408.9 2408.5 L/hr 636 636 gpm 1.000

T entering 29.5 29.5 °C 85.0 85.1 °F 0.0°F

T leaving 32.2 32.3 °C 90.0 90.1 °F 0.1°F


Refrigerant Side

T (°C) P (kPa) T (°C) P (kPa) T (°F) P (psia) T (°F) P (psia)

Compressor (screw)

suction 3.9 338 3.7 367 39.0 49.0 38.7 53.2

discharge 51.2 943 47.5 1007 124.2 136.8 117.4 146.0

dchrg SH | Pratio 14.0 9.5 25.2 2.79 17.15 2.75

Condenser (shell & tube w/integral subcooler)

inlet/shell 51.2 943 47.5 1,007 124.2 136.8 117.4 146.0

shell dewpoint 36.4 37.0 97.6 98.6

shell bubblept 36.4 37.0 97.6 98.6

subcooler outlet 32.5 911 32.5 964 90.5 132.1 90.5 139.8

subcooling (local) 3.5 3.8 6.2 6.8

Expansion Device (EXV)

inlet 32.5 911 32.5 964 90.5 132.1 90.5 139.8


inlet/shell 4.3 341 4.2 370 39.7 49.5 39.5 53.7

outlet/shell 4.3 341 4.2 370 39.7 49.5 39.5 53.7

Refrigerant Side Base Alt. SI Units Base Alt. IP Units Ratio

suction line pressure drop 3.2 3.7 kPa 0.46 0.53 psid 1.16

discharge line pressure drop 20 25 kPa 2.90 3.59 psid 1.24

08‐Nov‐2012

water

water

Base Alt. Base Alt.

Appendix B



Manufacturer: Trane

Basic Information

Alternative Refrigerant N‐13a Honeywell
















6.7 6.6 °C 43.98 43.93 °F ‐0.06

1928 1708 L/min 509.3 451.3 gpm 0.886


29.5 29.5 °C 85.0 85.0 °F 0.0

2409 2138 L/min 636 565 gpm 0.887


Capacity 371.9 329.1 kW 105.7 93.6 tons 0.885













12 3.1

Chilled

Water

Leaving Temp

Flow rate

Cooling

Water

Entering Temp

Flow rate

08‐Nov‐2012

Appendix B



Type of System: RTWD wc Water Chiller Alternate Refrigerant: N‐13a



fluid

flow rate 1928.0 1708.3 L/hr 509 451 gpm 0.886

T entering 9.4 9.4 °C 48.9 48.8 °F ‐0.1°F

T leaving 6.7 6.6 °C 44.0 43.9 °F ‐0.1°F



fluid

flow rate 2408.9 2137.7 L/hr 636 565 gpm 0.887

T entering 29.5 29.5 °C 85.0 85.0 °F 0.0°F

T leaving 32.2 32.2 °C 90.0 90.0 °F 0.0°F


Refrigerant Side


Compressor (screw)

suction 3.9 338 3.3 311 39.0 49.0 38.0 45.1

discharge 51.2 943 48.2 893 124.2 136.8 118.7 129.5

dchrg SH | Pratio 14.0 10.7 25.2 2.79 19.18 2.87


inlet/shell 51.2 943 48.2 893 124.2 136.8 118.7 129.5

shell dewpoint 36.4 36.7 97.6 98.1

shell bubblept 36.4 36.1 97.6 97.0




inlet 32.5 911 32.6 861 90.5 132.1 90.8 124.9


inlet/shell 4.3 341 2.9 314 39.7 49.5 37.2 45.5

outlet/shell 4.3 341 3.5 314 39.7 49.5 38.2 45.5




08‐Nov‐2012

water

water

Base Alt. Base Alt.

Appendix B



Manufacturer: Trane

Basic Information

Alternative Refrigerant N‐13b Honeywell
















6.7 6.7 °C 43.98 43.98 °F 0.00

1928 1636 L/min 509.3 432.3 gpm 0.849


29.5 29.5 °C 85.0 85.1 °F 0.1

2409 2047 L/min 636 541 gpm 0.850


Capacity 371.9 317.2 kW 105.7 90.2 tons 0.853













12 3.1

Chilled

Water

Leaving Temp

Flow rate

Cooling

Water

Entering Temp

Flow rate

08‐Nov‐2012

Appendix B



Type of System: RTWD wc Water Chiller Alternate Refrigerant: N‐13b



fluid

flow rate 1928.0 1636.2 L/hr 509 432 gpm 0.849

T entering 9.4 9.4 °C 48.9 48.9 °F 0.0°F

T leaving 6.7 6.7 °C 44.0 44.0 °F 0.0°F



fluid

flow rate 2408.9 2046.9 L/hr 636 541 gpm 0.850

T entering 29.5 29.5 °C 85.0 85.1 °F 0.1°F

T leaving 32.2 32.3 °C 90.0 90.1 °F 0.1°F


Refrigerant Side


Compressor (screw)

