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, N13a, 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)
Low	GWP	AREP	R134a	W/C	Screw	Chiller	Test	Summary	 –	 Final	Report		

created:		19	November	2012	

last	edited:		19	November	2012	

page	2	of	16	

TraneMP_Report#1_external_121119.docx 

Ken Schultz	•	Thermal	Systems	Group	

INTRODUCTION

This	report	documents	tests	run	on	a	nominal	230‐ton	water‐cooled	screw	compressor‐based	water	chiller	in	

Trane’s	La	Crosse,	Wisconsin,	laboratory.		The	refrigerants	tested	are	listed	below:	

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 Daikin	could	not	supply	enough	refrigerant	for	the	chiller.	

Tests	with	R134a	were	repeated	at	the	end	as	a	check;	performance	very	closely	duplicated	the	original	baseline	

data	set.		Tests	with	R1234yf	will	be	conducted	if/when	Honeywell	can	supply	the	volume	of	refrigerant	needed.		

Daikin	was	unable	to	provide	sufficient	volume	of	D4Y	for	the	test	chiller	used	here.	

TEST SETUP

The	chiller	tested	here	is	a	nominal	230‐ton	“RTWD”	dual‐circuit	water‐cooled	screw	compressor‐based	water	

chiller.		The	specific	unit	tested	is	a	pre‐production	prototype	built	for	design	verification	testing	in	the	

laboratory.		The	chiller	underwent	several	modifications	during	previous	testing,	including	a	change	to	high	lift	

compressors,	cupronickel	condenser	tubes,	and	alternative	copper	evaporator	tubes.	

Photos	of	the	chiller	are	shown	in	Figure	1.		The	chiller	consists	of	two	independent	refrigerant	circuits.		To	

minimize	the	amount	of	refrigerant	needed,	tests	here	were	run	with	only	one	circuit.		The	circuit	adjacent	to	the	

chilled	and	cooling	water	connections	was	used.		The	second	circuit	was	charged	with	nitrogen	at	5	psig	to	

minimize	heat	transfer	between	the	water	passes.	

The	evaporator	uses	falling	film	technology	in	conjunction	with	a	flooded	pool.		The	condenser	incorporates	a	

liquid	refrigerant	subcooler.		The	compressor	runs	at	fixed	speed	(no	AFD).	

Primary	instrumentation	included:	

 Chilled	water	loop	

o volume	flow	rate	(magnetic	flow	meter)	

o inlet	and	outlet	temperatures	(dual	RTD’s	at	each	location)	

o absolute	pressures	collocated	with	temperature	measurements	

o water‐side	pressure	drop	

 Cooling	water	loop	

o volume	flow	rate	(magnetic	flow	meter)	

o inlet	and	outlet	temperature	(dual	RTD’s	at	each	location)	

o absolute	pressures	collocated	with	temperature	measurements	

o water‐side	pressure	drop	

 Compressor	power	input	

The	collocated	temperature	and	pressure	measurements	are	used	to	compute	the	inlet	and	outlet	enthalpies	of	

the	water.		Heat	transfer	rate	is	calculated	as	the	product	of	the	water	mass	flow	rate	and	the	difference	between	

the	inlet	and	outlet	enthalpies.		The	compressor‐based	EER	is	calculated	as	the	ratio	of	the	chilled	water	heat	

transfer	rate	to	the	compressor	power	input.	
Low	GWP	AREP	R134a	W/C	Screw	Chiller	Test	Summary	 –	 Final	Report		

created:		19	November	2012	

last	edited:		19	November	2012	

page	3	of	16	

TraneMP_Report#1_external_121119.docx 

Ken Schultz	•	Thermal	Systems	Group	

Secondary	instrumentation	includes	various	temperature	and	pressure	measurements	along	the	refrigerant	flow	

path.		Key	measurements	include	the	temperature	and	pressure	at	the	compressor	suction	and	discharge	along	

with	the	condenser	liquid	leaving	temperature	and	pressure.		A	list	of	instrumentation	is	included	as	Appendix	A.	

