Research Papers

Experimental and Numerical Investigation of the Gas Side Heat Transfer and Pressure Drop of Finned Tubes—Part II: Numerical Analysis

[+] Author and Article Information
Rene Hofmann

Josef Bertsch GmbH & Co. KG,
Herrengasse 23,
A-6700 Bludenz, Austria
e-mail: rene.hofmann@bertsch.at

Heimo Walter

Institute for Energy Systems and Thermodynamics,
Vienna University of Technology,
Getreidemarkt 9,
A-1060 Vienna, Austria
e-mail: heimo.walter@tuwien.ac.at

Manuscript received February 27, 2012; final manuscript received June 16, 2012; published online October 17, 2012. Assoc. Editor: Larry Swanson.

J. Thermal Sci. Eng. Appl 4(4), 041008 (Oct 17, 2012) (11 pages) doi:10.1115/1.4007125 History: Received February 27, 2012; Revised June 16, 2012

The heat transfer and pressure drop behavior of segmented circular and helical as well as solid finned tubes are investigated in a three-dimensional numerical study. The simulation is carried out using a finite volume method for calculating the steady-state temperature and flow field of the fluid as well as the temperature distribution of the tube material. For modeling the turbulence, the k-ε turbulence model based on the renormalization group theory (RNG) is used to resolve the near-wall treatment between adjacent fins. All simulations are performed in the Re range between 3500 ≤ Re ≤ 50,000. The influence of Reynolds number and fin geometry (segmented or solid and circular or helical) on the local and global averaged heat transfer and pressure drop was studied. A comparison between solid and segmented finned tube has shown that the heat transfer and pressure drop for the segmented finned tubes is higher. The numerical results are compared with experimental data.

Copyright © 2012 by ASME
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Fig. 5

Part of the calculation grid of the segmented circular I-finned tube

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Fig. 6

Averaged heat transfer for a single finned tube row in cross flow

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Fig. 1

y-z-sketch of the segmented circular I-finned and U-finned tube as well as of the helical solid finned tube

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Fig. 2

x-y-sketch of the segmented circular finned tubes, whereby D = dA + 2hf

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Fig. 3

Sketch of the helical segmented I-finned tube

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Fig. 4

x-y-sketch of the helical segmented I-finned tube, whereby D = dA + 2hf

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Fig. 8

Velocity magnitudes between adjacent circular segmented I-finned tube at uin = 5 m/s

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Fig. 9

Contours of the local temperature distribution above the fin surface for a circular solid and a segmented finned tube at uin = 5 m/s

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Fig. 10

Contour of the local temperature distribution of a fin and fluid for a circular segmented finned tube whererby (a) uin = 1.5 m/s and (b) uin = 5 m/s

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Fig. 11

Circumferentially averaged heat transfer coefficient at uin = 5 m/s and uin = 7 m/s

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Fig. 7

Possible path lines with local velocities upstream and downstream from a helical segmented I-finned tube

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Fig. 12

Relative circumferentially averaged heat transfer coefficient at uin = 5 m/s and uin = 7 m/s

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Fig. 13

Averaged radial heat transfer coefficient with a discrete angle at uin = 5 m/s and uin = 9 m/s

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Fig. 14

Pressure drop coefficient ξ1R for a single finned tube row in cross flow

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Fig. 15

Comparison between Nu-correlation, experimental, and numerical data for segmented I-finned and U-finned tubes [5]

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Fig. 16

Comparison between the Nu number and the experimental and numerical data (the data denoted by an asterisk are converted with a row correction factor of 0.638)

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Fig. 17

Comparison between the experimental and numerical data for the pressure drop coefficient ξ1R



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