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Research Papers: Heat Transfer Enhancement

Local Heat/Mass Transfer and Friction Loss Measurement in a Rotating Matrix Cooling Channel

[+] Author and Article Information
In Taek Oh, Kyung Min Kim, Dong Hyun Lee, Jun Su Park

Department of Mechanical Engineering,  Yonsei University, Seoul 120-749, Koreahhcho@yonsei.ac.kr

Hyung Hee Cho1

Department of Mechanical Engineering,  Yonsei University, Seoul 120-749, Koreahhcho@yonsei.ac.kr

1

Corresponding author.

J. Heat Transfer 134(1), 011901 (Oct 27, 2011) (9 pages) doi:10.1115/1.4004853 History: Received August 30, 2010; Accepted August 12, 2011; Published October 27, 2011; Online October 27, 2011

The present investigation provides detailed local heat/mass transfer and pressure drop characteristics in a matrix cooling channel, under rotating conditions. The matrix channel had cooling subpassages with crossing angles of 45 deg. The detailed heat/mass transfer coefficients were measured via the naphthalene sublimation method, and pressure drops were also obtained. The experiments were conducted for various Reynolds numbers (10,500 to 44,000) and rotation numbers (0.0 to 0.8). In the stationary case, the heat transfer characteristics were dominated by turning, impinging, and swirling flow, induced by the matrix channel geometry. Average heat/mass transfer coefficients on the leading and trailing surfaces in the stationary channel were approximately 2.1 times greater than those in a smooth channel. In the rotating cases, the effect of rotation on heat/mass transfer characteristics differed from that of typical rotating channels with radially outward flow. As the rotation number increased, the Sherwood number ratios increased on the leading surfaces but changed only slightly on the trailing surfaces. The thermal performance factors increased with rotation number due to the increased Sherwood number ratios and decreased friction factor ratios.

Copyright © 2012 by American Society of Mechanical Engineers
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Figures

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Figure 11

Line-averaged ShL /Sh0 ratio distributions in the middle region (channel 8) at Ro = 0.4 with various Reynolds numbers; (a) trailing surface (pressure side), (b) leading surface (suction side)

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Figure 12

Friction factor ratios for various rotation and Reynolds numbers

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Figure 13

Thermal performance factors for various rotation numbers

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Figure 14

Sh/Sh0 in the various cooling method cases; (a) trailing surface (pressure side), (b) leading surface (suction side)

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Figure 15

Friction factor ratios in the various cooling method cases

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Figure 16

Thermal performance in the various cooling method cases; (a) trailing surface (pressure side), (b) leading surface (suction side)

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Figure 1

Schematic view of experimental apparatus [14]

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Figure 2

Geometry of the test channel

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Figure 3

Geometry parameters of matrix channel

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Figure 4

Subchannel numbers of the test section; (a) trailing surface (pressure side), (b) leading surface (suction side)

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Figure 5

Contour plots of Sh/Sh0 at Re = 44,000 in the stationary case (Ro = 0.0); (a) trailing surface (pressure side), (b) leading surface (suction side)

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Figure 6

Line-averaged ShL /Sh0 in the middle region (channel 5) at Ro = 0.0 for various Reynolds numbers; (a) trailing surface (pressure side) (b) leading surface (suction side)

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Figure 7

Predicted vector plot along the center plane of a subchannel

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Figure 8

Contour plots of Sh/Sh0 at Re = 44,000 for various rotation numbers; (a) Ro = 0.2 (trailing surface), (b) Ro = 0.2 (leading surface); (c) Ro = 0.4 (trailing surface), (d) Ro = 0.4 (leading surface)

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Figure 9

Line-averaged ShL /Sh0 distributions in the middle region on leading surface (channel 8) for various rotation numbers; (a) Re = 10,500, (b) Re = 44,000

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Figure 10

Line-averaged ShL /Sh0 distributions in the middle region on trailing surface (channel 8) for various rotation numbers; (a) Re = 10,500 (b) Re = 44,000

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