suction 3.9 338 3.6 290 39.0 49.0 38.5 42.0

discharge 51.2 943 48.0 836 124.2 136.8 118.4 121.2

dchrg SH | Pratio 14.0 10.4 25.2 2.79 18.75 2.89


inlet/shell 51.2 943 48.0 836 124.2 136.8 118.4 121.2

shell dewpoint 36.4 36.7 97.6 98.1

shell bubblept 36.4 36.1 97.6 96.9




inlet 32.5 911 32.1 806 90.5 132.1 89.7 116.9


inlet/shell 4.3 341 3.3 292 39.7 49.5 37.9 42.4

outlet/shell 4.3 341 3.8 292 39.7 49.5 38.8 42.4




08‐Nov‐2012

water

water

Base Alt. Base Alt.

Appendix B



Manufacturer: Trane

Basic Information

Alternative Refrigerant R1234ze Honeywell
















6.7 6.6 °C 43.98 43.96 °F ‐0.02

1928 1417 L/min 509.3 374.2 gpm 0.735


29.5 29.5 °C 85.0 85.0 °F 0.0

2409 1774 L/min 636 469 gpm 0.736


Capacity 371.9 277.4 kW 105.7 78.9 tons 0.746













12 3.1

Chilled

Water

Leaving Temp

Flow rate

Cooling

Water

Entering Temp

Flow rate

08‐Nov‐2012

Appendix B



Type of System: RTWD wc Water Chiller Alternate Refrigerant: R1234ze



fluid

flow rate 1928.0 1416.6 L/hr 509 374 gpm 0.735

T entering 9.4 9.4 °C 48.9 49.0 °F 0.1°F

T leaving 6.7 6.6 °C 44.0 44.0 °F 0.0°F



fluid

flow rate 2408.9 1773.7 L/hr 636 469 gpm 0.736

T entering 29.5 29.5 °C 85.0 85.0 °F 0.0°F

T leaving 32.2 32.3 °C 90.0 90.1 °F 0.0°F


Refrigerant Side


Compressor (screw)

suction 3.9 338 4.4 251 39.0 49.0 39.9 36.4

discharge 51.2 943 44.8 694 124.2 136.8 112.7 100.6

dchrg SH | Pratio 14.0 8.5 25.2 2.79 15.24 2.77


inlet/shell 51.2 943 44.8 694 124.2 136.8 112.7 100.6

shell dewpoint 36.4 35.6 97.6 96.1

shell bubblept 36.4 35.6 97.6 96.1




inlet 32.5 911 32.4 671 90.5 132.1 90.3 97.3


inlet/shell 4.3 341 4.4 254 39.7 49.5 39.9 36.8

outlet/shell 4.3 341 4.4 254 39.7 49.5 39.9 36.8




08‐Nov‐2012

water

water

Base Alt. Base Alt.

Appendix B



Manufacturer: Trane

Basic Information

Alternative Refrigerant ARM‐42a Arkema
















6.7 6.7 °C 43.98 43.99 °F 0.01

1928 1856 L/min 509.3 490.4 gpm 0.963


29.5 29.5 °C 85.0 85.0 °F 0.0

2409 2319 L/min 636 613 gpm 0.963


Capacity 371.9 367.9 kW 105.7 104.6 tons 0.989













12 3.1

Chilled

Water

Leaving Temp

Flow rate

Cooling

Water

Entering Temp

Flow rate

08‐Nov‐2012

Appendix B



Type of System: RTWD wc Water Chiller Alternate Refrigerant: ARM‐42a



fluid

flow rate 1928.0 1856.3 L/hr 509 490 gpm 0.963

T entering 9.4 9.5 °C 48.9 49.0 °F 0.1°F

T leaving 6.7 6.7 °C 44.0 44.0 °F 0.0°F



fluid

flow rate 2408.9 2318.9 L/hr 636 613 gpm 0.963

T entering 29.5 29.5 °C 85.0 85.0 °F 0.0°F

T leaving 32.2 32.3 °C 90.0 90.2 °F 0.2°F


Refrigerant Side


Compressor (screw)

suction 3.9 338 4.1 368 39.0 49.0 39.4 53.4

discharge 51.2 943 46.5 989 124.2 136.8 115.7 143.4

dchrg SH | Pratio 14.0 7.7 25.2 2.79 13.92 2.69


inlet/shell 51.2 943 46.5 989 124.2 136.8 115.7 143.4

shell dewpoint 36.4 37.9 97.6 100.2

shell bubblept 36.4 37.8 97.6 100.1




inlet 32.5 911 32.5 948 90.5 132.1 90.4 137.5


inlet/shell 4.3 341 4.5 372 39.7 49.5 40.1 53.9

outlet/shell 4.3 341 4.5 372 39.7 49.5 40.2 53.9




08‐Nov‐2012

water

water

Base Alt. Base Alt.

test report #7 system drop-in tests of r134a … cupronickel condenser tubes, and alternative copper...

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