METHOD OF TEST

The	method	of	test	is	consistent	with	Appendix	C	of	AHRI	Standard	550/590‐2011	with	operating	conditions	

generally	held	within	tighter	tolerances.		Performance	is	reported	here	as	measured;	no	adjustments	are	made	

for	fouling	allowance.		The	cooling	capacities	reported	are	calculated	from	the	measured	chilled	water	flow	rate	

and	the	difference	between	the	entering	and	leaving	chilled	water	enthalpies.		The	enthalpies	are	computed	from	

the	measured	water	temperatures	and	pressures	(collocated).		Therefore,	the	capacities	reported	here	

correspond	to	the	“gross	refrigerating	capacity”	defined	in	AHRI	Standard	550/590‐2011.		Thermodynamic	

properties	of	water	are	computed	using	Trane’s	internal	code,	which	is	consistent	with	the	550/590	equations	to	

well	within	experimental	accuracies.	

The	test	matrix	consisted	of	the	following	steps:	

1. Refrigerant	charge	sweep	at	baseline	operating	(boundary)	conditions	of:	

–		leaving	chilled	water	temperature	=	44°F	0.1°Fd	(2s)	

–		chilled	water	flow	rate	=	550	gpm	2	gpm	

–		entering	cooling	water	temperature	=	85°F	0.1°Fd	

–		cooling	water	flow	rate	=	700	gpm	2	gpm	

The	charge	for	further	testing	was	selected	at	maximum	EER	(5	lbm	resolution)	with	consideration	

given	to	the	refrigerant	level	in	the	condenser/subcooler.	

2. Load	line	at	100%,	90%,	80%,	70%,	60%,	min	with	“baseline”	flow	rates:	

–		leaving	chilled	water	temperature	=	44°F	0.1°Fd	(2s)	

–		chilled	water	flow	rate	=	550	gpm	2	gpm	

–		entering	cooling	water	temperature	=	85°F	0.1°Fd	

–		cooling	water	flow	rate	=	700	gpm	2	gpm	

3. Load	line	at	100%,	90%,	80%,	70%,	60%,	min	with	“standard”	flow	rates:	

–		leaving	chilled	water	temperature	=	44°F	0.1°Fd	(2s)	

–		chilled	water	flow	rate	=2.4	gpm/ton	×	tons@100%	×	2	

–		entering	cooling	water	temperature	=	85°F	0.1°Fd	

–		cooling	water	flow	rate	=	3.0	gpm/ton	×	tons@100%	×	2	

4. Variation	in	cooling	water	entering	temperature	with		

–		leaving	chilled	water	temperature	=	44°F	0.1°Fd	(2s)	

–		chilled	water	flow	rate	=	510	gpm	2	gpm	

–		entering	cooling	water	temperature	=	85°F	0.1°Fd	

–		cooling	water	flow	rate	=	635	gpm	2	gpm	

Note	that	the	water	flow	rates	were	based	on	full	chiller	capacity	(ie,	as	if	both	circuits	were	active).		Running	the	

water	flow	rates	based	on	the	single	circuit	capacity	would	result	in	very	low	water	velocities	in	the	tubes	and	

poor	water‐side	heat	transfer	coefficients.		In	hindsight,	it	might	have	been	more	appropriate	to	elevate	the	

entering	cooling	water	temperature	by	5°Fd	or	so	to	be	more	consistent	with	AHRI	550‐590	standard	rating	

conditions.		In	the	end,	consistent	conditions	were	used	that	provide	a	fair	comparison	among	the	different	

alternative	refrigerants	tested.	

Figure	2	shows	the	energy	balance	closure	errors	for	all	of	the	test	points	run.		Energy	balance	errors	were	

generally	less	than	1%.		This	demonstrates	the	stability	and	accuracy	of	the	primary	test	measurements.	

