Research Papers: Jets, Wakes, and Impingment Cooling

Heat Transfer Prediction of a Jet Impinging a Cylindrical Deadlock Area

[+] Author and Article Information
Yacine Halouane

Département d'Énergétique,
Universite M'hamed Bougara,
Boumerdes 35000, Algérie

Amina Mataoui

Laboratoire de Mécanique des
Fluides Théorique et Appliqué,
Faculté de Physique,
Université de Science et Technologie,
Houari Boumediene—USTHB,
Alger 16111, Algérie
e-mail: mataoui_amina@yahoo.fr

Farida Iachachene

Département de Physique,
Universite M'hamed Bougara,
Boumerdes 35000, Algérie

Contributed by the Heat Transfer Division of ASME for publication in the JOURNAL OF HEAT TRANSFER. Manuscript received May 7, 2013; final manuscript received August 2, 2014; published online September 16, 2014. Assoc. Editor: William P. Klinzing.

J. Heat Transfer 136(11), 112203 (Sep 16, 2014) (9 pages) Paper No: HT-13-1238; doi: 10.1115/1.4028323 History: Received May 07, 2013; Revised August 02, 2014

The turbulent heat transfer by a confined jet flowing inside a hot cylindrical cavity is investigated numerically in this paper. This configuration is found in several engineering applications such as air conditioning and the ventilation of mines, deadlock, or corridors. The parameters investigated in this work are the Reynolds number (Re, 20,000 ≤ Re ≤ 50,000) and the normalized distance Lf between jet exit and the cavity bottom (Lf, 2 ≤ Lf  ≤ 12). The numerical predictions are performed by finite volume method using the second order one-point closure turbulence model (RSM). The Nusselt number increases and attains maximum values at stagnation points, after it decreases. For an experimental test case available in the literature Lf = 8, the numerical predictions are in good agreement. Processes of heat transfer are analyzed from the flow behavior and the underlying mechanisms. The maximum local heat transfer between the cavity walls and the flow occurs at Lf = 6 corresponding to the length of the potential core. Nusselt number at the stagnation point is correlated versus Reynolds number Re and impinging distance Lf; [Nu0=f(Re,Lf)].

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Fig. 1

Scheme of the experimental setup and computational domain

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Fig. 2

Geometry and a typical mesh structure

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Fig. 3

Grid cases test (axial velocity)

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Fig. 13

Local Nusselt number along the bottom (a1, b1, c1) and lateral (a2, b2, c2) wall. Effect of Reynolds number (6 ≤ Lf ≤ 12).

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Fig. 14

The stagnation point Nusselt number at the bottom wall of the cavity

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Fig. 11

Effect of impinging distance on the isotherm and streamlines contours

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Fig. 12

Local Nusselt number evolution along the bottom (a1, b1) and lateral (a2, b2) wall: effect of Reynolds number (Lf = 2 and Lf = 4)

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Fig. 5

Reduced axial velocity profile along the jet axis

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Fig. 6

Mean axial velocity profiles for different cross sections (Re = 37,400 and Lf = 8)

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Fig. 7

Reynolds stress profiles for different cross sections (Re = 37,400 and Lf = 8)

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Fig. 8

Radial evolution of the local Nusselt number on the cavity bottom f Re = 20,000 and Lf = 8

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Fig. 9

Flow structure (Re = 37,400 and Lf = 8)

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Fig. 10

Effect of impinging distance on axial velocity




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