Natural convection in cavities with a thin fin on the hot wall
Introduction
Natural convection heat transfer in differentially heated, partitioned cavities are encountered in various industrial applications, such as heating and ventilating of living spaces, fire in buildings, solar thermal collector systems, electronic cooling devices, in storage of radioactive wastes. Studies of various aspects of this problem have been carried out by many researchers both theoretically and experimentally.
Excluding studies with multiple fins in tall systems (see, for example, [1], [2], [3]), thick fin(s) in square and tall cavities (see, for example, [4], [5], [6]), the specific problem studied in this work involving a single thin fin attached to the hot or cold wall makes a distinct category, which has been studied by various researchers that we will briefly review [7], [8], [9], [10], [11]. Oosthuizen and Paul [7] studied differentially heated cavities with aspect ratio between 3 and 7 with a horizontal plate attached to the center of the cold vertical wall. They found the local heat transfer rate on the upper portion of the hot wall increased, but the heat transfer rate near the center of the hot wall decreased. Frederick [8] studied a similar situation in a inclined cavity with diathermal partition at Rayleigh number between 103 and 105. The partition was attached to the cold wall at its center, its relative length was 0.25 and 0.50. The inclination angle was from 90° (corresponding to horizontal partition) to 45°. His results showed that the partition caused suppression of convection and the heat transfer relative to that in an identical cavity without partition was reduced considerably. Frederick and Valencia [9] studied natural convection in a square cavity with a conducting partition at the center of its hot wall and with perfectly conducting horizontal walls. Partition length and its conductivity were variable. For low values of relative conductivity, they reported reduced heat transfer with respect to that in an identical cavity without partition at Rayleigh numbers between 104 and 105. Nag et al. [10] studied numerically in a differentially heated square cavity where a horizontal plate was attached on the hot wall. The length and the position of the partition were varied and Rayleigh was between 103 and 106. They considered two cases, one with adiabatic partition and the other with perfectly conducting partition. They found that with the perfectly conducting partition the heat transfer at the cold wall increased irrespective of its position or length and it is attenuated with the adiabatic partition, which was more pronounced when the position of the partition was higher. Shi and Khodadadi [11] studied numerically the same problem reported by Nag et al. with almost perfectly conducting partition on the hot wall, but with more extensive parametric details. Their dimensionless fin length was between 0.20 and 0.50, which had seven positions along the hot wall and Rayleigh number was from 104 to 107. Since the fin was almost perfectly conducting and attached to the hot wall, the fin’s heating enhanced the convection while its blockage of the flow field suppressed it. The contribution of these two counter-acting mechanisms were not clearly quantified. Based on the numerical data, they proposed correlations to calculate Nusselt number as a function of relevant parameters for this particular case.
We see from this brief review that excluding that by Frederick and Valencia [9], all other studies considered only the perfectly conducting or insulated partitions. Yet, in practical engineering problems, often partitions are made from materials with finite conductivities. In this paper, we will study the case with dimensionless fin length from 0.10 to 0.90 at dimensionless fin position from 0.10 to 0.90 and fin to air conductivity ratio from 0 (perfectly insulating materials) to 60 (construction and fabrication materials) and examine heat transfer by conduction and convection due to fins with finite conductivity ratios.
Section snippets
Problem definition
A schematic of the two dimensional system is shown in Fig. 1. The square cavity is differentially heated, the left isothermal wall is at TH and the right at TC with horizontal walls insulated. A thin fin of WP long is attached to the active wall at a height YP. The coordinate system and boundary conditions are also shown in Fig. 1.
Mathematical model
The continuity, momentum and energy equations for a two dimensional laminar flow of an incompressible Newtonian fluid are written. Following assumptions are made:
Numerical technique
The numerical method used to solve (1), (2), (3), (4) is the SIMPLER (semi-implicit method for pressure linked equations revised) algorithm [12]. The computer code based on the mathematical formulation discussed earlier and the SIMPLER method were validated for various cases published in the literature, the results of which are discussed elsewhere [13].
Non-uniform grid in X and Y direction were used for all computations. Grid convergence was studied for the case of WP = 0.5 with grid sizes from 20
Results and discussion
Geometrical and thermal parameters governing the heat transfer in differentially heated square cavities with thin fin attached to the active wall are: aspect ratio A = L/H = 1, the length of thin fin, WP = 0, 0.1, 0.3, 0.5, 0.7, 0.9, the position of thin fin, YP = 0, 0.10, 0.30, 0.50, 0.70, 0.90, the dimensionless conductivity of thin fin, kr = 0, 1, 30, 60. Thus, the cases considered were 144 all together. Rayleigh number was varied from 104 to 109.
Flow and temperature fields, and heat transfer through
Conclusions
Heat transfer by natural convection in differentially heated square cavities with horizontal thin fin has been numerically studied. The cavity was formed by vertical isothermal walls and adiabatic horizontal walls. A thin fin was attached to the hot wall. Its dimensionless length, WP was varied from 0.10 to 0.90 and its dimensionless position, YP from 0.10 to 0.90. The relative conductivity of the thin fin, kr was varied from 1 to 60. Rayleigh number was from 104 to 109.
Based on the findings in
Acknowledgement
Financial support by Natural Sciences and Engineering Research Council of Canada is acknowledged.
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