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Research Papers: Forced Convection

Laminar Forced Convection Flow Past an In-Line Elliptical Cylinder Array With Inclination

[+] Author and Article Information
Esam M. Alawadhi

Department of Mechanical Engineering, Kuwait University, P.O. Box 5969, Safat, 13060 Kuwaitesam@kuc01.kuniv.edu.kw

J. Heat Transfer 132(7), 071701 (Apr 22, 2010) (10 pages) doi:10.1115/1.4000061 History: Received December 13, 2008; Revised July 23, 2009; Published April 22, 2010; Online April 22, 2010

Laminar forced convection flow past an in-line elliptical cylinder array with inclination is simulated using the finite element method. The inclination of the elliptical cylinders is increased with the number of the cylinder in the array, 0 deg for the first cylinder and 90 deg for the last cylinder. The global objective of this research is to enhance the heat transfer out of the cylinders. A parametric study of heat exchanges between the cylinders and flow (expressed by the Nusselt number) is reported for Reynolds numbers between 125 and 1000, while the Prandtl number is fixed at 0.71. The results are compared with an elliptical cylinder array without inclination to assess the heat transfer enhancement. The problem is solved as transient, and a vortex shedding phenomenon is reported. The results indicated that the Reynolds number has a significant effect on the heat transfer out of the cylinders, and the inclination of the elliptical cylinders enhances heat transfer rate up to 238.59%, but pressure drop is increased as high as 700%. Also, skin-friction coefficient along the five cylinders’ perimeter, plots of the velocity flow field, and temperature contours are presented.

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Copyright © 2010 by American Society of Mechanical Engineers
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Figures

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Figure 1

(a) Schematic diagrams of the elliptical cylinder array with inclination and (b) an inclined elliptical cylinder with the important geometrical parameters

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Figure 2

(a) Finite element mesh near the six cylinder region and (b) a close-up view of the mesh at the third cylinder

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Figure 3

The mesh near the cylinder surface of the model used for validation

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Figure 4

The average Nusselt number for the third elliptical cylinder for different mesh sizes and time steps and for Re=500

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Figure 5

Instantaneous velocity streamlines during a complete vortex shedding cycle for Re=500 and dimensionless time of t∗= (a) 0, (b) τ∗/4, (c) τ∗/2, and (d) 3τ∗/4

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Figure 6

time evaluation of temperature contours during a complete vortex shedding cycle for Re=500 and dimensionless time of t∗= (a) 0, (b) τ∗/4, (c) τ∗/2, and (d) 3τ∗/4

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Figure 7

Timewise variations in the local Nusselt number along the surface of the cylinders during a complete vortex shedding cycle cylinders for (a) cylinder 1, (b) cylinder 2, (c) cylinder 3, (d) cylinder 4, and (e) cylinder 5

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Figure 8

Timewise variations in the local skin-friction coefficient along the surface of the cylinders during a complete vortex shedding cycle cylinders for (a) cylinder 1, (b) cylinder 2, (c) cylinder 3, (d) cylinder 4, and (e) cylinder 5

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Figure 9

The effect of the Reynolds number on the pressure drop across the channel for the elliptical cylinder array with and without inclination

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