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Mathematics 2020, 9, 50 20 of 30 the streamlines. In addition, the flow is more uniform in the 40,000 rpm case while strong vorticity is created in the 30,000 rpm. Mathematics 2020, 8, x FOR PEER REVIEW 21 of 34 Figure 22. Pressure distributions, Mach numbers, and velocity streamlines at 50% span and 471.55 K, Figure 22. Pressure distributions, Mach numbers, and velocity streamlines at 50% span and 471.55 K, for (a) PR = 3, for (a) PR = 3, N = 40,000 rpm (b) PR = 4.5, N = 40,000 rpm (c) PR = 3, N = 30,000 rpm and (d) PR = 6.9, N = 40,000 rpm (b) PR = 4.5, N = 40,000 rpm (c) PR = 3, N = 30,000 rpm and (d) PR = 6.9, N = 30,000 rpm. N = 30,000 rpm. The simulation is then re-run again at two different pressure ratios (ππ = 3 πππ ππ = 6.9) with A parametric study is performed using ANSYS CFX to evaluate the turbine isentropic efficiency and power output at different pressure ratios and rotational speeds. The results are presented in Figure 23. It is clearly shown that the turbine operates more efficiently 30,000 rpm as shown in Figure 22c,d. It is known that turbine size is inversely proportional to the at off-design speeds 30,000 rpm than the design point 40,000 rpm at low pressure ratios. turbine speed. Therefore, the turbine size with 30,000 rpm is considered overestimated which makes However, this is expected since the turbine is designed to operate under high-pressure the flow does not follow the blade passage properly as shown in Figure 22c,d. Mach numbers in these ratios, which clarifies the high turbine efficiencies at high-pressure ratios. Figure 23 also cases are higher than that in Figure 22a,b, although they have the same pressure ratio. However, this shows that turbine efficiency increases with increasing the pressure ratio, reaching a is justified by the higher absolute velocities. Figure 22d presents the results at ππ = 6.9 and 30,000 maximum value and then decreases. The turbine power, on the other hand, is a function of rpm. Compared to the 40,000 rpm (Figure 22a), Mach numbers are higher due to the higher velocities the enthalpy drop and turbine speed, Equation (4). As shown in Figure 23, turbine power as shown by the streamlines. In addition, the flow is more uniform in the 40,000 rpm case while strong vorticity is created in the 30,000 rpm. increases significantly with increasing the pressure ratio due to the increased enthalpy drop. A parametric study is performed using ANSYS CFX to evaluate the turbine isentropic efficiency β’ Different Turbine Inlet Temperatures and power output at different pressure ratios and rotational speeds. The results are presented in Temperatures of exhaust gases in an internal combustion engine vary considerably Figure 23. It is clearly shown that the turbine operates more efficiently at off-design speeds 30,000 according to vehicleβs operation. As mentioned in the previous study [14], the turbine inlet rpm than the design point 40,000 rpm at low pressure ratios. However, this is expected since the temperature increases linearly with increasing heat source temperature. Therefore, turbine turbine is designed to operate under high-pressure ratios, which clarifies the high turbine efficiencies performance is also investigated at different inlet temperatures and rotational speeds in at high-pressure ratios. Figure 23 also shows that turbine efficiency increases with increasing the the current study. pressure ratio, reaching a maximum value and then decreases. The turbine power, on the other hand, Like the design point, flow vortices are noticed downstream of the rotor blades at is a function of the enthalpy drop and turbine speed, Equation (4). As shown in Figure 23, turbine the suction side for all off-design points, as shown in Figure 24. This indicates that this power increases significantly with increasing the pressure ratio due to the increased enthalpy drop. part of the blade is not optimum. Figure 24 also indicates that flow pattern improves with increasing turbine inlet temperature for the same rotational speed. The closer inlet temperature gets to design point, the more uniform flow results as shown in Figure 24a,b. At off-design rotational speed (30,000 rpm), the flow is more uniform than that in design point speed (40,000) for low temperatures due to low fluid densities at the stator exit. In contrast,PDF Image | Generation of 3D Turbine Blades for Automotive ORC
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