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Research Papers

Comparison of Steady and Unsteady RANS Heat Transfer Simulations of Hub and Endwall of a Turbine Blade Passage

[+] Author and Article Information
Lamyaa A. El-Gabry

Department of Mechanical Engineering, The American University in Cairo, New Cairo 11835, Egyptlelgabry@aucegypt.edu

Ali A. Ameri

Department of Aerospace Engineering, The Ohio State University, Columbus, OH 43210

J. Turbomach 133(3), 031010 (Nov 15, 2010) (9 pages) doi:10.1115/1.4002412 History: Received August 27, 2009; Revised May 22, 2010; Published November 15, 2010; Online November 15, 2010

The necessity of performing an unsteady simulation for the purpose of predicting the heat transfer on the endwall surfaces of a turbine passage is addressed. This is measured by the difference between the two solutions obtained from a steady simulation and the time average of an unsteady simulation. The heat transfer coefficient (Nusselt number) based on the adiabatic wall temperature is used as the basis of the comparison. As there is no film cooling in the proposed case, a computed heat transfer coefficient should be a better measure of such difference than, say, a wall heat flux. Results show that the effect of unsteadiness due to wake passage on the pressures and recovery temperatures on both hub and casing is negligible. Heat transfer on the endwalls, however, is affected by the unsteady wake; the time-averaged results yield higher heat transfer; in some regions, up to 15% higher. The results for the endwall heat transfer were compared with results in open literature and were found to be comparable.

Copyright © 2011This material is declared a work of the US government and is not subject to copyright protection in the United States. Approved for public release; distribution is unlimited.
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References

Figures

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Figure 1

The grid on the solid surfaces of the geometry

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Figure 2

(a) Casing surface mesh showing multiblock structure and (b) hub surface mesh showing multiblock structure

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Figure 3

Total temperature (T0) and total pressure (P0) at the blade inlet

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Figure 4

Instantaneous and time-averaged (dashed) hub surface pressure for a wake passing

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Figure 5

Instantaneous and time-averaged (dashed) hub heat transfer distribution for a wake passing

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Figure 6

Time-averaged casing pressure

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Figure 7

Time-averaged hub pressure

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Figure 8

Difference in casing pressure distribution between the time-averaged and steady results

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Figure 9

Difference in hub pressure distribution between the time-averaged and steady results

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Figure 10

Time-averaged casing adiabatic wall temperature

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Figure 11

Time-averaged hub adiabatic wall temperature

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Figure 12

Difference in casing adiabatic wall temperature distribution between the time-averaged and steady results

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Figure 13

Difference in hub adiabatic wall temperature distribution between the time-averaged and steady results

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Figure 14

Time-averaged casing heat transfer rate

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Figure 15

Time-averaged hub heat transfer rate

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Figure 16

Difference in casing heat transfer rate between the time-averaged and steady results

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Figure 17

Difference in hub heat transfer rate between the time-averaged and steady results

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Figure 18

Time-averaged casing Nusselt number

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Figure 19

Time-averaged hub Nusselt number

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Figure 20

Difference in casing Nusselt number between the time-averaged and steady results

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Figure 21

Difference in hub Nusselt number between the time-averaged and steady results

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Figure 22

Measured heat flux on casing surface (29)

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Figure 23

Predicted Stanton number on hub surface of Tallman (21)

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Figure 24

Predicted Nusslet number on the hub surface of E3 blade (similar to Fig. 1)

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