mostafa siminar
TRANSCRIPT
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Helwan University
Faculty of Engineering
Mechanical Power Eng. Dep. Mattaria-Cairo
1
PERFORMANCE EVALUATION OF A RESIDENTIAL
AIR-CONDITIONER WORKING WITH OZONE-FRIENDLY REFRIGERANTS
Submit ted by
Eng. Mostafa Hassanain Mahmod
In Partial Fulfillment of the Requirement for Degree of Master
of Science in Mechanical Engineering
Supervised by
Prof. Dr. Mohamed Fatouh Ahmed
Dr. Essam Mahrous Elgendy
Mechanical Power Engineering Department
Faculty of Engineering (Mattaria)
Helwan University
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Helwan University
Faculty of Engineering
Mechanical Power Eng. Dep. Mattaria-Cairo
PERFORMANCE EVALUATION OF A RESIDENTIALAIR-CONDITIONER WORKING WITH OZONE-FRIENDLY REFRIGERANTS
Examining committee:
Mechanical Power Engineering
Department
Faculty of Engineering, Cairo
University
Pro. Dr. Adel Khalil Hassan
Mechanical Power Engineering
Department
Faculty of Engineering,
Mattaria, Helwan University
Pro. Dr. Abdel Hamid Basheer Helali
Mechanical Power Engineering
Department
Faculty of Engineering,
Mattaria, Helwan University
Pro. Dr. Mohamed Fatouh Ahmed
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Table of contents
1. Introduction
2. Literature Survey
3. Objective of Present Work
4. Test rig Description
5. Experimental Results
6. Conclusions and Recommendations
3
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Introduction
4
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Introduction
5
Environmental Challenges.
Ozone Depletion (The Montreal Protocol)
Substance) Base Level Production/Consumption Rate Control
First Group
HCFC
substances
Average
Consumpti
on Rate in
2009-2010
Freezing production/consumption
levels (1st January, 2013)
10% reduction (1st January ,2015)
35% reduction (1st January , 2020)
67.5% reduction (1st January ,2025)
100% reduction (1st January, 2030) with a
possible exemptions for necessary uses.
Table (2.1): Timetable for phasing out use of HCFCs for (UNIDO, 2009)
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Introduction
Global Climate Change (Kyoto Protocol)
Fig.1 Global warming of HFC mixtures (Dupont,2009)
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Introduction
Refrigerant Selection Criteria.
Fig.2 Mechanisms and some refrigerant options to substitute R22 in medium
and low temperature applications. (Llopis et al., 2012)
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Introduction
100 200 300 400 500
Specific enthalby (kJ/kg)
1
10
100
Pressure(bar)
R-22
R-438A
T=40C
T=-25C
T=5C
Fig. 3 Pressure -enthalpy diagram of
the R-22 and R-438A
Fig.4 Pressure -enthalpy diagram of the R-22
and its drop-in R-422A.
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Literature Survey
9
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Literature survey
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Authors YearInvestigation
TypeWorking fluids
Investigation
in
Elgendy E., Hassanain
M, Fatouh M 2014 Experimental R22,R438A
Assessment of R-
438A as a retrofit
refrigerant for R-22in direct expansion
water chiller
R. Llopis a,*, E. Torrella
b, R. Cabello a, D.
Sanchez a
2012 TheoreticalR22,R417B,R422D,
R404
HCFC-22
replacement with
drop-in and retrofit
HFC refrigerants in a
two-stagerefrigeration plant
for low Temperature
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Literature survey
11
Authors YearInvestigation
TypeWorking fluids Investigation in
R. Llopis,
Cabello,Snchez
, Torrella,
Patio. Snchez
2011 Experimental R22,R422A,R417B
Experimental evaluation of
HCFC-22 replacement by
the drop-in fluids HFC-
422A
and HFC-417B for low
temperature refrigerationapplications
Bukola Olalekan
Bolaji2011 Experimental R22,R404A,R507
Performance investigation
of ozone-friendly R404A
and R507 refrigerants as
alternatives to R22 in a
window air-conditioner
J.U. Ahamed
,R. Saidur, H.H.
Masjuki
2011Review
A review on exergy
analysis of vapor
compression
refrigeration system
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Literature survey
Authors Year InvestigationType
Working fluids Investigatedparameters
Vincenzo La
Rocca,
Giuseppe
Panno
2011 Experimental R417A, R422A ,R422D
Experimental performance
evaluation of a vapour
compression refrigerating
plant when replacing R22
with alternative
refrigerants
E. Torrella a, R.
Cabellob,, D.
Slnchezb, J.A.
Larumbea, R.
Llopisb
2010 ExperimentalR417A, R422A ,R422D
On-site study of HCFC-22
substitution for HFC non-
azeotropic blends
(R417A, R422D) on a water
chiller of a centralized
HVAC system
Ki-Jung Park,
Yun-Bo Shim,Dongsoo Jung
2009 Experimental R432A
Experimental performance
of R432A to replace R22 in
residential
air-conditioners and heat
pumps
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The literature survey revealed that many investigations were carried out on
air conditioner working with R22 alternatives but.