Low	GWP	AREP	R134a	W/C	Screw	Chiller	Test	Summary	 –	 Final	Report		

created:		19	November	2012	

last	edited:		19	November	2012	

page	5	of	16	

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Ken Schultz	•	Thermal	Systems	Group	

alternative	refrigerants	are	all	lower	than	for	R134a,	except	for	the	third	ARM‐42a	data	set.2		The	XP10	HTC’s	are	

just	slightly	lower	than	for	R134a.		The	shell‐side	HTC’s	for	R1234ze(E)	were	roughly	30%	lower	than	for	R134a.		

This	appears	contrary	to	recently	published	single‐tube	pool	boiling	data.3		The	UoE	for	R1234ze(E)	is	also	

negatively	impacted	by	the	reduced	tube	in‐side	HTC	due	to	the	reduction	in	chilled	water	flow	rate	when	

operating	with	reduced	capacity	at	the	standard	flow	rates.		N‐13a	and	N‐13b	had	very	poor	evaporator	

performance.		This	could	possibly	be	attributable	to	the	~1°Fd	glide	associated	with	these	two	blends.			

Visual	observations	indicated	that	the	bundle	wetting	appeared	to	be	similar	for	all	refrigerants;	there	were	no	

obvious	indications	of	unusual	dry‐out	or	carryover	for	any	of	the	refrigerants.		There	were	some	variations	in	oil	

foaming	behavior	in	the	pool	section	(eg,	the	bubble	sizes	were	larger	for	R1234ze(E),	indicative	of	the	higher	

vapor	specific	volume),	but	they	were	minor	and	did	not	appear	to	impact	evaporator	performance.	

The	bundle	average	heat	transfer	coefficients	for	the	condenser	relative	to	R134a	are	shown	in	Figure	10.		

Relatively	mild	to	moderate	reductions	in	condenser	shell‐side	heat	coefficients	were	observed	for	R1234ze(E),	

XP10,	N‐13a,	and	N13b.		Curiously,	the	N‐13	blends	(with	~1°Fd	glide)	appeared	to	have	suffered	a	greater	

degradation	in	evaporator	performance	than	condenser	performance.	

After	seeing	very	poor	condenser	heat	transfer	performance	during	the	initial	test	set	with	ARM‐42a	(#1),	a	

refrigerant	sample	was	collected	from	the	chiller	condenser	vapor	space,	appearing	to	indicate	a	non‐

condensables	concentration	of	1.5%vol.4		The	refrigerant	charge	was	reclaimed	back	into	the	original	two	

cylinders	and	the	cylinder	vapor	space	vented	until	the	non‐condensables	concentrations	were	0.96%	vol	and	

0.78%vol.5		The	chiller	was	then	recharged	with	ARM‐42a	and	the	test	set	repeated	(#2).		Condenser	

performance	improved	marginally,	but	was	still	quite	poor.		The	condenser	vapor	space	was	again	sampled,	this	

time	with	a	non‐condensables	concentration	of	0.9%vol.			

The	refrigerant	was	again	reclaimed	into	the	cylinders.		Samples	taken	from	cylinders	showed	a	non‐

condensables	concentration	of	~1.5%vol.		The	cylinders	were	again	vented	until	the	non‐condensables	

concentrations	were	0.5%vol	and	0.7%vol.		The	chiller	was	then	recharged	with	ARM‐42a	and	the	test	set	

repeated	a	third	time	(#3).		Condenser	performance	again	did	not	change.		A	refrigerant	sample	extracted	from	

the	condenser	vapor	space	showed	a	non‐condensables	concentration	of	only	0.3%vol.		When	reclaimed	back	

into	the	cylinders,	the	non‐condensables	concentration	was	measured	to	be	only	0.6%vol.	

As	noted	above,	curiously	during	the	third	ARM‐42a	test	set,	the	evaporator	heat	transfer	performance	increased	

significantly.		The	reason	for	this	is	unknown.		A	repeat	of	the	baseline	with	R134a	(Oct)	following	the	ARM‐42a	

tests	produced	results	very	consistent	with	the	initial	baseline	test	set	(May).		The	comparisons	shown	here	are	

based	on	the	overall	better	performance	of	the	third	ARM‐42a	data	set.	

