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12 Proceedings of the University of Vaasa. Reports losses. The use of the Kalina cycle for medium and high temperature thermal sources seems unjustified because there is no gain in performance instead, a com- plicated plant scheme, large surface heat exchangers and corrosion resistant mate- rials, such as titanium in the turbine, result. Zamfirescu & Dincer (2008) have compared the TFC, four ORCs and a Kalina cycle, all operating under the same conditions in the both heat sink and source. The same flow rate and temperature at source inlet and an isentropic efficiency of 70 % for the expander were assumed. Cycle pressures were selected to maximize exergy efficiency for each fluid. The cycle efficiencies ( ), power outputs (P) and heat inputs (Q) are listed in Table 1. Table 1. Comparison of TFC, four ORCs and a Kalina cycle, after (Zam- firescu & Dincer 2008) Cycle (fluid) ORC (R141b) ORC (R123) ORC (R245ca) ORC (R21) Kalina (NH3–H2O) TFC (NH3–H2O) An ORC with R141b has the highest from the source, while the trilateral more. The TFC uses the most of the source’s exergy because both the source fluid (water) and the working fluid (ammonia–water) are in liquid state and have simi- lar specific heats, and thus the temperature difference in the heat exchanger is minimized. Since the source stream exergy is fixed, the cycle that converts the most of it into work (or useful exergy) is the best. The TFC recovers the most of the source’s exergy (93 %), the Kalina cycle being the second best (76 %). Teng et al. (2011) have studied a Rankine cycle based WHR system for a modern heavy duty truck diesel engine. The primary WHR heat source was EGR cooling. Four working fluids, R245fa (C3H3F5), ethanol (C2H5OH), water and water- ethanol mixture were chosen as candidates for the comparison. Ethanol was se- (%) 10 9 9 9 3 8 P (kW) 13 17 18 18 13 38 Q (kW) 132 179 189 198 373 477 efficiency of 10 %, but extracts the least heat flash cycle receives the most, i.e., 3.6 timesPDF Image | Waste Heat Recovery Bottoming Cycle Alternatives
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