0
Research Papers: Heat Transfer Enhancement

Numerical Analysis of Flow Structure and Heat Transfer Characteristics in Dimpled Channels With Secondary Protrusions

[+] Author and Article Information
Yonghui Xie

School of Energy and Power Engineering,
Xi’an Jiaotong University,
Xi’an, Shaanxi 710049, China
e-mail: yhxie@mail.xjtu.edu.cn

Zhongyang Shen

School of Energy and Power Engineering,
Xi’an Jiaotong University,
Xi’an, Shaanxi 710049, China
e-mail: szy_xjtu@163.com

Di Zhang

Key Laboratory of Thermo-Fluid
Science and Engineering,
Ministry of Education,
School of Energy and Power Engineering,
Xi’an Jiaotong University,
Xi’an, Shaanxi 710049, China
e-mail: zhang_di@mail.xjtu.edu.cn

Phillip Ligrani

Department of Mechanical
and Aerospace Engineering,
University of Alabama in Huntsville,
Huntsville, AL 35899
e-mail: phillip.ligrani@uah.edu

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF HEAT TRANSFER. Manuscript received January 10, 2014; final manuscript received October 12, 2015; published online November 11, 2015. Assoc. Editor: Keith Hollingsworth.

J. Heat Transfer 138(3), 031901 (Nov 11, 2015) (6 pages) Paper No: HT-14-1014; doi: 10.1115/1.4031787 History: Received January 10, 2014; Revised October 12, 2015

Dimple structure is an effective heat transfer augmentation approach on coolant channel due to its advantage on pressure penalty. The implication of secondary protrusion, which indicates protrusion with smaller dimension than dimple, will intensify the Nusselt number Nu inside dimple cavity without obvious extra pressure penalty. The objective of this study is to numerically analyze the combination effect of dimples and secondary protrusion. Different protrusion–dimple configurations including protrusion print-diameter Dp, protrusion–dimple gap P, and staggered angle α are investigated. From the results, it is concluded that the implication of secondary protrusion will considerably increase the heat transfer rates inside dimple cavity. Cases 4 and 6 possess the highest Nusselt number enhancement ratio Nu/Nu0 reaching up to 2.1–2.2. The additional pressure penalty brought by the protrusion is within 15% resulting in total friction ratio f/f0 among the range of 1.9–2.1. Dimpled channels with secondary protrusions possess higher thermal performance factor TP, defined as (Nu/Nu0)/(f/f0)1/3, among which cases 4 and 6 are the optimal structures. Besides this, the TP of protrusion–dimple channels are comparable to the other typical heat transfer devices, and higher TP can be speculated after a more optimal dimple shape or combination with ribs and fins.

FIGURES IN THIS ARTICLE
<>
Copyright © 2016 by ASME
Your Session has timed out. Please sign back in to continue.

