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46 Results and Discussion Table 4-4: Comparative analysis of the turbine results Speed [rpm] Specific Volume Ratio [-] Specific Pressure Ratio [-] Blade height at nozzle outlet [mm] Rotor inlet diameter [mm] Rotor out rms diameter [mm] Isentropic Efficiency [%] Mach number at rotor inlet Mw2 [-] Mach number at rotor outlet Mw3 [-] * Quoted as Mabs2 in [21] Hypothetical Optimum Fluid 103129 54.62 32.03 1.25 47 25 81.22 1.59 0.75 Real Optimum Fluid D4[21] 66880 25990 57.69 53 41.16 45.06 1.69 2.8 68 160 37 90 81.13 78 1.67 1.66∗ 0.79 0.92 while a low degree of reaction has been considered for reasons stated in the previous chapter. The speed of revolution of the turbine for the optimum fluid is considerably higher than the reference work. One of the reasons for this could be the molecular weight which is lower in case of MDM than D4. The total mass flow decreases by around 9% in case of MDM . Thus in order to achieve volumetric flow rates of the same order, the turbine with MDM as working fluid has to rotate at a much higher rpm than D4. The resulting turbine has a significantly smaller rotor diameter thus making the system compact and feasible to be implemented on board a truck. The specific speed is best regarded as a shape parameter that for any given value there is an optimum rotor form [1]. The specific speed of the turbine in case of MDM is 0.8. Rohlik [45] predicted a distribution of losses along the curve of maximum total to static efficiency of the turbine with respect to the specific speed which is shown in Figure 4-8. Figure 4-8: Predicted distribution of losses along the curve of maximum total to static efficiency [45] The majority of the losses that are present at a specific speed of 0.8 is due to the exit Akshay Hattiangadi Master of Science ThesisPDF Image | Working Fluid Design for Organic Rankine Cycle
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