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TECHNICAL PAPERS

Quantitative Visualization of the Flow in a Centrifugal Pump With Diffuser Vanes—II: Addressing Passage-Averaged and Large-Eddy Simulation Modeling Issues in Turbomachinery Flows

[+] Author and Article Information
Manish Sinha, Joseph Katz, Charles Meneveau

Department of Mechanical Engineering, The Johns Hopkins University, Baltimore, MD 21218

J. Fluids Eng 122(1), 108-116 (Nov 17, 1999) (9 pages) doi:10.1115/1.483232 History: Received January 08, 1999; Revised November 17, 1999
Copyright © 2000 by ASME
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References

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Rhie, C. M., Gleixner, A. J., Spear, D. A., Fischberg, C. J., and Zacharias, R. M., 1995, “Development and Application of a Multistage Navier-Stokes Solver. Part A: Multistage Modeling Using Body Forces and Deterministic Stresses,” ASME Int. Gas Turbine and Aeroengine Congress and Exposition, 95-GT-342.
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Dong,  R., Chu,  S., and Katz,  J., 1992, “Quantitative Visualization of The Flow Structure Within the Volute of a Centrifugal Pump, Part B: Results And Analysis,” ASME J. Fluids Eng., 114, p. 390.
Dong,  R. , 1997, “Effect of Modification to Tongue and Impeller Geometry on Unsteady Flow, Pressure Fluctuations and Noise in a Centrifugal Pump,” ASME J. Turbomach., 119, p. 506.
Chu,  S., Dong,  R., and Katz,  J., 1995, “Relationship Between Unsteady Flow, Pressure Fluctuations and Noise In A Centrifugal Pump. Part A: Use of PIV Data To Compute The Pressure Field,” ASME J. Fluids Eng., 117, p. 24.
Chu,  S., Dong,  R., and Katz,  J., 1995, “Relationship Between Unsteady Flow, Pressure Fluctuations and Noise In A Centrifugal Pump. Part B: Effect of Blade-Tongue Interaction,” ASME J. Fluids Eng., 117, p. 30.
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Figures

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The pump geometry. The blade tip in sample area is at 206 deg phase.
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(a) Passage averaged velocity field in the stator reference frame. Contours represent velocity magnitude. (b) Distribution of deterministic kinetic energy, k*S det(x).
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(right column) (a) An example of matched profiles acquired from phases 206 deg and 246 deg of the impeller. (b) Passage averaged velocity field in the impeller reference frame. For clarity we do not add Ωr to the circumferential velocity. Above the red dashed line all the data involves averaging of the same number of phase averaged distributions. (c) Distribution of deterministic kinetic energy, k*R det(x,t) (impeller reference frame).
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Distribution of k*turb(x,t) at a phase of 226 deg
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Distribution of deterministic shear stresses. The gray and white areas denote negative and positive shear stresses, respectively. The normalized deterministic shear stress (τ12det/ut2) contours are plotted in increments of 0.25×10−3.
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Distribution of Reynolds shear stress based on phase averaging at 226 deg
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Instantaneous distribution of SGS shear stress (τ12smag×103/Ut2) obtained from spatial filtering at scale=6.3 mm. The phase angle is 226 deg
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Instantaneous distribution of SGS shear stress (τ12smag×103/Ut2) as predicted by the Smagorinsky model, for same filter scale and phase angle as Fig. 7
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Filtered vorticity distribution of a single realization at same scale and phase angle as Fig. 7
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Unfiltered vorticity distribution of same single realization as Figs. 7, 8, and 9
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Filtered strain-rate distribution of same realization
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Filtered strain-rate distribution of a different realization at phase angle of 226 deg
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Distribution of SGS dissipation for a single realization at the same scale and phase as Fig. 7. The physical interpretation of this variable is as flux of kinetic energy from large to small scale (when positive). Negative regions denote backscatter.
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Phase-averaged distribution of SGS dissipation at the same scale and phase as Fig. 13
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Subgrid stresses (τ12), derived using a 12×12 filter on a 128×128 vector map for flow in a jet
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Subgrid stresses (τ12), derived using a 3×3 filter on the prefiltered (4×4 filter) vector map. The computation is for the same realization of unfiltered velocity field as in Fig. 15.

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