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3. THE FLUID-DYNAMIC STUDY In the last years a rising interest in the radial outflow turbine has been noticed and some studies about its fluid-dynamics have been proposed (Spadacini et al., 2011 - Pini et al., 2013 - Persico et al., 2013 - Spadacini et al., 2013). Until today this configuration has been studied alone. In this work we would like to focus our attention on a comparison between the radial outflow and the axial configurations, considered as the reference technology. 3.1. Case study description To perform the above mentioned comparison a common case study has been used for both configurations. The boundary conditions are listed in Table 1. Table 1: Boundary conditions for common case study Paper ID: 118, Page 4 Fluid Turbine Inlet Pressure Turbine Inlet Temperature Turbine Outlet Pressure Turbine Mass Flow Rate [-] Pentane [bar] 10.3 [°C] 130 [bar] 1 [kg s^-1] 25 In order to simplify the mechanical configuration of the system and to reduce costs of investment, operation and maintenance due to the presence of gear, a direct coupling with the generator is chosen: so both turbines must rotate at 3000 rpm. An in-house made 1D code has been used to design the two machines: the code simulates the expansion of the working fluid in the turbine and it uses the losses model by AMDCKO (Ainley and Mathieson, 1951 – Dunham and Came, 1970 – Kacker and Okapuu, 1981); thermodynamic properties are calculated with Refprop 9.1 (NIST, 2013). As output the radial outflow turbine results in having 5 stages and producing an estimated power of 1924 kW, with an isentropic efficiency of 85.50%; the axial turbine, with 3 stages, has instead the power of 1852 kW and an efficiency of 82.30%. Figure 3: Example of modeled geometry for the radial outflow turbine (left) and axial turbine (right) – From Spadacini et al., 2011 3rd International Seminar on ORC Power Systems, October 12-14, 2015, Brussels, BelgiumPDF Image | FLUID-DYNAMICS OF THE ORC RADIAL OUTFLOW TURBINE
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