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has an impact on the performance of the total ORC system. For the off-design analysis of the expander a commercial tool was utilized (Rital [16]). Table 3: Constrains of the expander design code Parameter Rotor inlet diameter, d4 Inlet blade height, b4 Inlet absolute flow angle, α4 Radius ratio, r5tip/r4 3. Results 3.1 Engine Modelling: Unit value m > 0.02 m > 0.001 degree < 80 - < 0.85 Explanation The minimum value considered for manufacturability. The minimum value considered for manufacturability. To achieve reasonable number of blade and minimize associated losses To prevent excessive tip curvature A heavy duty diesel engine model has been developed in this study, using a commercial engine simulation tool. The model was calibrated at three (3) different load/speed operating points, such as the optimum bsfc engine operating point, the maximum engine torque and maximum engine power. The engine model calibration was based on experimental fuel consumption values obtained in literature [18]. Table 4 briefly presents the engine simulation values, regarding fuel consumption and exhaust gas conditions. Table 4: Brief presentation of the engine simulation values Parameters Engine Speed [rpm] Bmep [bar] Power [kW] Torque [Nm] Bsfc [g/kWh] Exhaust Mass Flow Rate [kg/s] Exhaust Temperature [K] Bsfc point 1300 18.00 201 1476 192 0.30 681 Max Torque 1400 23.00 277 1887 194 0.39 719 Max Power 2100 18.00 325 1477 212 0.46 804 3.2 Design and Off-Design Analysis of the Radial Inflow Turbine The design of the ORC system is performed on the maximum engine power operating point, as this point is characterized by the higher content of exhaust waste heat, which can potentially lead to high inlet pressure and temperature for the expander and hence higher cycle efficiency. Initially, the proposed ORC thermodynamic model was utilized for the calculation of the 8PDF Image | Off Hwy Vehicle Radial Turbine Expander Design WHR ORC
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