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Chapter 5: Fluid selection and cycle optimization The overall system efficiency: ηoverall= W ̇ net =εhr⋅ηORC (75) M ̇ h t f ⋅ c̄ p , h t f ⋅ ( T h t f , s u , e v − T a m b ) 5.4 Thermodynamic optimization In the present case of an ORC designed for a waste heat recovery application, the thermodynamic optimization should maximize the net power output. This is equivalent to maximizing the overall efficiency since the flow rate and the temperature of the heat source are fixed in Eq. 75. For the purpose of this optimization, the pinch points on the heat exchangers must be imposed. A value of 10K is selected for both the condenser and the evaporator. The pressure drop is set to 100 mbar on the evaporator and to 200 mbar on the condenser. The optimization is performed in agreement with the guidelines developed in section 4.2 : superheating and condensing temperature are kept as low as possible while the evaporating temperature is optimized. Increasing the evaporation temperature implies several antagonist effects: ➢ The under-expansion losses in the expander are increased, and its efficiency is decreased ➢ The heat recovery efficiency is decreased since the heat source is cooled down to a higher temperature. This is shown in Figure 70: the dashed cycle operates at a lower evaporating temperature, and more heat is recovered from the heat source. ➢ The expander specific work is increased since the pressure ratio is increased. Figure 70: T-s diagram of the cycle for two different Tev 22PDF Image | Organic Rankine Cycles for Waste Heat Recovery and Solar Uses
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