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Chapter 5: Fluid selection and cycle optimization the last 30°C are not exploited, which represents more than 16% of the heat source potential. This is illustrated in Figure 64, showing the T-s diagram of the cycle in four different cases: Case A corresponds to a small heat source temperature glide, without recuperator; case B corresponds to a high temperature glide in the evaporator, without recuperator ; case C corresponds to a small temperature glide, with recuperator; Case D corresponds to a high temperature glide, with recuperator. For the purpose of the example, a heat source consisting of hot air at a temperature of 160°C and characterized by a flow rate of 1 kg/s is imposed. The heat sink is also assumed to be air, whose supply temperature is 10°C, and whose flow rate is adapted to maintain the imposed condensing temperature. The considered working fluid is HFC-245fa. The superheating at the evaporator exhaust is set to 10K, and the subcooling at the condenser exhaust is set to 5K. The pinch points are set to 10K. In case A, the heat capacity flow rate in the heat exchangers is high. This allows high evaporating and low condensing pressures. Increasing the pressure ratio leads to a higher efficiency. In case B, the temperature glide of the heat source is important and more heat is recovered from the heat stream. The pinch point limitation leads to a lower evaporating pressure and thus to a lower cycle efficiency (11.6% instead of 14.7%), but the amount of heat Figure 64: Cycle efficiency and output power for a given heat source and varying working conditions 6PDF Image | Organic Rankine Cycles for Waste Heat Recovery and Solar Uses
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