13
Literature survey
Concluding Remarks
Less research was conducted on an air conditioner running with R-422A
No investigation was carried for R-438A to evaluate its performance at
various operating conditions.
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Objective of Present Work
Flow rate through the condenser
Operating parameters
Inlet water temperature to the evaporator.
Inlet water temperature to the condenser.
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Test Rig
16
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PC unit
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Test rig description
Plate 2 Hot water circuit.Plate 1 Primary working fluid circuit.
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Test rig description
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Sightglass Receiver
Filter
drier
Evaporator
Expansion
Condenser
device
Compressor
p 3,t 3
ValveBall valveGate valve
T Temperaturep Pr es su reF Flow rate
Measured parameters
Chilled water
Hot water
Refrigerant
V 12
Condensing unit
DrainV 13
Hot water tank
Cooling coil
V 11 V 10t8
t9
F 2
Hot waterpu m p
t7
F 1
V 7V 6t6
V 9
V 8
Chilled water
pu m p
Drain
Chilled water
tank
Electric heater
Condensing unitCooling coil
Electric heater
V 1
p 5,t 5
p4
,t4
V 5
V 4
p 1,t 1p 2,t 2
V 3
V 2
Fig.5 A schematic diagram of the experimental apparatus.
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Test rig description
Ranges of operating parameters during the
experimental work
10 to 20 CInlet water temperature to the evaporator.
25 to 35CInlet water temperature to the condenser.
360kg/h to 556.9kg/hFlow rate through the condenser
358.2kg/hFlow rate through the evaporeator
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Test rig description
Instrumentation
Temperature at various locations in both primary and secondary
working fluids
Pressure at four locations in the primary working fluid circuit
Flow rate of secondary working fluids.
Input current and voltage supplied to the compressor.
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Data Reduction
EquationsParameter
)8T9(Twccwc= mcon,actQActual heating load
Qeva,act = mwe cwe (T6 T7)Actual cooling capacity
mr = Qeva,act / (h5 h1)Calculated ref. mass flow rate
Pelec = I V cos ()Actual compressor power
COPact,c = Qeva,act / PelecActual coefficient of
performance
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Experimental
Results
22
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Experimental result
23
Test Rig Validations
0
0.5
1
1.5
2
2.5
3
COP
PR
Present model
Fatouh et al. (2010)
Fig.6 Test rig validation using R-22 with Fatouh et al. (2010)
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24
Experimental result
Effect of Evaporator Water Inlet Temperature
Effect of Condenser Water Inlet Temperature
10 15 20Evaporator water inlet temperature (C )
1
6
11
16
21
26
Condenserandevaporatorpressures(bar)
pcon
peva
Twci=25.4 0.9 C
Twci=29.9 1.1 C
Twci=34.9 0.9 C
10 15 20Evaporator water inlet temperature (C )
1
6
11
16
21
26
Condenserandevapora
torpressures(bar)
pcon
peva
Twci=24.9 0.5 C
Twci=30.7 0.8 C
Twci=34.8 1.5 C
Fig.8 Variation of operating pressures with evaporator water inlet
temperature at different condenser water inlet temperature for R-
422A.
Fig.7 Variation of operating pressures with evaporator
water inlet temperature at different condenser water inlet
temperature for R-438A
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Experimental result
10 15 20Evaporator water inlet temperature (C )
1
2
3
4
5
Pressureratio
30
60
90
120
150
Ref
rigerantmassflowrate(kg/h)
PR
ref.
Twci=25.4 0.9 C
Twci=29.9 1.1 CTwci=34.9 0.9 C
Fig.9 Variation of pressure ratio and refrigerant mass
flow rate with evaporator water inlet temperature at
different condenser water inlet temperature for R-438A
10 15 20Evaporator water inlet temperature (C )
1
2
3
4
5
Pressureratio
20
65
110
155
200
Refrigerantmassflowrate(kg/h)
PR
ref.
Twci=24.9 0.5 C
Twci=30.7 0.8 CTwci=34.8 1.5 C
Fig.10 Variation of pressure ratio and refrigerant mass
flow rate with evaporator water inlet temperature at
different condenser water inlet temperature for
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Experimental result
10 15 20Evaporator water inlet temperature ( C )
1
2
3
4
5
Coolingcapac
ityandcompressorpower(kW)
Qeva
Pcomp
Twci=25.4 0.9 C
Twci=29.9 1.1 C
Twci=34.9 0.9 C
Fig.11 Variation of actual cooling capacity and the
power input to the compressor with evaporator waterinlet temperature at different condenser water inlet
temperature for R-438A.
10 15 20Evaporator water inlet temperature (C )
0
1
2
3
4
Coolingcapacityandcompressorpower(kW)
Qeva
Pcomp
Twci=24.9 0.5 CTwci=30.7 0.8 C
Twci=34.8 1.5 C
Fig.12 Variation of actual cooling capacity and the
power input to the compressor with evaporator water
inlet temperature at different condenser water inlet
temperature for R-422A.
