Performance analysis of liquified petroleum gas (LPG) driven half-cycle air conditioning system
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ORIGINAL
Performance analysis of liquified petroleum gas (LPG) driven half-cycle air conditioning system Atif Muzaffar 1 & Taqi Ahmad Cheema 1 Cheol Woo Park 2
&
Ahmad Abbas 1 & Muhammad Tayyab 1 & Muhammad Ilyas 1 &
Received: 16 November 2019 / Accepted: 13 June 2020 # Springer-Verlag GmbH Germany, part of Springer Nature 2020
Abstract Liquified petroleum gas (LPG) is one of the potential refrigerants to be used in half-cycle air conditioning systems. After evaporation to get air-conditioning, LPG may be further used in combustion applications such as electric-generators, auto-motives and cooking stoves. Expansion device (or a flow control valve) is usually used before the evaporator to make sure that the refrigerant vaporizes in evaporator and provides cooling. The present study reports the investigation of an experimental study to determine the performance of three in-house designed and manufactured evaporators for an air conditioning system using LPG as refrigerant. The evaporators used are finned-tube evaporators having difference in tube arrangements, fin materials, fin spacing and tube dimensions. The thermal energy to evaporate LPG is obtained from air driven by a fan attached to one side of the evaporator. Cold air exiting from the evaporator is then supplied to a cabin having the similar dimensions of an automotive rickshaw. The performance parameters determined for a fixed time duration for different fan speeds include; the cooling effect, contact factor and rate of condensation. The investigations were conducted for different LPG flow rates and evaporative pressures. The test results show that for each flow condition; the cooling effect, contact factor and rate of condensation are also the function of air flow rate passing through the evaporator. Experimentally determined cooling effects were then analytically validated by using the Nusselt number correlations of Grimison model, modified Grimison model and Zhukauskas model for each of the evaporators used. Nomenclature a (constant) A total Surface area of finned tube evaporator [m2]. AT total surface area of tubes without fin [m]. Af surface area of fins [m2]. Aw surface area of tubes between fins [m2]. b Reynolds number exponent. B width of the fin per unit tube [m]. C length of the fin per unit tube [m]. c Prandtl number exponent. D tube internal diameter [m]. Df equivalent fin diameter [m]. Dr tube external diameter [m].
* Taqi Ahmad Cheema [email protected] * Cheol Woo Park [email protected] 1
Faculty of Mechanical Engineering, GIK Institute of Engineering Sciences and Technology, Topi 23460, Pakistan
2
School of Mechanical Engineering, Kyungpook National University, 80 Daehak-Ro, Buk-Gu, Daegu 41566, South Korea
EER F h h" h1 h2 Δh I K LPG LMTD l L Lt m mf ˙a m nr nt n N
energy efficiency ratio. correction factor. heat transfer coefficient [W/(m2K)]. effective heat transfer coefficient [W/(m2K)]. enthalpy of air at the inlet of evaporator [W/(m2K)]. enthalpy of air at the outlet of evaporator [W/(m2K)]. difference of specific enthal
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