RESEARCH PAPERS: Heat Exchangers

Air Flow and Heat Transfer in Louver-Fin Round-Tube Heat Exchangers

[+] Author and Article Information
H. L. Wu1

 Advanced Heat Transfer LLC, 1715 Aaron Brenner Drive, Suite 726, Memphis, TN 38120hailingwu̱02@yahoo.com

Y. Gong, X. Zhu

 Advanced Heat Transfer LLC, 1715 Aaron Brenner Drive, Suite 726, Memphis, TN 38120


Corresponding author.

J. Heat Transfer 129(2), 200-210 (May 21, 2006) (11 pages) doi:10.1115/1.2402180 History: Received September 09, 2005; Revised May 21, 2006

Experimental investigations were conducted to understand the air flow and heat transfer in louver-fin round-tube two-row two-pass cross-counterflow heat exchangers. The Colburn factor j and friction factor f were obtained by using the ε-NTU approach. A three-dimensional computational fluid dynamics model was developed based on a representative unit cell with periodical and symmetric boundary conditions. Analysis of tube-side circuiting effect has been conducted and showed improvement by applying overall nonlinear tube-side fluid temperature boundary conditions. Comparison of heat transfer rate of the first and second rows showed that the first row was much more effective, achieving 6853% of the total heat transfer rate, when air velocity changes from 1.02msto2.54ms. A dimensionless parameter, F, was introduced to describe the louver interaction for different fin designs with various louver angles. Using jf13 as a criterion to evaluate the heat transfer and pressure loss performance, an optimal F was predicted around 0.62.

Copyright © 2007 by American Society of Mechanical Engineers
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Figure 1

Experimental facility: (a) sketch 3map of the test facility; and (b) circuiting

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Figure 2

Fin configurations: (a) core section; (b) isometric view; and (c) side view

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Figure 4

The Colburn factor j and friction factor f versus Reo

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Figure 5

Computational domain and grids: (a) computational domain (top view); and (b) fin geometry and periodical boundary; and (c) meshes near louver corners

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Figure 6

Water temperature profiles along the circuit: (a) circuiting; and (b) water temperature profiles

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Figure 7

Top views of streamlines released from line MN in the midplane between two fins (Note: higher uin produces recirculation loop): (a) case 1, uin=1.017m∕s; and (b) case 7, uin=2.542m∕s

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Figure 8

Contours of heat flux and wall temperature: (a) heat flux; and (b) wall temperature

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Figure 11

The four fin designs and geometric parameters: (a) Fin A; (b) Fin B; (c) Fin C; (d) Fin D; and (e) geometric relationship.

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Figure 12

Performance of the four fin designs: (a) j′ versus F; (b) f versus F; and (c) j′∕fx(x=1∕3,1) versus F

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Figure 13

Influence of louver interaction on pressure field and streamline pattern: (a) Fin B; and (b) Fin C

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Figure 3

ε-NTU relationships for two-row two-pass cross counterflow heat exchangers

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Figure 10

Profiles of: (a) segment-area-averaged heat flux qw,seg; and (b) segment-area-averaged heat transfer coefficient ho,seg

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Figure 9

Flow pattern through louver fins (Case 1): (a) side view of streamline pattern; and (b) streamlines in representative louver sections (two rows shown)




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