Online proceedings - EDA Publishing Association
Online proceedings - EDA Publishing Association
Online proceedings - EDA Publishing Association
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7-9 October 2009, Leuven, Belgium<br />
For the simulation of global flow variables, the model from θ ( x)<br />
and<br />
s θ ( x)<br />
are the non-dimensional solid and fluid<br />
f<br />
Bau is used, assuming fully developed laminar flow. This<br />
temperatures; Nu ( α ) is the Nusselt number;<br />
model calculates the non-dimensional mass flow rate m,<br />
α<br />
max<br />
= maxα( x)<br />
is<br />
0≤x≤1<br />
defined relative to the mass flow rate scale<br />
* * * * *<br />
m ( )<br />
0<br />
= hc Δp<br />
ν L . the maximum aspect ratio of the channel; k s is the ratio<br />
*<br />
*<br />
h is the channel’s height;<br />
c<br />
Δ p is the pressure drop over the<br />
between the conductivity of solid and fluid k * s /k * f ; A s and A f<br />
are the areas of the cross-sections of the solid and fluid<br />
*<br />
channels; ν is the kinematic viscosity of the coolant. The<br />
*<br />
region, non-dimensionalized with ( L ) 2<br />
;<br />
* * * *<br />
χ = ( k<br />
dimensionless mass flow m depends on the aspect ratio shape<br />
f<br />
L / c m<br />
) with<br />
0<br />
profile<br />
* *<br />
α ( x ) = wc ( x) h c<br />
along the channel:<br />
c * the fluid heat capacity. The parameter χ is inverse<br />
1<br />
−1<br />
*<br />
proportional to<br />
⎛ 1 (1 + α)²<br />
⎞<br />
Δ p .<br />
m = ⎜ ( ) ⎟<br />
8∫ Po α dx<br />
(1)<br />
³<br />
The three terms in (3) represent respectively the heat<br />
⎝ α<br />
0 ⎠<br />
source, the convective heat transfer from solid wall to the<br />
*<br />
Herein is Po (α ) the Poiseuille number and x = x * L is the coolant and axial conductive heat transfer in the solid wall.<br />
In these equations –using<br />
*'' * *<br />
Q s<br />
hc<br />
k III. OPTIMIZATION PROCEDURE<br />
f<br />
The shape of the channels is optimized with respect to two<br />
dimensionless axial coordinate. For the determination of the<br />
Poiseuille number, following correlation for fully developed<br />
flow is used [10] ( 0 ≤ α ≤1):<br />
Similarly, the three terms in (4) represent convective heat<br />
transfer from solid to coolant, the axial conductive heat<br />
transfer in the coolant and the capacitive heating of the fluid.<br />
2<br />
3<br />
Po ( α ) = 96(1 −1.3553α<br />
+ 1.9467α<br />
−1.7012α<br />
(2)<br />
A constant heat flux correlation for Nu ( α ) is used in the<br />
4<br />
5<br />
+ 0.9564α<br />
− 0.2537α<br />
).<br />
assumption of fully developed flow with three-wall heating<br />
The simulation of the axial temperature profiles introduces [10] ( 0 ≤ α ≤1):<br />
2<br />
3<br />
some differences with the model from Bau. In this model, Nu ( α ) = 8.235(1 −1.883α<br />
+ 3.767α<br />
− 5.814α<br />
(5)<br />
axial temperature distribution is calculated for both the fluid<br />
4 5<br />
+ 5.361α<br />
− 2α<br />
).<br />
and the solid wall region including axial conduction. The set of modeling equations (3)-(4) is solved numerically<br />
Therefore, a set of 2 dimensionless heat transfer equations – using finite volume discretization with appropriate boundary<br />
one for each region– is introduced.<br />
conditions. The fluid inlet has a specified temperature. The<br />
The equation describing heat transfer in the solid wall is:<br />
Nu<br />
( )<br />
( α )( 1+<br />
α )( 2 + α ) fluid outlet and both ends of the solid wall have adiabatic<br />
d ⎛ dθ<br />
s ⎞<br />
α<br />
max<br />
+ w<br />
f<br />
−<br />
⋅ ( θ<br />
s<br />
−θ<br />
f<br />
) + ⎜ks<br />
As<br />
⎟ = 0 boundary conditions.<br />
2α<br />
dx ⎝ dx ⎠<br />
If the axial conduction terms in (3)-(4) are ignored, the<br />
(3) modeling equations of Bau are retrieved. It is recalled in (6):<br />
The heat transfer in the fluid region is described by:<br />
Nu( α )( 1 + α )( 2 + α ) ⎛ 2α<br />
χ ⎞<br />
θ<br />
d ⎛ dθ<br />
f ⎞ m dθ<br />
s<br />
( x)<br />
= ( α + w ) ⎜<br />
+ ⋅ x⎟ (6)<br />
max f<br />
f<br />
⋅ ( θ<br />
s<br />
−θ<br />
f<br />
) + ⎜ A ⎟<br />
f<br />
= ⋅ (4)<br />
⎝ Nu( α )( 1+<br />
α )( 2 + α ) m ⎠<br />
2α<br />
dx<br />
dx<br />
⎝ ⎠ χ dx<br />
objectives. The first objective J consists of the<br />
1<br />
minimization of the wall temperature gradient. This is<br />
formulated as the Euclidian norm of the local wall<br />
temperature gradient dθ s<br />
(x)<br />
:<br />
dx<br />
2<br />
⎛ ⎞<br />
= 1 dθ<br />
s<br />
J ∫ ⎜ ⎟ ( ) 0<br />
⎝ dx<br />
dx<br />
α x ⎠<br />
(7)<br />
The second objective J that is regarded is the<br />
2<br />
minimization of the thermal resistance, which is defined as<br />
the maximum dimensionless wall temperature along the<br />
channel:<br />
J = min maxθ<br />
( )<br />
s<br />
α ( x)<br />
x<br />
(8)<br />
The primary variable describing the shape of the channels<br />
is the aspect ratio profile α (x), which is a dimensionless<br />
representation of the channel width. This shape profile is in<br />
fact a continuous function defined over the entire length of<br />
the channel. Conventional optimization routines are only<br />
suitable for a finite number of variables. Therefore a<br />
Fig. 1: Schematic of the channels cross-section<br />
©<strong>EDA</strong> <strong>Publishing</strong>/THERMINIC 2009 158<br />
ISBN: 978-2-35500-010-2