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Research Papers: Heat Exchangers

Heat Transfer Investigation of a Tube Partially Wrapped by Metal Porous Layer as a Potential Novel Tube for Air Cooled Heat Exchangers

[+] Author and Article Information
M. Mohammadpour-Ghadikolaie

Department of Mechanical Engineering,
Amirkabir University of Technology,
P.O. Box 15875-4413,
Tehran, Iran
e-mail: m_mohammadpour@aut.ac.ir

M. Saffar-Avval

Department of Mechanical Engineering,
Amirkabir University of Technology,
P.O. Box 15875-4413,
Tehran, Iran
e-mail: mavval@aut.ac.ir

Z. Mansoori

Energy Research Center,
Amirkabir University of Technology,
P.O. Box 15875-4413,
Tehran, Iran
e-mail: z.mansoori@aut.ac.ir

N. Alvandifar

Department of Mechanical Engineering,
Amirkabir University of Technology,
P.O. Box 15875-4413,
Tehran, Iran
e-mail: n.alvandifar@aut.ac.ir

N. Rahmati

Department of Mechanical Engineering,
Amirkabir University of Technology,
P.O. Box 15875-4413,
Tehran, Iran
e-mail: nahid-rahmati@aut.ac.ir

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF HEAT TRANSFER. Manuscript received December 8, 2016; final manuscript received September 5, 2018; published online November 21, 2018. Assoc. Editor: Amitabh Narain.

J. Heat Transfer 141(1), 011802 (Nov 21, 2018) (12 pages) Paper No: HT-16-1793; doi: 10.1115/1.4041795 History: Received December 08, 2016; Revised September 05, 2018

Laminar forced convection heat transfer from a constant temperature tube wrapped fully or partially by a metal porous layer and subjected to a uniform air cross-flow is studied numerically. The main aim of this study is to consider the thermal performance of some innovative arrangements in which only certain parts of the tube are covered by metal foam. The combination of Navier–Stokes and Darcy–Brinkman–Forchheimer equations is applied to evaluate the flow field. Governing equations are solved using the finite volume SIMPLEC algorithm and the effects of key parameters such as Reynolds number, metal foam thermophysical properties, and porous layer thickness on the Nusselt number are investigated. The results show that using a tube which is fully wrapped by an external porous layer with high thermal conductivity, high Darcy number, and low drag coefficient, can provide a high heat transfer rate in the high Reynolds number laminar flow, increasing the Nusselt number almost as high as 16 times compared to a bare tube. The most important result of thisstudy is that by using some novel arrangements in which the tube is partially covered by the foam layer, the heat transfer rate can be increased at least 20% in comparison to the fully wrapped tube, while the weight and material usage can be considerably reduced.

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References

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Figures

Grahic Jump Location
Fig. 1

Sketch of the problem domain

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Fig. 2

Nusselt number versus nondimensional porous layer radius for different foam samples at U = 0.7 m/s, U = 1.4 m/s, U = 2.8 m/s, U = 5.6 m/s

Grahic Jump Location
Fig. 3

Comparing the Nusselt number of a finned tube to a tube wrapped by samples A and C for different foam layer thicknesses at (a) U = 0.7 m/s, (b) U = 1.4 m/s, (c) U = 2.8 m/s, and (d) U = 5.6 m/s

Grahic Jump Location
Fig. 4

Local Nusselt number for a tube wrapped by sample A at U = 2.8 m/s and Rp/Rs = 2

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Fig. 5

Geometry of arrangement 2

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Fig. 6

Average Nusselt number versus porous layer radius for arrangements 1 and 2 for sample B at U = 0.7 m/s and for sample A at U = 2.8 m/s

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Fig. 7

Geometry of arrangements 3 and 4

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Fig. 8

Average Nusselt number versus porous layer radius for arrangements 1 and 3 for sample A and B and at U = 5.6 m/s, U = 2.8 m/s, and U = 0.7 m/s

Grahic Jump Location
Fig. 9

Variation of local Nusselt number around the tube forarrangements 1 and 3 at U = 5.6 m/s and Rp/Rs = 2.5 for sample B

Grahic Jump Location
Fig. 10

Average Nusselt number versus porous layer radius for arrangements 1 and 4 for samples A and B at U = 5.6 m/s, U = 2.8 m/s, and U = 0.7 m/s

Grahic Jump Location
Fig. 11

Variation of local Nusselt number around the tube forarrangements 1 and 4 at U = 0.7 m/s and Rp/Rs = 2.5 for sample B

Grahic Jump Location
Fig. 12

Variation of local Nusselt number around the tube forarrangements 1 and 4 at U = 5.6 m/s and Rp/Rs = 2.5 for sample B

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