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Research Papers: Heat Exchangers

Performance of Gas-to-Gas Micro-Heat Exchangers

[+] Author and Article Information
J. Miwa

Department of Mechanical Engineering, Tokyo Metropolitan University, Hachioji, Tokyo, 192-0397, Japan

Y. Asako1

Department of Mechanical Engineering, Tokyo Metropolitan University, Hachioji, Tokyo, 192-0397, Japanasako@tmu.ac.jp

C. Hong

Department of Mechanical Engineering, Tokyo University of Science, Yamazaki, Noda, Chiba, 278-8501, Japan

M. Faghri

Department of Mechanical Engineering and Applied Mechanics, University of Rhode Island, Kingston, RI 02881-0805

1

Corresponding author.

J. Heat Transfer 131(5), 051801 (Mar 18, 2009) (9 pages) doi:10.1115/1.3013828 History: Received January 25, 2008; Revised September 30, 2008; Published March 18, 2009

Heat transfer performance of two-stream parallel and counter-flow gas-to-gas micro-heat exchangers are investigated numerically. Flow passages are plane channels with heights in the range of 10100μm and selected lengths of 12.7mm and 25.4mm. Numerical methodology is based on the arbitrary-Lagrangian-Eulerian method. Computations were performed to find the effects of capacity ratio, channel height, and length on the heat transfer characteristics of micro-heat exchangers. To results are presented in the form of temperature contours, bulk temperatures, total temperatures, and heat flux variation along the channel. It was found that the temperature inversion occurs under certain conditions. Also, the effectiveness and the number of transfer units approach and the estimation of the heat exchange rate were discussed. The range of parameters where the predicted effectiveness agrees with the numerical result were investigated.

Copyright © 2009 by American Society of Mechanical Engineers
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Figures

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Figure 1

A schematic of a problem (a) parallel-flow (b) counter-flow

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Figure 2

Contour plots of temperature (h=50μm and L=12.7mm); (a) ReH=168.7(MaoutH=0.081) and ReC=170.5(MaoutC=0.082), (b) ReH=177.4(MaoutH=0.082) and ReC=1458.5(MaoutC=0.643), (c) ReH=1326.4(MaoutH=0.622) and ReC=163.6(MaoutC=0.080), and (d) ReH=1360.2(MaoutH=0.625) and ReC=1425.0(MaoutC=0.641)

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Figure 3

Bulk temperature for h=50μm and L=12.7mm

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Figure 4

Heat flux from hot passage to cold passage for case of Fig. 2

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Figure 5

Total temperature for h=50μm and L=12.7mm

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Figure 6

Temperature contour near outlet for h=10μm, L=25.4mm, ReH=26.1(MaoutH=0.06), and ReC=416.4(MaoutC=0.792)

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Figure 7

Effectiveness ε as a function of Ntu

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Figure 8

Ratio of estimated effectiveness and the simulated result εest∕εsim as a function of Rc

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Figure 9

Contour plots of temperature for parallel-flows (h=50μm and L=12.7mm); (a) ReH=168.4(MaoutH=0.079) and ReC=171.0(MaoutC=0.084), (b), ReH=180.0(MaoutH=0.083) and ReC=1472.0(MaoutC=0.643), (c) ReH=1320.0(MaoutH=0.671) and ReC=162.3(MaoutC=0.081), and (d) ReH=1360.9(MaoutH=0.621) and ReC=1430.4(MaoutC=0.640)

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Figure 10

Bulk temperature for h=50μm and L=12.7mm

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Figure 11

Heat flux from hot passage to cold passage for case (c) of L=12.7mm

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Figure 12

Total temperature for h=50μm and L=12.7mm

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Figure 13

Temperature contour near x=0 of Fig. 1 (h=50μm and L=12.7mm) [ReH=180.0(MaoutH=0.083) and ReC=1472.0(MaoutC=0.643)]

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Figure 14

Total temperature and temperature contour near x=L for h=10μm and L=12.7mm [ReH=352.0(MaoutH=0.0747) and ReC=65.6(MaoutC=0.162)]; (a) total temperature (b) temperature contour

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Figure 15

Effectiveness ε as a function of Ntu

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Figure 16

Ratio of estimated effectiveness and the simulated result εest∕εsim as a function of Rc

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