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69 The exhaust gas conditions at the three selected operating points are fed into the simple ORC model. Table 3-4: Presentation of the Engine Simulation Values Parameters P1 Engine Speed [rpm] 1400 Torque [N.m] 440 Power [kW] 69.4 Exhaust Temperature, C 338.6 Exhaust Mass Flow Rate [Kg/s] 0.1533 P2 P3 1500 2301 1108.2 858.2 173.98 186.7 474.8 512 0.2224 0.5194 The optimisation algorithm explained in Chapter 5 is applied to design and optimise the turbine at engine operating point P3. P3 is selected as the design point due to itshigh exhaust waste heat content, which can potentially lead to high inlet pressure and temperature for the turbine. After this process, the optimised geometry is then exported to the off-design code (Chapter 5) to generate turbine maps. R245fa is selected as the working fluid for the FGT and VGT becauseit presents a high thermal efficiency (Figure 3-8) and is also considered a dry fluid, which is favourable for avoiding fluid droplets at the turbine blades. The optimised turbine geometry is presented inTable 3-5. Figure 3-9 shows the nozzle vanes positions for closed, medium and fully open arrangements. The nozzle position is expressed by the turbine throat area, where 0.3 corresponds to 30% opening and 1 corresponds to 100% opening. Table 3-5: Turbine optimised geometry Parameter Diameter d2 (mm) 105 Diameter d3 (mm) 81 Diameter d4 (mm) 77 Diameter d5 (mm) 38 Diameter d_{5,tip} (mm) 6.6 Diameter d_{5,hub} (mm) 15.4 Blade height b4 (mm) 3.8 Blade height b5 (mm) 22.6 Number of rotor blades 16 Reaction (–) 0.41 Value Specific speed, Ns (–) Turbine power output, KW 0.486 Total to static efficiency 75.8 18.15PDF Image | Automotive Radial Turbine Expander Design WHR
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