References

Lau, S. C. , McMillin, R. D. , and Han, J. C. , 1991, “ Heat Transfer Characteristics of Turbulent Flow in a Square Channel With Angled Discrete Ribs,” ASME J. Turbomach., 113(3), pp. 367–374. [CrossRef]
Han, J. C. , 1988, “ Heat Transfer and Friction Characteristics in Rectangular Channels With Rib Turbulators,” ASME J. Heat Transfer, 110(2), pp. 321–328. [CrossRef]
Zhang, Y. M. , Gu, W. Z. , and Han, J. C. , 1994, “ Heat Transfer and Friction in Rectangular Channels With Ribbed or Ribbed-Grooved Walls,” ASME J. Heat Transfer, 116(1), pp. 58–65. [CrossRef]
Ligrani, P. M. , and Mahmood, G. I. , 2003, “ Spatially Resolved Heat Transfer and Friction Factors in a Rectangular Channel With 45-Deg Angled Crossed-Rib Turbulators,” ASME J. Turbomach., 125(3), pp. 575–585. [CrossRef]
Ligrani, P. M. , Oliveira, M. M. , and Blaskovich, T. , 2003, “ Comparison of Heat Augmentation Techniques,” AIAA J., 41(3), pp. 337–362. [CrossRef]
Afanasyev, V. N. , Chudnovsky, Y. P. , and Leontiev, A. I. , 1993, “ Turbulent Flow Friction and Heat Transfer Characteristics for Spherical Cavities on a Flat Plate,” Exp. Therm. Fluid Sci., 7(1), pp. 1–8. [CrossRef]
Griffith, T. S. , Luai, A. , and Han, J. , 2003, “ Heat Transfer in Rotating Rectangular Cooling Channels (AR = 4) With Dimples,” ASME J. Turbomach., 125(3), pp. 555–564. [CrossRef]
Elyyan, M. A. , and Danesh, K. T. , 2010, “ Effect of Coriolis Forces in a Rotating Channel With Dimples and Protrusions,” Int. J. Heat Fluid Flow, 31(1), pp. 1–18. [CrossRef]
Elyyan, M. A. , and Danesh, K. T. , 2012, “ Investigation of Coriolis Forces Effect of Flow Structure and Heat Transfer Distribution in a Rotating Dimpled Channel,” ASME J. Turbomach., 134(3), pp. 1–8. [CrossRef]
Ligrani, P. M. , Harrison, J. L. , and Mahmmod, G. I. , 2001, “ Flow Structure Due to Dimple Depressions on a Channel Surface,” Phys. Fluids, 13(11), pp. 3442–3451. [CrossRef]
Ligrani, P. M. , Mahmood, G. I. , Harrison, J. L. , Clayton, C. M. , and Nelson, D. L. , 2001, “ Flow Structure and Local Nusselt Number Variation in a Channel With Dimples and Protrusions on Opposite Walls,” Int. J. Heat Mass Transfer, 44(23), pp. 4413–4425. [CrossRef]
Mahmood, G. I. , Sabbagh, M. Z. , and Ligrani, P. M. , 2001, “ Heat Transfer in a Channel With Dimples and Protrusions on Opposite Walls,” J. Thermophys. Heat Transfer, 15(3), pp. 275–283. [CrossRef]
Burgess, N. K. , and Ligrani, P. M. , 2005, “ Effects of Dimple Depth on Channel Nusselt Numbers and Friction Factors,” ASME J. Heat Transfer, 127(8), pp. 839–847. [CrossRef]
Elyyan, M. A. , and Tafti, D. K. , 2012, “ Investigation of Coriolis Forces Effect of Flow Structure and Heat Transfer Distribution in a Rotating Dimpled Channel,” ASME J. Turbomach., 134(3), p. 031007. [CrossRef]
Alshroof, O. , Reizes, J. , Timchenko, V. , and Leonardi, E. , 2009, “ Flow Structure and Heat Transfer Enhancement in Laminar Flow With Protrusions–Dimple Combinations in a Shallow Rectangular Channel,” ASME Paper No. HT2009-88251.
Hwang, S. D. , Kwon, H. G. , and Cho, H. H. , 2010, “ Local Heat Transfer and Thermal Performance on Periodically Dimple–Protrusion Patterned Walls for Compact Heat Exchangers,” Energy, 35(12), pp. 5357–5364. [CrossRef]
Chang, S. W. , Chiang, K. F. , and Chou, T. C. , 2010, “ Heat Transfer and Pressure Drop in Hexagonal Ducts With Surface Dimples,” Exp. Therm. Fluid Sci., 34(8), pp. 1172–1181. [CrossRef]
Han, J. C. , Zhang, Y. M. , and Lee, C. P. , 1991, “ Augmented Heat Transfer in Square Channels With Parallel, Crossed and V-Shaped Angled Ribs,” ASME J. Heat Transfer, 113(3), pp. 590–596. [CrossRef]
Taslim, M. E. , Li, T. , and Kercher, D. , 1996, “ Experimental Heat Transfer and Friction in Channels Roughened With Angle, V-Shaped and Discrete Ribs on Two Opposite Walls,” ASME J. Turbomach., 118(1), pp. 20–28. [CrossRef]
Chyu, M. K. , Yu, Y. , Ding, H. , Downs, J. P. , and Soechting, F. O. , 1997, “ Concavity Enhanced Heat Transfer in an Internal Cooling Passage,” ASME Paper No. 97-GT-437.
Shen, Z. Y. , Qu, H. C. , Zhang, D. , and Xie, Y. H. , 2013, “ Effect of Bleed Hole on Flow and Heat Transfer Performance of U-Shaped Channel With Dimple Structure,” Int. J. Heat Mass Transfer, 66, pp. 10–22. [CrossRef]

Figures

Grahic Jump Location
Fig. 1

A schematic diagram of the investigated rectangular channel

Grahic Jump Location
Fig. 2

Detailed descriptions of channel dimensions

Grahic Jump Location
Fig. 3

Schematics of mesh details: (a) inline arrangement and (b) staggered arrangement

Grahic Jump Location
Fig. 4

Comparison of the calculated results with different turbulence model: (a) Nu versus Re and (b) f/f0 versus Re

Grahic Jump Location
Fig. 5

Typical flow patterns of protrusion–dimpled channel: (a) flow insight and special region, (b) streamlines in zone 1, and (c) streamlines in zone 2

Grahic Jump Location
Fig. 6

Streamlines and velocity contours above the protrusion and dimple surfaces: (a) case 1, (b) case 3, (c) case 4, and (d)case 8

Grahic Jump Location
Fig. 7

Local Nusselt number ratio for (a) case 1, (b) case 4, (c) case 3, and (d) case 8

Grahic Jump Location
Fig. 8

Average Nu/Nu0 profiles for all cases (Nu0 indicates the baseline Nusselt number by the equation)

Grahic Jump Location
Fig. 9

Average f/f0 profiles for all cases (f0 indicates the baseline friction coefficient by the equation)

Grahic Jump Location
Fig. 10

Thermal performances of representative cases in the present study and other typical heat transfer devices

Tables

Errata

Discussions

Some tools below are only available to our subscribers or users with an online account.

Related Content

Customize your page view by dragging and repositioning the boxes below.

Related Journal Articles
Related eBook Content
Topic Collections

Sorry! You do not have access to this content. For assistance or to subscribe, please contact us:

  • TELEPHONE: 1-800-843-2763 (Toll-free in the USA)
  • EMAIL: asmedigitalcollection@asme.org
Sign In