Performance Evaluation of an Automobile Air Conditioning System Using R134a

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Abstract:

In this paper, a detailed energy and exergy analysis have been dealt with on experimental AAC (Automobile Air Conditioning) system with R134a as working refrigerant. For this aim, an experimental AAC system consisting of a laminated type evaporator, swash plate type compressor, a parallel flow type condenser, TXV(thermostatic expansion valve) and a receiver drier. The performance analysis of separate components of AAC system has been carried out under various compressor speeds and thermal loads. AAC system equipped with increasing compressor speed by three-phase electric motor controlled by frequency converter. Various thermal loads in the range of 1500 and 2850 W were applied to the system by means of electric heaters. The experiments were conducted at the condensing temperatures of 50-60 oC for each thermal load, and at the compressor speeds of 600, 800, 1000, 1200, 1400 rpm for each thermal load-condensing temperature combination. The refrigerant and air temperatures, refrigerant pressures, compressor speed, air velocity passing through the evaporator and thermal load were measured. Effects on system performance of such operational parameters as compressor speed, return air in the evaporator and condensing air temperatures have been experimentally evaluated and by means of energy and exergy analysis.

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Periodical:

Advanced Materials Research (Volumes 433-440)

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4952-4958

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January 2012

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[1] Kiatsiriroat T, Euakit T. Performance analyses of an automobile air conditioning system with R/22/R124/R152A Refrigerant. Applied Thermal Engineering 1997; 17(11): 1085–1097.

DOI: 10.1016/s1359-4311(97)80003-8

Google Scholar

[2] Bhatti M.S. Enhancement of R-134a automotive air conditioning system. SAE Technical Papers, Society of Automotive Engineers 1999; 1999-01-0870.

DOI: 10.4271/1999-01-0870

Google Scholar

[3] Jung D, Park B, Lee H. Evaluation of supplementary/retrofit refrigerants for automobile air-conditioners charged with CFC12. Int. J. Refrigeration 1999; 22, 558–568.

DOI: 10.1016/s0140-7007(99)00022-5

Google Scholar

[4] Lee GH, Yoo JY. Performance analysis and simulation of automobile air conditioning system, International Journal of Refrigeration 2000; 23, 243–254.

DOI: 10.1016/s0140-7007(99)00047-x

Google Scholar

[5] Ratts EB, Brown JS. An experimental analysis of the effect of refrigerant charge level on an automotive refrigeration system. Int. J. Therm. Sci., 2000; 39, 592–604.

DOI: 10.1016/s1290-0729(00)00208-8

Google Scholar

[6] Esen DO. Experimental analysis of the effect of R12 and R134a refrigerants and compressor speed on the performance of the refrigeration cycle of automobile air conditioning. Ph.D. Thesis, Kocaeli University, Turkey, (2005).

Google Scholar

[7] Exergy Analysis of an Automobile Air Conditioning System Using R134a ", Hosoz, M, Proc. Second Int. Exergy, Energy and Environment Symposium (IEEES2), Proc. Second Int. Exergy, Energy and Environment Symposium (IEEES2), Kos, Greece, (2005).

DOI: 10.1007/978-3-319-04681-5_27

Google Scholar

[8] Brown JS, Yana-Motta SF, Domanski PA. Comparative analysis of an automotive air conditioning system operating with CO2 and R134a. International Journal of Refrigeration 2002; 25, 19–32.

DOI: 10.1016/s0140-7007(01)00011-1

Google Scholar

[9] Jabardo JMS, Mamani WG, Ianella MR. Modelling and experimental evaluation of an automotive air conditioning system with a variable capacity compressor. International Journal of Refrigeration 2003; 25, 1157–1173.

DOI: 10.1016/s0140-7007(02)00002-6

Google Scholar

[10] Kaynakli O, Horuz I. An experimental analysis of automotive air conditioning system. Int. Commun. Heat Mass Transfer 2003; 30, 273–284.

DOI: 10.1016/s0735-1933(03)00038-1

Google Scholar

[11] Al-Rabghi OM, Niyaz AA. Retrofitting R-12 car air conditioner with R-134a refrigerant, Int. J. Energy Res. 2000; 24, 467–474.

DOI: 10.1002/(sici)1099-114x(200005)24:6<467::aid-er592>3.3.co;2-i

Google Scholar

[12] Tian C, Li X. Numerical simulation on performance band of automotive air conditioning system with variable displacement compressor, Energy Conversion Management 2005; 46, 2718–2738.

DOI: 10.1016/j.enconman.2004.12.012

Google Scholar

[13] Moffat RJ, Describing the uncertainties in experimental results. Experimental Thermal and Fluid Science 1988; 1(1), 3-17.

DOI: 10.1016/0894-1777(88)90043-x

Google Scholar

[14] Aprea C, Rossi FD, Greco A, Renno C, Refrigeration plant exergetic analysis varying the compressor capacity, International Journal of Energy Research 2003; 27: 653–669.

DOI: 10.1002/er.903

Google Scholar

[15] Bejan A. Fundamentals of exergy analysis entropy generation minimation and the generation of flow architecture. International Journal of Energy Research 2002; 26, 545-565.

DOI: 10.1002/er.804

Google Scholar

[16] Moran MJ, Shapiro H.N. Fundamentals of engineering thermodynamics. New York: John& Sons.; (2000).

Google Scholar

[17] A collection of simulation tools for refrigeration. Cool Pack, 2004. www. et. dtu. dk/CoolPack Figure 1. Sketch of the experimental setup and instrumentation Figure 2. Refrigerant and air flow in evaporator Figure 3. Compression ratio as function of the compressor speed Figure 4. COP as a function of the compressor speed Figure 5. Refrigerant mass flow rate as a function of the compressor speed Figure 6. Rate of exergy change in the compressor. Figure 7. Rate of exergy change in the condenser Figure 8. Rate of exergy change in the thermostatic expansion valve. Figure 9. Rate of exergy change in the evaporator and suction line Figure 10. Rate of exergy change in the entire refrigeration circuit. Figure 11. Rate of exergy change in the entire refrigeration circuit to the evaporator load.

DOI: 10.7717/peerj.9582/fig-6

Google Scholar