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Research Papers: Heat Exchangers

Numerical Evaluation of Thermal Hydraulic Performance in Fin-and-Tube Heat Exchangers With Various Vortex Generator Geometries Arranged in Common-Flow-Down or Common-Flow-Up

[+] Author and Article Information
Mohd Fahmi Md Salleh

Faculty of Mechanical Engineering,
Universiti Teknologi MARA,
Cawangan Johor, Kampus Pasir Gudang, Jalan
Purnama, Bandar Seri Alam,
Masai 81750, Johor, Malaysia
e-mail: fahmisalleh@uitm.edu.my

Ahmadali Gholami

High Speed Reacting Flow Laboratory,
School of Mechanical Engineering,
Faculty of Engineering,
Universiti Teknologi Malaysia,
Skudai 81310, Johor Bahru, Malaysia
e-mail: gholamifdg@gmail.com

Mazlan A. Wahid

High Speed Reacting Flow Laboratory,
School of Mechanical Engineering,
Faculty of Engineering,
Universiti Teknologi Malaysia,
Skudai 81310, Johor Bahru, Malaysia
e-mail: mazlan@mail.fkm.utm.my

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF HEAT TRANSFER. Manuscript received March 19, 2018; final manuscript received October 24, 2018; published online December 13, 2018. Assoc. Editor: Danesh K. Tafti.

J. Heat Transfer 141(2), 021801 (Dec 13, 2018) (13 pages) Paper No: HT-18-1158; doi: 10.1115/1.4041832 History: Received March 19, 2018; Revised October 24, 2018

Vortex generator as secondary flow enhancement technique has captured the attention of many researchers recently to augment the performance of the fin-and-tube heat exchanger (FTHE). There are various vortex generator parameters that influence the thermal and hydraulic performance in the FTHE such as the geometry and arrangement. In this study, the effect of different vortex generator geometries and arrangements was investigated using numerical simulation method. There are three vortex generator geometries studied including rectangular winglet (RWVG), delta winglet (DWVG), and trapezoidal winglet (TWVG). The vortex generators were placed behind tubes either in common flow down (CFD) or common flow up (CFU) arrangement. The introduction of vortex generators behind tubes resulted in heat transfer augmentation but comes together with higher pressure drop penalty. Further analysis on the thermal performance has found that TWVG in CFU arrangement almost obtained similar thermal performance factor with respect to the baseline case at Reynolds number 500 and 600. However, the thermal performance factor for TWVG in CFU arrangement decreases as the Reynolds number further increased. For other vortex generator cases, lesser thermal performance factor was found as compared to the baseline case.

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Figures

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Fig. 1

Fin-and-tube heat exchanger geometry (a) top view and (b) front view

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Fig. 4

Comparison of numerical simulation and experimental results of j/jo and f/fo with various Reynolds number

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Fig. 2

The geometry and dimension of (a) DWVG (b) RWVG, and (c) TWVG

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Fig. 3

Vortex generator behind tubes (a) in CFD arrangement (b) in CFU arrangement, and (c) center point location

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Fig. 5

The streamline pattern in the various vortex generator geometry and arrangement at Re = 500 (a) baseline case, (b) RWVG CFD, (c) RWVG CFU, (d) DWVG CFD, (e) DWVG CFU, (f) TWVG CFD, and (g) TWVG CFU

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Fig. 6

Velocity contour for the various vortex generator geometry and arrangement at Re = 500 (a) baseline case, (b) RWVG CFD, (c) RWVG CFU, (d) DWVG CFD, (e) DWVG CFU, (f) TWVG CFD, and (g) TWVG CFU

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Fig. 7

Pressure distribution across the FTHE for various vortex generator geometry and arrangement at Re = 500 (a) baseline case, (b) RWVG CFD, (c) RWVG CFU, (d) DWVG CFD, (e) DWVG CFU, (f) TWVG CFD, and (g) TWVG CFU

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Fig. 8

The temperature contour in the various vortex generator geometry and arrangement at Re = 500 (a) baseline case, (b) RWVG CFD, (c) RWVG CFU, (d) DWVG CFD, (e) DWVG CFU, (f) TWVG CFD, and (g) TWVG CFU

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Fig. 9

Variation of pressure drop versus Reynolds number

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Fig. 10

Fanning friction factor versus Reynolds number

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Fig. 11

Nusselt number variation versus Reynolds number

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Fig. 12

Heat transfer performance factor versus pumping power factor

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Fig. 13

Overall thermal-hydraulic performance versus Reynolds number

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Fig. 14

Thermal performance factor versus Reynolds number

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