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CHAPTER 5: Mean-line Modelling and Optimization of Organic RIT and Integration with Cycle Analysis Programme The known turbine inlet temperature (T1) and pressure (P1) were used to determine all the other thermodynamic properties at turbine inlet using EoS. The turbine is modelled to have a constant isentropic efficiency defined by: 𝜂𝑠𝑡𝑎𝑔𝑒,𝑡𝑠 = h1 − h5 Equation 5-1 h1 − h5,𝑠 Where h5,s is the turbine exit enthalpy after an isentropic expansion. For the turbine outlet, the isentropic expansion state point (S5,s=S1 & P5,s= P6) were used to determine all other properties with the known turbine isentropic efficiency. P6 itself was obtained from the given expansion ratio in Table 5-2 and the with the known P6 and quality (x6=0) at the condenser exit assuming that pressure losses are negligible and the condenser exit is at saturated liquid state T6 is obtined (T6 =EoS(P6, x6)). The power generated by the turbine was obtained by: 𝑊 =𝑚̇ (h−h) Equation5-2 𝑡𝑢𝑟𝑏𝑖𝑛𝑒 𝑤𝑓 1 5 All the heat rejection occurs in a single counter-flow condenser (with adiabatic assumption) and the condenser is constrained with a minimum pinch-point temperature difference of 5K. Heat balance on the condenser is defined by: 𝑄𝑜𝑢𝑡 = 𝑚̇ 𝑤𝑓(h5 − h6) = 𝑚̇ 𝑐𝑜𝑜𝑙𝑎𝑛𝑡(h𝑐𝑜𝑜𝑙𝑎𝑛𝑡,𝑜𝑢𝑡 − h𝑐𝑜𝑜𝑙𝑎𝑛𝑡,𝑖𝑛) Equation 5-3 The condenser inlet coincides with turbine outlet and its outlet properties were determined with the known T6 and x6. The performance of the pump is governed by a constant isentropic efficiency defined as: 𝜂𝑝𝑢𝑚𝑝 = h7,𝑠 − h6 Equation 5-4 h7 − h6 Where h7,s is the enthalpy at state 7 under an isentropic compression. The pump power consumption was determined by: 161 | P a g ePDF Image | SMALL-SCALE RADIAL INFLOW TURBINE FOR WHR ORC
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