The	source	of	the	non‐condensables	found	in	the	ARM‐42a	tests	is	unknown.		We	are	confident	in	our	laboratory	

procedures	with	respect	to	chiller	evacuation	and	charging.		Additional	precautions	were	taken	during	

preparation	and	charging	for	the	third	test	of	ARM‐42a	to	ensure	no	introduction	of	air	during	the	process.	

The	isentropic	efficiency	of	the	compressor	can	be	determined	from	the	measured	temperatures	and	pressures	

at	the	compressor	suction	and	discharge	along	with	the	refrigerant	thermodynamic	properties	description	

provided	by	the	refrigerant	suppliers.		The	results	obtained	here	for	the	full‐load	capacity	points	run	with	

standard	water	flow	rates	are	shown	in	Figure	11.		The	compressor	performed	similarly	for	all	refrigerants,	most	

running	slightly	below	R134a	(∆η~0..0.02).		The	N‐13b	point	in	Figure	11	is	somewhat	of	an	outlier;	the	part‐

load	points	all	fell	at	or	below	the	respective	R134a	points.	

																																																																		 2	More	below.		The	first	two	ARM‐42a	data	sets	produced	evaporator	HTC’s	that	fell	between	XP10	and	R1234ze.	

3	E	van	Rooyen	and	JR	Thome,	“POOL	BOILING	ON	ENHANCED	BOILING	TUBES	WITH	R‐134a,	R‐236fa	AND	

R‐1234ze”,	ECI	8th	International	Conference	on	Boiling	and	Condensation	Heat	Transfer,	Ecole	Polytechnique	

Fédérale	de	Lausanne,	3‐7	June	2012,	Lausanne,	Switzerland.	

4	The	non‐condensable	gases	eluted	from	the	GC	column	at	the	time	indicative	of	being	air.	

5	The	concentrations	are	below	the	1.5%vol	upper	limit	typical	of	most	refrigerants	listed	in	AHRI	Standard	700.	

Low	GWP	AREP	R134a	W/C	Screw	Chiller	Test	Summary	 –	 Final	Report		

created:		19	November	2012	

last	edited:		19	November	2012	

page	7	of	16	

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Ken Schultz	•	Thermal	Systems	Group	

consideration	will	need	to	be	given	to	design	of	the	condenser	coil	for	air‐cooled	chiller	products	using	

R1234ze(E).	

All	of	the	alternate	fluids	suffered	to	some	extent	with	regard	to	heat	transfer	performance	relative	to	R134a.		

The	poor	performance	of	ARM‐42a	in	the	condenser	remains	puzzling	at	this	point.	Further	study	of	both	

evaporation/boiling	and	condensing	behavior	of	these	refrigerants	on	enhanced	tubes	is	warranted.	

The	consistency	between	calculated	saturation	and	measured	temperatures,	along	with	general	agreement	

among	the	compressor	adiabatic	efficiencies	and	suction	volume	flow	rates,	indicates	that	the	refrigerant	

properties	descriptions	provided	are	reasonably	accurate.	

NOMENCLATURE

BL	 “baseline”	operating	conditions	as	

described	in	Method	of	Test	section	

CAP	 Capacity			

Chrg	 refrigerant	charge			

COP	 Coefficient	of	Performance;	see	EER			

EB	 Energy	balance	closure	error	

EER	 Energy	Efficiency	Ratio	=	cooling	

capacity	divided	by	electrical	power	

input	to	the	compressor	[Btu/W·hr]	

