Research Papers: Natural and Mixed Convection

Free Convection in Antisymmetrically Heated Vertical Channels

[+] Author and Article Information
D. Roeleveld

e-mail: droeleve@ryerson.ca

W. H. Leong

Department of Mechanical
and Industrial Engineering,
Ryerson University,
350 Victoria Street,
Toronto, ON M5B 2K3, Canada

1Corresponding author.

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF HEAT TRANSFER. Manuscript received March 19, 2013; final manuscript received August 16, 2013; published online October 25, 2013. Assoc. Editor: Patrick E. Phelan.

J. Heat Transfer 136(1), 012502 (Oct 25, 2013) (7 pages) Paper No: HT-13-1151; doi: 10.1115/1.4025269 History: Received March 19, 2013; Revised August 16, 2013

Free convection in a vertical channel with antisymmetrical heating is a special case that has not received a great deal of attention in the literature. Antisymmetrical heating is where the hot wall is heated above the ambient temperature by the same amount that the cold wall is cooled below the ambient, giving equal but opposing buoyancy forces inside the channel. An experimental model was constructed to study antisymmetrical heating inside an isothermally heated vertical channel. Flow visualization was used to obtain the flow field and laser interferometry was used to obtain the temperature field. Based on the measured temperature field, the local and average Nusselt numbers were determined, which were compared with numerical predictions obtained using ansys fluent. A range of Rayleigh numbers were studied for air with a Prandtl number of 0.71. The results show that an open-ended channel with antisymmetrical heating has some similarities to a tall enclosure. The average convective heat transfer can be approximated using an existing correlation for a tall enclosure from the literature.

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Fig. 1

Schematic of the problem geometry

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Fig. 2

Schematic of the Mach-Zehnder interferometer

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Fig. 3

Boundary conditions and computational domain

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Fig. 4

(a) Flow visualization, (b) sketch of the observed flow pattern, and (c) numerical solution streamlines for A = 37.9 and Ra = 1.51 × 103

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Fig. 5

Infinite fringe interferograms and numerically predicted isotherms for different aspect ratios

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Fig. 6

Graph of the local Nusselt number versus distance for A = 26.4 and Ra = 1.48 × 103

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Fig. 7

Graph of the local Nusselt number versus distance for A = 13.2 and Ra = 1.18 × 104

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Fig. 8

Hot wall average Nusselt number variation with Rayleigh number




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