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Research Papers

Investigation of Leakage Flow and Heat Transfer in a Gas Turbine Blade Tip With Emphasis on the Effect of Rotation

[+] Author and Article Information
Dianliang Yang, Xiaobing Yu

Institute of Turbomachinery, Xi’an Jiaotong University, Xi’an 710049, P.R.C.

Zhenping Feng

Institute of Turbomachinery, Xi’an Jiaotong University, Xi’an 710049, P.R.C.zpfeng@mail.xjtu.edu.cn

J. Turbomach 132(4), 041010 (May 04, 2010) (9 pages) doi:10.1115/1.3213560 History: Received April 01, 2009; Revised April 21, 2009; Published May 04, 2010; Online May 04, 2010

Numerical analysis was applied to investigate the effect of rotation on the blade tip leakage flow and heat transfer. Flows around both flat and squealer tips at the first stage rotor blade of GE E3 high-pressure turbine were studied. The tip gap and squealer groove depth were specified as 1% and 2% of the blade height, respectively. The heat transfer coefficient on the tip surface was obtained by using different turbulence models and compared with the experimental data. The grid independence study was also carried out by using the Richardson extrapolation method. The effect of the blade rotation was studied in the following cases: (1) the blade domain is rotating and the shroud is stationary; (2) the blade domain is stationary and the shroud is rotating; and (3) both blade domain and shroud are stationary. In this approach, the effects of the relative motion of the endwall, the centrifugal force, and the Coriolis force can be investigated, respectively. By comparing the results of the three cases discussed, it is concluded that the main effect of the rotation on the tip leakage flow and heat transfer resulted from the relative motion of the shroud, especially for the squealer tip blade.

Copyright © 2010 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

Grid distribution for the squealer tip

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Figure 2

Detailed boundary conditions for all cases: (a) inlet total pressure, (b) inlet total temperature, (c) inlet angle, and (d) outlet static pressure

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Figure 3

Comparison of the heat transfer coefficients between experimental and predicted results: (a) experiment result, (b) standard κ-ε model, (c) RNG κ-ε model, (d) low Re κ-ω model, and (e) SST κ-ω model

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Figure 4

Heat transfer coefficient distributions and surface streamlines on the tip: (a) 0.8 million, (b) 1.1 million, (c) 1.47 million, and (d) 2.5 million

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Figure 5

The secondary flow streamlines around the flat tip at various axial locations (left is the pressure side): (a) DRSS, 20% axial chord, (b) DSSR, 20% axial chord, (c) DSSS, 20% axial chord, (d) DRSS, 50% axial chord, (e) DSSR, 50% axial chord, (f) DSSS, 50% axial chord, (g) DRSS, 80% axial chord, (h) DSSR, 80% axial chord, and (i) DSSS, 80% axial chord

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Figure 6

Surface streamlines and velocity magnitude contours on the middle plane between the tip and shroud for the flat tip cases: (a) DRSS, (b) DSSR, and (c) DSSS

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Figure 7

The pressure distributions on the blade surface for the flat tip cases: (a) midspan and (b) near the tip

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Figure 8

The pressure contours on the shroud surface for the flat tip cases: (a) DRSS, (b) DSSR, and (c) DSSS

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Figure 9

The heat transfer coefficient contours on the flat tip: (a) DRSS, (b) DSSR, and (c) DSSS

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Figure 10

The heat transfer coefficient contours on the suction surface of the flat tip blade: (a) DRSS, (b) DSSR, and (c) DSSS

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Figure 11

View of the secondary velocity vectors around the squealer tip at various axial locations (left is the pressure side): (a) DRSS, 25% axial chord; (b) DSSR, 25% axial chord; (c) DSSS, 25% axial chord; (d) DRSS, 50% axial chord; (e) DSSR, 50% axial chord; (f) DSSS, 50% axial chord; (g) DRSS, 75% axial chord; (h) DSSR, 75% axial chord; and (i) DSSS, 75% axial chord

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Figure 12

The surface streamlines and velocity magnitude contours on the middle plane between the tip and shroud for the squealer tip cases: (a) DRSS, (b) DSSR, and (c) DSSS

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Figure 13

The pressure distributions on the blade surface for the squealer tip cases: (a) midspan and (b) near tip

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Figure 14

The pressure contours on the shroud surface for the squealer tip cases: (a) DRSS, (b) DSSR, and (c) DSSS

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Figure 15

The heat transfer coefficient contours on the squealer tip: (a) DRSS, (b) DSSR, and (c) DSSS

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Figure 16

The heat transfer coefficient contours on the suction surface of the squealer tip blade: (a) DRSS, (b) DSSR, and (c) DSSS

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