°Fd	 temperature	difference	in	Fahrenheit	

FC,	FC’s	 “fouling	checks”;	essentially	repeat	

points	taken	at	a	specific	operating	

condition	

HTC	 heat	transfer	coefficient	

hoC’,	݄௢,஼

ᇱ 	 shell‐side	heat	transfer	coefficient	in	

the	condenser	bundle	

hoE,	݄௢,ா	 shell‐side	heat	transfer	coefficient	in	

the	evaporator	bundle	

Pmsrd	 measured	pressure	

q"C	 average	heat	flux	in	the	condenser		

q"E	 average	heat	flux	in	the	evaporator		

QChW,	ܳሶ

஼௛ௐ	heat	transfer	rate	computed	from	

measurements	of	the	chilled	water	

QClW,	ܳሶ

஼௟ௐ	 heat	transfer	rate	computed	from	

measurements	of	the	cooling	water	

Std	 “standard”	operating	conditions	as	

described	in	Method	of	Test	section	

(in	particular,	standard	evaporator	

chilled	water	flow	is	2.4	gpm/max	ton	

and	standard	condenser	cooling	water	

flow	is	3.0	gpm/max	ton)	

∆TappC,	dTappC			approach	temperature	in	the	

condenser	(condenser	saturation		

leaving	cooling	water	temperature)	

∆TappE,	dTappE			approach	temperature	in	the	

evaporator	(leaving	chilled	water	

evaporator	saturation	temperature)	

∆Tsc	 refrigerant	subcooling	leaving	the	

condenser/subcooler	(refrigerant	

saturation	temperature		actual	

temperature)	

Tmsrd	 measured	temperature	

Tsat	 saturation	temperature	

UoC,	ܷ௢,஼	 overall	heat	transfer	coefficient	in	the	

condenser	bundle	

UoE,	ܷ௢,ா	 overall	heat	transfer	coefficient	in	the	

evaporator	bundle	

Wcmpr,	ܹሶ

௖௠௣௥			compressor	power	consumption	

x	 refrigerant	quality	in	the	two‐phase	

region	

ηCmpr	 adiabatic	efficiency	of	the	compressor	
T	&	P	measurement	

stations	for	cooling	and	

chilled	water	loops.	

not	tested	 not	tested	
not	tested	 not	tested	 not	tested	 not	tested	
not	tested	 not	tested	 not	tested	 not	tested	
not	tested	 not	tested	

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

331 Evap RI probe Temp ‐ Loc 2 ‐ Ckt 1 °F  SI: °C Type T TC ± 1.0 F

332 Evap RI probe Temp ‐ Loc 3 ‐ 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: %

481 Evap RI probe ‐ loc 2 ‐ ckt 1 %  SI: %

482 Evap RI probe ‐ loc 3 ‐ 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
Low	GWP	AREP	R134a	W/C	Screw	Chiller	Test	Summary	 –	 Final	Report		

created:		19	November	2012	

last	edited:		19	November	2012	

page	16	of	16	

TraneMP_Report#1_external_121119.docx 

Ken Schultz	•	Thermal	Systems	Group	

Appendix B

Data Points Collected at Full‐Load Capacity

When Running at the Standard Operating Conditions

(Insert	the	pages	from		

TraneMP_Report#1_DataForms.pdf	

following	this	page	in	the	PDF.)	
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

Flow rate (tons × 2) 6.5 6.5 L/min∙kW 3.01 3.01 gpm/ton 1.002

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

Data Points Collected at Standard Operating Conditions

Low GWP AREP SYSTEM DROP‐IN TEST DATA FORM page 2

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

pressure drop 140 136 kPa 20.3 19.7 psid 0.969

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

Evaporator (shell & tube)

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

Data Points Collected at Standard Operating Conditions

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

Manufacturer: Trane

Basic Information

Alternative Refrigerant N‐13a Honeywell

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 79.4 kg 180 175 lbm 0.972

Composition (at Cmpr Suct)

