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3-D Inviscid Analysis of Radial Turbine Flow

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3-D Inviscid Analysis of Radial Turbine Flow ( 3-d-inviscid-analysis-radial-turbine-flow )

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such geometries, as was done in reference 1, it is clear that these geometries should benefit further from fully three-dimensional approaches. effects of viscosity should ultimately be included, the results obtained from a solution of the Euler equations are useful in preliminary design work where information on pressure alone isdesired. Inproblems where heat transfer and skin friction are required, a solution of the boundary-layer equations provides an adequate approximation. But, the outer-edge boundary conditions, including pressure, must be established from the Inviscid solution as the first step in such an analysis (ref. 2). A parabolized Navier-Stokes solver (ref. 3), for instance, uses an Inviscid pressure field as an initial pressure field. Development of a fully three-dimensional inviscid code for turbomachinery flows was reported by Denton (ref. 4), and this code was used for solutions of the Euler equations through blade rows (ref. 5). The method was later improved through the simple nonoverlapping grid and multigrid solution scheme described in references 6 and 7. The version of the code reported in reference 6 was assessed in reference 8 by comparing computed results with experimental data from an axial annular cascade (ref. 9) and from an axial turbine stage (ref.10). Reportedflowanglesandvelocitycomponentsobtainedfromthe inviscid computation by the DENTON code and experiment were in good agreement with the annular cascade data. The DENTON code also gave reasonable agreement for the temperature distribution at the exit of a low-aspect-ratio axial tur­ bine rotor with a nonuniform temperature distribution imposed at the inlet. The code, however, gave substantially different rotor-exit flow-angle d'stri­ butions. An objective of the current effort was to extend the assessment of the DENTON code to a radial turbine configuration. The code was used to analyze' the flow through the radial-inflow turbine rotor described in reference 11 and to compare computed results with experimental data. The rotor blades of this 15.04-cm-diameter radial turbine were designed thick to allow for internal cooling passages and trailing-edge coolant ejection. The test rotor, however, was a solid rotor with no coolant flows involved. Since the experimental pro­ gram was undertaken primarily to determine overall performance, no detailed measurements internal to the rotor passage were made, and the available experi­ mental data are limited to rotor-inlet and -exit surveys. The radial distri­ bution of absolute flow angle and total pressure from the experiment are com­ pared with the computed results. Other computed results are presented inthe form of velocity-vector plots, loading diagrams, and contour plots. puted results are presented without comparison 'because of the lack of experi­ mental data. Some of the flow characteristics are qualitatively compared with analytical results of Bosman and Highton (ref. 12) as well as aquasi-three­ dimensional analysis. EXPERIMENTAL DATA Experimental data from a 15.04-cm-tip-diameter radial-inflow turbine rotor wereobtainedfromreference11. Theactualrotorusedintheexperimentis shown in figure 1. The rotor had 12 full blades that were thick enough to allow internal cooling passages and the trailing-edge ejection of coolant. For the turbine tests reported inthe reference, however, the blading was sol1d. with no coolant ejection. The rotor had unswept radial blades at the inducer. inlet and large blockages (78.7, 38.2, and 14.9 percent at the hub, mean, and tip, respectively) resulting from the thick trailing edges. 2 The test program While the Most com­

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