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ηR _ th = Net work input Total heat input = = (h3 − h4 )− (h2 − h1 ) P International Journal of Civil and Environmental Engineering 2:1 2010 φ14 φ11 Outlet Inlet 1.0 φ9 Front View Isometric View T (ExpanderpowerW )−(PumppowerW )(5) Heat gain in Evaporator QE h3 −h2 If the pump work W P is significantly less than expander power, then W P can be ignored. If process 1→2 occurs at a low pump pressure without any temperature change, or by isentropic compression, then (h3− h2) in Eq. 5 can be replaced with (h3− h1). The theoretical thermal efficiency is given by ηR_th=(h3−h4)−(h2−h1)≅h3−h4 . (6) h3 − h2 h3 − h 1 The measured thermal efficiency that does not take into account the pump power loss, is given by (7) 3 1 WF The measured thermal efficiency that takes into account the pump power loss, is given by Fig. 3 Rotary-vane-type expander used in the proposed ORC system η= WT ( h − h ) m Pump Heater 3 Expander Evaporator 4 Condenser 2 Pump 1 Flow Surge meter tank Load Electric motor load Water Hot water Drain R1 η = WT −WP (8) ( h − h ) m 3 1 WF R2 The theoretical expander power is calculated using the following equation W =m (h−h) (9) T_th WF 3 1 The expander efficiency is calculated using the following equation WT _ th In the above equations, the enthalpies were calculated using the measured pressure and temperature in the experiment. REFPROP ver.8, developed by the NIST [8], was used in the calculations. The mass flow rate of the working fluid was also measured in the experiment. III. EXPERIMENT USING COMPACT ORC SYSTEM A. Rotary-vane-type expander The theoretical thermal efficiency of the ORC system for a small temperature difference between the hot and cold sources (60°C–80°C in our study) is usually low because of the low expander efficiency. A few studies focusing on the development of an efficient compact expander for low temperature ORC systems have been conducted. For this purpose, a compact rotary-vane-type expander, categorized as a displacement-type Fig. 4 Experimental apparatus of the proposed ORC system η = WT T (10) TABLE I PRINCIPAL SPECIFICATIONS OF THE PROPOSED ORC SYSTEM HFC-245fa (CH3CH2CHF2), Working fluid Heat exchangers (evaporator & condenser) Hot source Heater Cold source Expander Working fluid pump Molecular weight: 134.05, Boiling temperature: 14.9°C Brazed plate heat exchanger, 2 Heat conduction area (Evaporator): 0.144 m Heat conduction area (Condenser): 0.168 m2 Circulated water, Temperature range: 60∼90°C Electrical heater, Maximum output: 1kW Tap water, Temperature range: 7∼12°C Rotary-vane-type expander Rietschle Thomas 5002F Diaphragm Typical volume flow rate: 0.4 L/min pump, 13 expander, was employed. This expander has a high efficiency and a low cost due to its simple mechanism and minimal mechanical parts. Fig. 3 shows the structure of the rotary-vane-type expander. 27 19PDF Image | Efficiency of Compact Organic Rankine Cycle System with Rotary-Vane-Type Expander for Low-Temperature Waste Heat Recovery
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