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27
Experimental result
10 15 20Evaporator water inlet temperature (C )
0
5
10
15
20
25
Evaporatoerwateroutlettemperature(C)
0
0.7
1.4
2.1
2.8
Coefficientofperformance
Tweo
COP
Twci=25.4 0.9 C
Twci=29.9 1.1 C
Twci=34.9 0.9 C
Fig.13 Variation of actual coefficient of performance andexit temperatures of evaporator with evaporator water
inlet temperature at different condenser water inlet
temperature for R-438A.
10 15 20Evaporator water inlet temperature (C )
0
6
12
18
24
30
Evaporatoerwateroutlettemperature(C)
0
0.5
1
1.5
2
Coefficientofperformance
Tweo
COP
Twci=24.9 0.5 CTwci=30.7 0.8 C
Twci=34.8 1.5 C
Fig.14 Variation of actual coefficient of performance and exittemperatures of evaporator with evaporator water inlet
temperature at different condenser water inlet
temperature for R-422A.
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28
Experimental result
Effect of Condenser Water Mass Flow Rate
10 15 20
Evaporator water inlet temperature (C )
0
9
18
27
36
Evaporatoerwaterout
lettemperature(C)
0
0.55
1.1
1.65
2.2
Coefficientofperformance
Tweo
COP
wc=363.6kg/h
wc=406.8kg/h
wc=542.5kg/h
Fig.15 Variation of actual coefficient of performance and
exit temperatures of evaporator with evaporator water
inlet temperature at different condenser water flow rate
for R-438A
10 15 20
Evaporator water inlet temperature (C )
0
9
18
27
36
Evaporatoerwaterout
lettemperature(C)
0
0.55
1.1
1.65
2.2
Coefficientofperformance
Tweo
COP
wc=367.2kg/h
wc=406.8kg/h
wc=558kg/h
Fig.18 Variation of actual coefficient of performance and
exit temperatures of evaporator with evaporator water
inlet temperature at different condenser water flow rate
for R-422A.
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Experimental result
Comparison among Investigated Refrigerants
5 10 15 20 25Evaporator water inlet temperature (C )
0
5
10
15
20
25
Condenserandevapo
ratorpressures(bar)
pconpeva
R-22
R-438A
R-422A
10 15 20Evaporator water inlet temperature (C )
1
1.75
2.5
3.25
4
Pressur
eratio
30
55
80
105
130
Refrigerantmassflowrate(kg/h)
PR
ref.
R-22
R-438A
R-422A
Fig.20 Comparison of variation of pressure ratio and
refrigerant mass flow rate with evaporator water inlet
temperature.
Fig.19 Comparison of variation of operating pressures with
evaporator water inlet temperature.
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Experimental result
10 15 20Evaporator water inlet temperature (C )
0
1
2
3
4
Coolingcapacityandcompressorpower(kW)
Qeva
Pcomp
R-22
R-438A
R-422A
10 15 20Evaporator water inlet temperature (C )
0
9
18
27
36
Evaporatoerw
ateroutlettemperature(C)
0
0.7
1.4
2.1
2.8
Coefficientofperformance
Tweo
COP
R-22
R-438A
R-422A
Fig.22 Comparison of variation of actual coefficient ofperformance and exit temperatures of evaporator
with evaporator water inlet temperature.
Fig.21 Comparison of variation of actual coolingcapacity and the power input to the compressor with
evaporator water inlet temperature.
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Experimental result
8 12 16 20 24Evaporator water inlet temperature (C )
75
80
85
90
95
100
Compressordichargetemperature(C)
R-22R-438A
R-422A
Fig. 23 Comparison of variation of compressor discharge temperature with evaporator water inlet temperature.
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Conclusions
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Conclusions
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The relative condenser pressure of R-438A and R-422A to R-22 is
106.8% and129%, respectively.
The refrigerant mass flow rate of R-438A and R-422A is higher than
that of R-22 by 8% and 27.5% respectively.
The Pressure ratio of R-438A and R-422A increase by 8.9% and 18%
respectively.
The compressor electric power of R-438A decreases by 1.7% about
R-22, while R-422A increases by16.4%.
Actual cooling capacity of R-438A decreases by 8.6% and R-422A by
21.6%.
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Conclusions
The reported results of present work confirm that R-438A is the best
drop-in refrigerant for R-22 in the old water cooled chiller.
COP of R-438A and R-422A decrease by 9.3% and 32.8%
respectively.
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Recommendations
Predict the performance characteristics of the Heat pump system working
with R-438A .
Predict the performance characteristics of the R438A as a drop-in to R-22
in low back pressure applications.
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Present work publications
36
Elgendy E., Hassanain M., Fatouh M., Assessment of R-438A as a
retrofit refrigerant for R-22 in direct expansion water chiller,
International Journal of Refrigeration 2014, In press.
Elgendy E., Hassanain M, Fatouh M, International Journal of
Refrigeration 2014, In reviw.
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Thank you