Review Articles

A Comprehensive Review of Natural Convection in Triangular Enclosures

[+] Author and Article Information
O. M. Kamiyo

Department of Mechanical Engineering,  University of Lagos, Lagos, Nigeriaola_kamiyo@hotmail.com

D. Angeli1

DIMeC - Dipartimento di Ingegneria Meccanica e Civile,  Università di Modena e Reggio Emilia, via Vignolese 905, I-41100 Modena, Italydiego.angeli@unimore.it

G. S. Barozzi

DIMeC - Dipartimento di Ingegneria Meccanica e Civile,  Università di Modena e Reggio Emilia, via Vignolese 905, I-41100 Modena, Italygiovanni.barozzi@unimore.it

M. W. Collins

School of Engineering and Design,  Brunel University, Uxbridge, Middlesex, UB8 3PH, UKcollinmw@hotmail.com

V.O.S. Olunloyo

Department of Systems Engineering,  University of Lagos, Lagos, Nigeriavosolunloyo@hotmail.com

S.O. Talabi


Corresponding author.

Appl. Mech. Rev 63(6), 060801 (Jun 21, 2011) (13 pages) doi:10.1115/1.4004290 History: Received February 03, 2011; Revised May 05, 2011; Accepted May 12, 2011; Published June 21, 2011; Online June 21, 2011

Natural convection in triangular enclosures is an important problem. It displays well the generic attributes of this class of convection, with its dependence on enclosure geometry, orientation and thermal boundary conditions. It is particularly rich in its variety of flow regimes and thermal fields as well as having significant practical application. In this paper, a comprehensive view of the research area is sought by critically examining the experimental and numerical approaches adopted in studies of this problem in the literature. Different thermal boundary conditions for the evolution of the flow regimes and thermal fields are considered. Effects of changes in pitch angle and the Rayleigh number on the flow and thermal fields are examined in detail. Although most of the past studies are in the laminar regime, the review extends up to the recent studies of the low turbulent regime. Finally, areas of further research are highlighted.

Copyright © 2011 by American Society of Mechanical Engineers
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Figure 1

Schematic of the problem

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Figure 2

(a) Seven possible nontrivial combinations of isothermal and adiabatic boundary conditions (H = hot wall, C = cold wall, A = adiabatic wall); (b) flow patterns for the seven nontrivial configurations (adapted from)

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Figure 3

Schematic view of the first experimental study

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Figure 4

Heat transfer components

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Figure 6

Local Nusselt number (Nu) versus Grashof number (Gr) for both hot and cold walls [14]

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Figure 8

Steady-state stream function (ψ, left) and temperature (T, right) fields with Pr = 0.72, AR = 0.2 and (a) Gr = 1.0 x 103 , (b) Gr = 3.0 x 103 , (c) Gr = 4.0 x 103 , (d) Gr = 4.5 x 103 , and (e) Gr = 5.0 x 103 , showing the change in flow regime from single cell to multicellular flow as Gr increases [24-25]

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Figure 9

Steady-state stream function (ψ, left) and temperature (T, right) fields with Pr = 0.72, Gr = 105 and (a) AR = 1.0, (b) AR = 0.5, (c) AR = 0.3, (d) AR = 0.15, and (e) AR = 0.1, showing the change in flow structure as AR decreases [24-25]

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Figure 10

Streamlines for Ra = 105 , AR = 1.73 [31]

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Figure 11

(a) Streamline pattern; (b) mean Nusselt number against Grashof number [18]

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Figure 12

Streamlines and isotherms for different aspect ratios (L*) and Rayleigh numbers (Ra) [49]

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Figure 13

(a) streamlines (left) and isotherms for Gr = 107 , AR = 0.5 [51-55], configuration II; (b) streamlines for Gr = 8.38 x 106 , AR = 1.0 [15], configuration IV

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Figure 14

Point of singularity

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Figure 15

18 deg pitch enclosure: (a) streamlines and (b) mean temperature field when heated from below isothermally; (c) turbulent kinetic energy distribution when heated from above isothermally and (d) uv− Re stress when heated from above with constant heat flux [70]

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Figure 16

Local Nusselt number along the inclined wall as a function of the Grashof number [74]

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Figure 7

Schematic illustration of a vented attic, Ref. [20]

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Figure 5

Experimental rig in Ref. [6]



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