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Paper ID: 118, Page 5 In Table 2 the main results of the 1D analysis are provided respectively for the radial outflow and axial turbine. Table 2: Main results of 1D mean line analysis Radial Outflow Turbine Profile and T.E. losses [%] 3.572% Endwall losses [%] 6.635% Leakage losses [%] 2.974% Disk friction [%] 1.332% Axial Turbine 5.353% 6.925% 4.110% 1.332% In Table 2 four categories of fluid-dynamic losses are listed: the profile and trailing edge losses and the endwall ones are defined as in AMDCKO model (Ainley and Mathieson, 1951 – Dunham and Came, 1970 – Kacker and Okapuu, 1981). Leakage losses are calculated as indicated by Egli (Egli, 1935) and disk friction as Daily and Nece (Daily and Nece, 1960): to compute these losses, clearances are supposed to be the same for both configurations. Important conclusions can be deduced by analyzing results in Table 2. In fact profile losses in the axial configuration are higher than in the radial outflow, as the first results to have its stages more loaded than the other one with a highly supersonic flow; on the other side the expansion in the radial outflow turbine is at most transonic. The axial turbine has also higher endwall losses, as a consequence of the lower h/c and h/d ratios (Traupel, 1966 – Horlock, 1966 - Dixon, 1998 - Lakshminarayana, 1986 or Moustapha et al., 2003). Finally, as axial blades are smaller than the radial ones and because of the lower h/d ratio, leakage losses are minor in the radial outflow turbine. As a consequence of this considerations, for the present case study the radial outflow turbine results to have a higher efficiency than the axial one. 3.2. CFD simulation After the conclusions reported above, the comparison must be continued; for this reason a viscous 3D CFD analysis of both turbines is performed. The code employed in this step is ANSYS CFX. In both of the domains periodic boundary conditions are used and for interface between the two cascades the stage method is utilized for modeling frame change (ANSYS, 2013). Figure 4: Interfaces for each cascade studied (periodic boundary conditions on yellow surfaces) To generate blades of both the turbines an in-house database has been used. For thermodynamic properties look-up tables (Pini et al., 2015) are compiled with data from Refprop 9.1 (NIST, 2013). The used turbulence model is the k-omega SST with the high resolution advection scheme (ANSYS, 2013). In a first step for both the turbines a computational grid of about 2 million nodes and 7.5 million of tetra and hexa elements has been used; mesh has been then refined to about 8.5 million nodes and 30 million elements with differences in calculated results below 1%. Skewness has been always below 0.9 and maximum Aspect Ratio results to be 62. 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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