A heat sink made of an array of fins that have a straight, rectangular cross section is used to cool an electronic micro-chip module, as schematically shown in the figure. The heat sink (base and fins) is made of copper, and each fin is 3 mm thick and 30 mm long. If the fin-base temperature is 85°C and the cooling air is at 25°C with an average convective heat transfer coefficient of ch =100 W/(m2 K), determine the temperature distribution in one fin and the rate of heat transferred per unit width of the fin. If the fins are made of aluminum instead, what is the change in the rate of heat dissipated by the aluminum fin of same thickness? For the numerical analysis, in both the cases, consider a minimum of 11 nodes from the base to tip and convective heat transfer from the fin tip.

Compare the results with the one- dimensional fin analysis



GIVEN

• Heat sink made of an arry of straight rectangular cross section fins.

• Fin base temperature (T0)= 850C

• Surrounding air temperature (T?)= 250C

• Convection heat transfer coefficient ( ch )= 100 W/(m2 K)

• Fin thickness(t)= 3 mm = 0.003 m

• Fin length (L)= 30 mm =0.03 m

• Number of nodes (N)=11

FIND

(a) Temperature distribution in one fin considering convection from fin tip

(b) Heat transfer rate per unit width of fin

(c) Rate of change in heat dissipated if Aluminum of same thickness is used.

PROPERTIES

• Thermal conductivity of copper(kCu)= 396 W/(m K)

• Thermal conductivity of Aluminum (kAl)=238 W/(m K)

SKETCH


For the node and control volume arrangement shown in the sketch, we have



For the control volume at i = 1, we have a specified temperature, therefore



For the interior control volumes, i = 2, 3, 4, 5,... , 8 an energy balance gives



Writing this in the tridiagonal form



Since W>>t

P=2(W+t) 2W

Cross sectional Area (A)= W*t



For the control volume at node i = N, an energy balance gives



In the tridiagonal form this becomes





The heat transferred through the fin per unit width is given by



We can solve the above problem by MATLAB by discretization. The boundary conditions for the

discretization are





L=0.03; % in m

N=11;

delx=L/(N-1); % in m

t=0.003; % in m

h=100; % W/(m^2 K)

k=396; % W/(m K)

T(1)=85; % Celsius

T(2:N)=0; % Celsius

Tinf=25; % Celsius



for j=1:1:3000

for i=N-1:-1:2

Tf=T;

T(i)=((2*(delx^2)*h*Tinf/(k*t))+T(i+1)+T(i-1))/(2+(2*(delx^2)*h/(k*t)));

T(N)=(T(N-

1)+(h*delx/(k*t)*(delx+t)*Tinf))/(1+(h*delx/(k*t)*(2*delx+t)));



end;

count=0;

for i=1:N

if abs(Tf(i)-T(i))<10^-4

count=count+1;

end

end

if count==N

break

end

end

for i=1:1:N

x(i)=(i-1)*delx;

end

plot(x,T)

q=(T(1)-T(2))*t*k/delx+h*delx*(T(1)-Tinf) % in Watts



The following temperature distribution is obtained along the length of fin from above program.



The heat transfer per fin is calculated as per equation



When Aluminum fin is used instead of Copper

Replacing thermal conductivity (k) in above program we get



For exact solution entry 4 with For the exact solution use entry 4 with



Which is close to the heat transfer rate obtained by discretization.

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