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40 Results and Discussion composition from engine performance maps [21]. Another reason for this difference could be due to the fact that the paper does not consider the pressure drops in the heat exchanging equipments. The turbine model implemented influences the mass flow rate of the working fluid which in turn affects the net power output of the ORC system. The net efficiency is, however, higher because the input power to the system is lower (57 kWth) than the work of Lang et al. (62 kWth) in addition to a higher turbine efficiency. The system model developed here is then optimized along with the fluid parameters. However, before proceeding onto the optimization results, it is essential to validate the thermodynamic model implemented. The following section presents this comparison. 4-2 Validation of Thermodynamic model The fluid parameters of the PCP-SAFT EOS have been derived by fitting them to the seg- ment number as described in Chapter 3. A model to calculate the ideal gas heat capacity coefficients has also been proposed. It is important validate the model before proceeding onto the optimization problem. The PCP-SAFT model in FluidProp [37] is chosen as the reference against which this work has been validated. Table 4-2 presents a comparison of the simulated fluid parameters with those from FluidProp. Table 4-2: Comparison of the simulated fluid parameters Segment number [-] Molecular Mass[kg/kmol] Segment diameter [Å] Segment energy parameter ǫ/k [K] A [J/molK] 103 B [J/molK2 ] 106 C [J/molK3 ] 109 D [J/molK4 ] MDM (This Work) 5.15037 246.343 4.1038 211.915 69.4034 991.4745 -556.495 93.6186 MDM (FluidProp [37]) 5.15037 236.53 4.16893 213.3824 -6.16409 1184.23 -679.873 145.228 600 550 500 450 400 350 300 100 150 200 250 300 350 400 450 500 Temperature [degC] Cp(FluidProp) Cp(This Work) Figure 4-1: Comparison of the specific heat capacities for relevant temperature range for MDM Akshay Hattiangadi Master of Science Thesis Cp [kJ/kmolK]PDF Image | Working Fluid Design for Organic Rankine Cycle
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