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Working Fluid Design for Organic Rankine Cycle

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Working Fluid Design for Organic Rankine Cycle ( working-fluid-design-organic-rankine-cycle )

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24 Model 3-3-2 Preliminary design of radial turbine The application plays an important role in defining the turbine’s performance in terms of quantities such as pressure ratio and required power output or flow rates and speed of rota- tion. Other requirements such as maximizing efficiency or specific work transfer (and hence minimizing size) also need to be considered which are often in conflict with the application based parameters mentioned earlier. Thus it is important to have the right balance between these two class of parameters. The objective and scope of this model is to correlate the tur- bine isentropic efficiency with the corresponding fluid properties and does not provide the final optimum dimensions of a turbine. Certain assumptions are made in this design procedure. These are listed in the following section. Assumptions The model is based on the procedure which uses non-dimensional parameters. The assump- tions and scope of this model are: 1. The methodology is commonly used for incompressible flow machines but can be ex- tended to compressible flow machines [1]. 2. The flow in the rotor is extremely complicated with unsteady, 3-D, viscous and com- pressible flows with complicated secondary flows. The preliminary design is a very simplified representation of the real flow. 3. The design process is more concerned with the aerodynamic considerations without any mechanical stress analysis except in conditions where the knowledge of experience can be used. 4. The stator (nozzle) geometry has not been considered. 5. Due to the comparatively large expansion ratio resulting from the thermodynamic cycle design, the absolute velocities at the nozzle outlet are supersonic. This results in an uncertainty over the predicted turbine performance, because there are no validations available for organic fluids with supersonic rotor inflow conditions. 6. Because of the strict constraints on sizes, an efficient diffuser cannot be designed; thus its possibly beneficial effect is also neglected. 7. The loss coefficients for the nozzle and rotor have been assumed based on practical values available for well-designed nozzle and rotor for 90o inflow radial turbines [17]. 8. The method uses some empirical values which are not available for the high-expansion ratio typical of high-temperature ORC turbines. These values were therefore assumed, resulting in a certain degree of uncertainty on the predicted isentropic efficiency [21]. Based on these assumptions, a model has been implemented which is discussed in the following section. Akshay Hattiangadi Master of Science Thesis

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