Thermal optimization of plate-fin heat sinks with variable fin thickness

2010 ◽  
Vol 53 (25-26) ◽  
pp. 5988-5995 ◽  
Author(s):  
Dong-Kwon Kim ◽  
Jaehoon Jung ◽  
Sung Jin Kim
Author(s):  
Dong-Kwon Kim ◽  
Jaehoon Jung ◽  
Sung Jin Kim

In the present paper, we conducted thermal optimization of plate-fin heat sink with fin thickness varying in the vertical direction. The model based on volume averaging theory (VAT) was used for this optimization. It is shown that the thermal resistance of plate-fin heat sink is reduced by allowing the fin thickness to increase in the vertical direction. In the case of water-cooled heat sink, the thermal resistance decreases up to about 20%. The amount of the reduction increases as either pumping power increases or the length of heat sink decreases.


Author(s):  
S. Manna ◽  
S. K. Ghosh ◽  
S. C. Haldar

Free convection from an upward facing radial heat sink with fins at an equal angular gap attached to an isothermal base has been investigated numerically. The governing equations in primitive variables were changed to vorticity-vector potential formulation, and an in-house code was developed using finite difference technique. To close the computational domain, two pseudo boundaries were considered. Length, height, and number of fins strongly influence the rate of heat transfer while the fin thickness has a marginal role. As the fin length increases, the rate of heat transfer first increases and then remains almost unaffected. However, the active length of the fins depends on the strength of buoyancy. Heat transfer continuously increases with fin height but with diminishing effect. Adding more number of fins has two opposing effects. It provides more surface area for convection, but at the same time, the induced air is unable to reach the interior of the heat sink making the inner portion of the fins inoperative. As a result of these two opposing influences, heat transfer increases in the beginning and then decreases as more fins are added. This article suggests various fin parameters to achieve maximum cooling. In addition, one can estimate the rate of cooling to be achieved by any radial heat sink.


2015 ◽  
Vol 137 (2) ◽  
Author(s):  
S. S. Feng ◽  
J. J. Kuang ◽  
T. J. Lu ◽  
K. Ichimiya

A numerical investigation was carried out to characterize the thermal performance of finned metal foam heat sinks subject to an impinging air flow. The main objective of the study was to quantify the effects of all relevant configurational parameters (channel length, channel width, fin thickness, and fin height) of the heat sink upon the thermal performance. Open-cell aluminum foam having fixed porosity of 0.9118 and fixed pore density of five pores per inch (PPI) was used in the study. A previously validated model based on the porous medium approach was employed for the numerical simulation. Various simulation cases for different combinations of channel parameters were carried out to obtain the Nusselt number correlation. Based on the inviscid impinging flow, a pressure drop correlation was derived for impinging flow in finned metal foam heat sinks. By using these correlations, the thermal performance of finned metal foam heat sinks was compared with the conventional plate-fin heat sinks. It was demonstrated that the finned metal foam heat sinks outperformed the plate-fin heat sinks on the basis of given weight or given pumping power.


Author(s):  
Jaehoon Jung ◽  
Sung Jin Kim

Analytical solutions for entropy generation rate distribution associated with heat transfer and fluid friction in microchannel heat sinks are examined. Microchannel heat sinks are modeled as a porous medium through which fluid flows. Analytical solutions are obtained by using velocity and temperature distributions of microchannel heat sinks, which are based on the modified Darcy model for fluid flow and the two-equation model for heat transfer. Using the analytical solution, the entropy generation of heat sinks was obtained. The effects of height, channel width, and fin thickness on the entropy generation rate were studied and thermal optimization of heat sink was performed.


2007 ◽  
Vol 129 (4) ◽  
pp. 518-521 ◽  
Author(s):  
Gaowei Xu ◽  
Yingjun Cheng ◽  
Le Luo

The heat-transfer characteristics of 128 small-sized plate-fin heat sinks in a supercomputer chassis are investigated with CFD simulation. The V-shaped curves of the chip temperature versus fin pitch and fin thickness are derived and a thermal resistance model is built to explore the profile and obtain the convective heat-transfer coefficient of the heat sinks. It turns out that the V-shaped profile arises from the joint action of the thermal conduction and convection of heat sink, which can be attributed to the intricacy of the dependencies of thermal resistances on either fin pitch or thickness. It can be further concluded that Biot criterion is applicable to estimate the Biot number of large-scale plate-fin heat sink but not applicable for the small-sized one. The convective heat-transfer coefficient is a complicated function of fin pitch and fin thickness. The empirical formulas of heat transfer are obtained and the fin pitch and fin thickness are optimized.


1993 ◽  
Vol 115 (1) ◽  
pp. 75-81 ◽  
Author(s):  
A. Bejan ◽  
A. M. Morega

This paper reports the optimal geometry of an array of fins that minimizes the thermal resistance between the substrate and the flow forced through the fins. The flow regime is laminar. Two fin types are considered: round pin fins, and staggered parallel-plate fins. The optimization of each array proceeds in two steps: The optimal fin thickness is selected in the first step, and the optimal thickness of the fluid channel is selected in the second. The pin-fin array is modeled as a Darcy-flow porous medium. The flow past each plate fin is in the boundary layer regime. The optimal design of each array is described in terms of dimensionless groups. It is shown that the minimum thermal resistance of plate-fin arrays is approximately half of the minimum thermal resistance of heat sinks with continuous fins and fully developed laminar flow in the channels.


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