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Research Papers

Correlation-Based Riblet Model for Turbomachinery Applications

[+] Author and Article Information
Viktor Koepplin

Institute of Turbomachinery and Fluid Dynamics,
Leibniz Universität Hannover,
Appelstr. 9, 30167, Hannover, Germany
e-mail: koepplin@tfd.uni-hannover.de

Florian Herbst

Institute of Turbomachinery and Fluid Dynamics,
Leibniz Universität Hannover,
Appelstr. 9, 30167, Hannover, Germany
e-mail: herbst@tfd.uni-hannover.de

Joerg R. Seume

Institute of Turbomachinery and Fluid Dynamics,
Leibniz Universität Hannover,
Appelstr. 9, 30167, Hannover, Germany
e-mail: seume@tfd.uni-hannover.de

1Corresponding author.

Contributed by the International Gas Turbine Institute (IGTI) of ASME for publication in the JOURNAL OF TURBOMACHINERY. Manuscript received August 9, 2016; final manuscript received December 7, 2016; published online February 28, 2017. Assoc. Editor: Dr. Cengiz Camci.

J. Turbomach 139(7), 071006 (Feb 28, 2017) (10 pages) Paper No: TURBO-16-1190; doi: 10.1115/1.4035605 History: Received August 09, 2016; Revised December 07, 2016

An empirical riblet model for manufactured V-shaped and trapezoidal riblets which is suitable for turbomachinery application is presented. The implementation of the riblet effect employs a correlation-based correction for the damping of the specific dissipation rate ω in the vicinity of the wall which has been previously presented by other researchers. In the current paper, the correlations are extended into the drag-increasing regime and are extended to account for the effect of misalignment of the riblets relative to the flow and for the effect of adverse pressure gradients. In order to account for the latter in modern, massive parallel Reynolds-averaged Navier–Stokes (RANS) codes, a local Clauser parameter has been newly derived. The model is implemented in a three-dimensional (3D) turbomachinery design code and validated with flat plate measurement data and a NACA6510 compressor cascade. The predictions of the experimental values are in very good agreement with the experimental data, showing the capability of the model for designing riblet structured turbomachinery blading.

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References

Figures

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Fig. 1

Flow visualization of turbulent near-wall flow structures in the cross-sectional view (Lee and Lee [3]): (a) near-wall vortex over smooth surface and (b) near-wall vortex over ribbed surface in case of drag decreasing

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Fig. 2

Effect of misalignment: Comparison of numerical approximation Eq. (16) with experimental data of Hage [8] left: trapezoidal riblets and right: V-shaped riblets

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Fig. 3

Corrected and uncorrected functions of ΔU+ in the drag increasing regime for two different riblet-geometries

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Fig. 4

Amplification of the riblet-effect due to adverse pressure gradient

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Fig. 5

Global versus local Clauser parameter in the turbulent boundary layer on the suction side of the NACA6510 profile

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Fig. 6

Numerical setup of the flat plate test case according to Sawyer and Winter [7] (LE:leading edge, TE: trailing edge; every second grid line shown)

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Fig. 7

Skin friction coefficient versus unit Reynolds number. Comparison of the riblet-model with experimental data of Sawyer and Winter [7] and riblet-model of Aupoix et al. [34], V-shaped riblets, left: h = 0.39 mm s/h = 1.28 right: h = 0.48 mm, s/h = 2.08

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Fig. 8

Definition of geometrical parameters of the NACA6510 test profile [52]

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Fig. 9

Blocking, mesh, geometrical details, and reference positions of the NACA6510 cascade setup (every third grid line shown)

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Fig. 10

Calculated versus experimental results. Left: integral loss reduction. Right: change in exit flow angle.

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Fig. 11

Calculated versus experimental loss reduction for different misalignment angles of the riblet structures

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