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𝜂= h!−h! −(h!−h!) (Eq.1) h! − h! where h! is the specific enthalpy at different states. The mass flow rate of the working fluid (𝑚!") was calculated by Equation 2, 𝑚!" = 𝑚!"(h! − h!) (Eq. 2) h! − h! where 𝑚!" is the assumed unit mass flow rate of the exhaust gas. Equation 2 assumes no heat loss in the evaporator. The mass flow rate of the air in the condenser (𝑚!"#) was calculated by Equation 3, 𝑚!"# = 𝑚!"(h! − h!) (Eq. 3) h!! − h!" Equation 3 assumes no heat loss in the condenser. The amount of work produced by the cycle (𝑊) was calculated by Equation 4, 𝑊 = 𝑚!"(h! − h!) (Eq. 4) The maximum pressure in the cycle is the turbine inlet pressure P5, while the minimum pressure in the cycle is the condenser pressure P1, P6 or P7. So far, the cycle calculations have been based on the statement that T9 and P5 are known variables. Given a T9 (or T5 since T! = T! − ∆T!!!), P5 can vary from the saturated vapor pressure at T5 to the condensing pressure P1, P6 or P7 (condensing pressure is independent of P5). Therefore, to optimize the cycle performance, the model will internally calculate the efficiency or work at different P5 given a T9, and will only report the cycle characteristics when the cycle performance (either efficiency or work) is optimized at a given T9. Figure 4 shows this idea. 13PDF Image | Working Fluid Selections in Organic Rankine Cycle ICE
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