6.7 6.6 °C 43.98 43.93 °F ‐0.06

1928 1708 L/min 509.3 451.3 gpm 0.886

Flow rate (tons × 2) 5.2 5.2 L/min∙kW 2.41 2.41 gpm/ton 1.001

29.5 29.5 °C 85.0 85.0 °F 0.0

2409 2138 L/min 636 565 gpm 0.887

Flow rate (tons × 2) 6.5 6.5 L/min∙kW 3.01 3.02 gpm/ton 1.003

Capacity 371.9 329.1 kW 105.7 93.6 tons 0.885

Power to Compressor 86.0 79.0 kW 86.0 79.0 kW 0.919

COP or EER (compressor only) 4.33 4.17 [] 14.76 14.21 Btu/W∙hr 0.963

Refrigerant Mass Flow Rate 8,596 8,405 kg/hr 18,950 18,530 lbm/hr 0.978

Refrig Flow @ Cmpr Suction 518.2 518.2 m3/hr 305.0 305.0 cfm 1.000

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

Data Points Collected at Standard Operating Conditions

Low GWP AREP SYSTEM DROP‐IN TEST DATA FORM page 2

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

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

Evaporator (shell & tube)

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

pressure drop 121 96 kPa 17.5 14.0 psid 0.799

Condenser (shell & tube)

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

pressure drop 140 112 kPa 20.3 16.3 psid 0.802

Refrigerant Side

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

Compressor (screw)

suction 3.9 338 3.3 311 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

Condenser (shell & tube w/integral subcooler)

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

subcooler outlet 32.5 911 32.6 861 90.5 132.1 90.8 124.9

subcooling (local) 3.5 2.9 6.2 5.3

Expansion Device (EXV)

inlet 32.5 911 32.6 861 90.5 132.1 90.8 124.9

Evaporator (shell & tube)

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

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

suction line pressure drop 3.2 3.0 kPa 0.46 0.44 psid 0.96

discharge line pressure drop 20 19 kPa 2.90 2.82 psid 0.97

08‐Nov‐2012

water

water

Base Alt. Base Alt.
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 N‐13b Honeywell

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 79.4 kg 180 175 lbm 0.972

Composition (at Cmpr Suct)

6.7 6.7 °C 43.98 43.98 °F 0.00

1928 1636 L/min 509.3 432.3 gpm 0.849

Flow rate (tons × 2) 5.2 5.2 L/min∙kW 2.41 2.40 gpm/ton 0.995

29.5 29.5 °C 85.0 85.1 °F 0.1

2409 2047 L/min 636 541 gpm 0.850

Flow rate (tons × 2) 6.5 6.5 L/min∙kW 3.01 3.00 gpm/ton 0.996

Capacity 371.9 317.2 kW 105.7 90.2 tons 0.853

Power to Compressor 86.0 74.4 kW 86.0 74.4 kW 0.865

COP or EER (compressor only) 4.33 4.26 [] 14.76 14.55 Btu/W∙hr 0.986

Refrigerant Mass Flow Rate 8,596 7,784 kg/hr 18,950 17,160 lbm/hr 0.906

Refrig Flow @ Cmpr Suction 518.2 519.0 m3/hr 305.0 305.5 cfm 1.002

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

Data Points Collected at Standard Operating Conditions

Low GWP AREP SYSTEM DROP‐IN TEST DATA FORM page 2

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

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

Evaporator (shell & tube)

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

pressure drop 121 92 kPa 17.5 13.4 psid 0.766

Condenser (shell & tube)

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

pressure drop 140 108 kPa 20.3 15.7 psid 0.774

Refrigerant Side

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

Compressor (screw)

suction 3.9 338 3.6 290 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

Condenser (shell & tube w/integral subcooler)

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

subcooler outlet 32.5 911 32.1 806 90.5 132.1 89.7 116.9

subcooling (local) 3.5 3.5 6.2 6.3

Expansion Device (EXV)

inlet 32.5 911 32.1 806 90.5 132.1 89.7 116.9

Evaporator (shell & tube)

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

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

suction line pressure drop 3.2 2.9 kPa 0.46 0.42 psid 0.92

discharge line pressure drop 20 20 kPa 2.90 2.84 psid 0.98

08‐Nov‐2012

water

water

Base Alt. Base Alt.
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 R1234ze Honeywell

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 79.4 kg 180 175 lbm 0.972

Composition (at Cmpr Suct)

