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Research Papers: Jets, Wakes, and Impingment Cooling

Experimental Investigation of Air–Water Mist Jet Impingement Cooling Over a Heated Cylinder

[+] Author and Article Information
Chunkyraj Khangembam

Department of Mechanical Engineering,
National Institute of Technology Manipur,
Imphal West, Manipur 795004, India
e-mail: chunky_kh@yahoo.com

Dushyant Singh

Department of Mechanical Engineering,
National Institute of Technology Manipur,
Imphal West, Manipur 795004, India
e-mails: dushyant7raghu@gmail.com;
dushyant@nitmanipur.ac.in

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF HEAT TRANSFER. Manuscript received December 8, 2018; final manuscript received May 4, 2019; published online June 12, 2019. Assoc. Editor: Amy Fleischer.

J. Heat Transfer 141(8), 082201 (Jun 12, 2019) (12 pages) Paper No: HT-18-1801; doi: 10.1115/1.4043771 History: Received December 08, 2018; Revised May 04, 2019

Experimental investigation on heat transfer mechanism of air–water mist jet impingement cooling on a heated cylinder is presented. The target cylinder was electrically heated and was maintained under the boiling temperature of water. Parametric studies were carried out for four different values of mist loading fractions, Reynolds numbers, and nozzle-to-surface spacings. Reynolds number, Rehyd, defined based on the hydraulic diameter, was varied from 8820 to 17,106; mist loading fraction, f ranges from 0.25% to 1.0%; and nozzle-to-surface spacing, H/d was varied from 30 to 60. The increment in the heat transfer coefficient with respect to air-jet impingement is presented along with variation in the heat transfer coefficient along the axial and circumferential direction. It is observed that the increase in mist loading greatly increases the heat transfer rate. Increment in the heat transfer coefficient at the stagnation point is found to be 185%, 234%, 272%, and 312% for mist loading fraction 0.25%, 0.50%, 0.75%, and 1.0%, respectively. Experimental study shows identical increment in stagnation point heat transfer coefficient with increasing Reynolds number, with lowest Reynolds number yielding highest increment. Stagnation point heat transfer coefficient increased 263%, 259%, 241%, and 241% as compared to air-jet impingement for Reynolds number 8820, 11,493, 14,166, and 17,106, respectively. The increment in the heat transfer coefficient is observed with a decrease in nozzle-to-surface spacing. Stagnation point heat transfer coefficient increased 282%, 248%, 239%, and 232% as compared to air-jet impingement for nozzle-to-surface spacing of 30, 40, 50, and 60, respectively, is obtained from the experimental analysis. Based on the experimental results, a correlation for stagnation point heat transfer coefficient increment is also proposed.

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Figures

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Fig. 1

Schematic diagram of the experimental setup for mist jet impingement on heated circular cylinder

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Fig. 2

Schematic diagram for (a) the air atomizing nozzle (not to scale) and (b) position of the thermocouples along the cylinder

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Fig. 3

Comparison of local Nusselt number distribution for air-jet impingement at various d/D and H/d ratio along (a) axial direction and (b) circumferential direction

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Fig. 4

Effect of mist loading fraction on the variation of local heat transfer coefficient along the axial and circumferential direction for H/d = 30 and 60 and Rehyd = 8820 and 17,106

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Fig. 5

Effect of mist loading fraction on the variation of local heat transfer coefficient increment along the axial and circumferential direction for H/d = 30 and 60 and Rehyd = 8820 and 17,106

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Fig. 6

Effect of Reynolds number on the variation of local heat transfer coefficient and heat transfer coefficient increment along the axial direction for H/d = 30 at f = 0.25% and 1.0%

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Fig. 7

Effect of Reynolds number on the variation of local heat transfer coefficient and heat transfer coefficient increment along the circumferential direction for H/d = 30 at f = 0.25% and 1.0%

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Fig. 8

Effect of Reynolds number on the variation of local heat transfer coefficient and heat transfer coefficient increment along the axial direction for H/d = 60 at f = 0.25% and 1.0%

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Fig. 9

Effect of Reynolds number on the variation of local heat transfer coefficient and heat transfer coefficient increment along the circumferential direction for H/d = 60 at f = 0.25% and 1.0%

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Fig. 10

Effect of nozzle-to-surface spacing on the variation of local heat transfer coefficient and heat transfer coefficient increment along the axial direction

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Fig. 11

Effect of nozzle-to-surface spacing on the variation of local heat transfer coefficient and heat transfer coefficient increment along the circumferential direction

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Fig. 12

Parity plot for stagnation point heat transfer coefficient increment with respect to experimental result and correlation result

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