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Research Papers

Heat Transfer Enhancement in a Radial Turbulent Sink Flow Cooling System

[+] Author and Article Information
Medhat M. Sorour

Mechanical Engineering Department,
Faculty of Engineering,
Alexandria University,
Alexandria 21524, Egypt
e-mail: sorour1950@gmail.com

Mohamed Fayed

Mechanical Engineering Department,
Faculty of Engineering,
Alexandria University,
Alexandria 21524, Egypt
e-mail: mohamed.fayed@aum.edu.kw

Noha Alaa El-Din

Mechanical Engineering Department,
Faculty of Engineering,
Pharos University,
Alexandria 21648, Egypt
e-mail: noha.alaaeldin@pua.edu.eg

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF THERMAL SCIENCE AND ENGINEERING APPLICATIONS. Manuscript received August 13, 2018; final manuscript received October 19, 2018; published online January 25, 2019. Assoc. Editor: Pedro Mago.

J. Thermal Sci. Eng. Appl 11(3), 031003 (Jan 25, 2019) (11 pages) Paper No: TSEA-18-1399; doi: 10.1115/1.4041883 History: Received August 13, 2018; Revised October 19, 2018

The steady forced convection between two stationary parallel circular disks in a radial sink flow cooling system is investigated numerically. This investigation is devoted to study the effect of swirling flow and/or grooved surface on the heat transfer and on the thermo-hydraulic parameter. A wide range of inlet Reynolds number (Re), 100 ≤ Re ≤ 105, inlet swirl ratio (S), 0 ≤ S ≤ 20, and the gap spacing ratio (G), 0.01 ≤ G ≤ 0.1 is considered in the study. The rectangular grooves are characterized by ribs with three dimensionless lengths: height (t/δ), 0.1 ≤ t/δ ≤ 0.35, the interval spacing between ribs (i/Ro), 0.025 ≤ i/Ro ≤ 0.1, and the width of rib (w/Ro), 0.025 ≤ w/Ro ≤ 0.1. The results of the heat transfer analysis indicate that the swirling flow enhances the cooling system for plain and ribbed surfaces. However, the thermal hydraulic study indicated that the swirling flow is beneficial for plain surfaces only. And the ribs are beneficial with pure radial inflow.

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References

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Figures

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Fig. 1

Geometrical configuration

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Fig. 2

Numerical model verification and comparison with the previous work: (a) streamlines of the experiment by Savino and Keshock [1], and the numerical streamlines, (b) comparison of numerical radial velocity axial profiles with experimental Savino and Keshock [1] for different radial locations at S = 15, (c) comparison of numerical tangential velocity axial profiles with experimental Savino and Keshock [1] for different radial locations at S = 15, and (d) comparison of numerical pressure profile with experimental Savino and Keshock [1]

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Fig. 3

The pumping friction factor ratio in the case of plain disks

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Fig. 4

The streamlines for different values of Reynolds number (Re) for G = 0.05 and S = 20

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Fig. 5

The streamlines for different values of gap spacing (δ) for S = 20 and Re = 104

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Fig. 6

The local Nusselt number

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Fig. 7

The temperature gradient over the disk at different radial positions

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Fig. 8

The average Nusselt number profile

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Fig. 9

The thermal hydraulic performance factor for plain disks case

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Fig. 10

The streamlines for different ribs sizes at Re = 5000, S = 20, and G = 0.05

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Fig. 11

The pumping friction factor ratio in the case of ribbed disks

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Fig. 12

The average Nusselt number as a function of inlet swirl ratio in the case of ribbed disks

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Fig. 13

Effect of ribs size on the radial and tangential velocity at specified radial position r/Ro = 0.5 and Re = 5000

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Fig. 14

The thermal hydraulic performance factor as a function of inlet swirl ratio

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