6.7 6.6 °C 43.98 43.96 °F ‐0.02

1928 1417 L/min 509.3 374.2 gpm 0.735

Flow rate (tons × 2) 5.2 5.1 L/min∙kW 2.41 2.37 gpm/ton 0.985

29.5 29.5 °C 85.0 85.0 °F 0.0

2409 1774 L/min 636 469 gpm 0.736

Flow rate (tons × 2) 6.5 6.4 L/min∙kW 3.01 2.97 gpm/ton 0.987

Capacity 371.9 277.4 kW 105.7 78.9 tons 0.746

Power to Compressor 86.0 63.0 kW 86.0 63.0 kW 0.733

COP or EER (compressor only) 4.33 4.40 [] 14.76 15.02 Btu/W∙hr 1.017

Refrigerant Mass Flow Rate 8,596 6,981 kg/hr 18,950 15,390 lbm/hr 0.812

Refrig Flow @ Cmpr Suction 518.2 517.7 m3/hr 305.0 304.7 cfm 0.999

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

Data Points Collected at Standard Operating Conditions

Low GWP AREP SYSTEM DROP‐IN TEST DATA FORM page 2

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

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

Evaporator (shell & tube)

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

pressure drop 121 71 kPa 17.5 10.2 psid 0.585

Condenser (shell & tube)

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

pressure drop 140 81 kPa 20.3 11.7 psid 0.578

Refrigerant Side

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

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

Condenser (shell & tube w/integral subcooler)

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

subcooler outlet 32.5 911 32.4 671 90.5 132.1 90.3 97.3

subcooling (local) 3.5 2.8 6.2 5.0

Expansion Device (EXV)

inlet 32.5 911 32.4 671 90.5 132.1 90.3 97.3

Evaporator (shell & tube)

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

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

suction line pressure drop 3.2 2.6 kPa 0.46 0.38 psid 0.83

discharge line pressure drop 20 15 kPa 2.90 2.14 psid 0.74

08‐Nov‐2012

water

water

Base Alt. Base Alt.
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 ARM‐42a Arkema

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 79.4 kg 180 175 lbm 0.972

Composition (at Cmpr Suct)

6.7 6.7 °C 43.98 43.99 °F 0.01

1928 1856 L/min 509.3 490.4 gpm 0.963

Flow rate (tons × 2) 5.2 5.0 L/min∙kW 2.41 2.34 gpm/ton 0.973

29.5 29.5 °C 85.0 85.0 °F 0.0

2409 2319 L/min 636 613 gpm 0.963

Flow rate (tons × 2) 6.5 6.3 L/min∙kW 3.01 2.93 gpm/ton 0.973

Capacity 371.9 367.9 kW 105.7 104.6 tons 0.989

Power to Compressor 86.0 88.1 kW 86.0 88.1 kW 1.024

COP or EER (compressor only) 4.33 4.18 [] 14.76 14.25 Btu/W∙hr 0.966

Refrigerant Mass Flow Rate 8,596 9,825 kg/hr 18,950 21,660 lbm/hr 1.143

Refrig Flow @ Cmpr Suction 518.2 526.1 m3/hr 305.0 309.7 cfm 1.015

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

Data Points Collected at Standard Operating Conditions

Low GWP AREP SYSTEM DROP‐IN TEST DATA FORM page 2

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

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

Evaporator (shell & tube)

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

pressure drop 121 111 kPa 17.5 16.1 psid 0.919

Condenser (shell & tube)

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

pressure drop 140 130 kPa 20.3 18.9 psid 0.932

Refrigerant Side

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

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

Condenser (shell & tube w/integral subcooler)

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

subcooler outlet 32.5 911 32.5 948 90.5 132.1 90.4 137.5

subcooling (local) 3.5 4.6 6.2 8.3

Expansion Device (EXV)

inlet 32.5 911 32.5 948 90.5 132.1 90.4 137.5

Evaporator (shell & tube)

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

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

suction line pressure drop 3.2 3.6 kPa 0.46 0.53 psid 1.16

discharge line pressure drop 20 22 kPa 2.90 3.24 psid 1.12

08‐Nov‐2012

water

water

Base Alt. Base Alt.