Heat Transfer from Extended Surfaces Heat Transfer Enhancement by Fins Bare surfaceFinned surface.
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Transcript of Heat Transfer from Extended Surfaces Heat Transfer Enhancement by Fins Bare surfaceFinned surface.
![Page 1: Heat Transfer from Extended Surfaces Heat Transfer Enhancement by Fins Bare surfaceFinned surface.](https://reader036.fdocuments.us/reader036/viewer/2022081417/56649f495503460f94c6b93a/html5/thumbnails/1.jpg)
Heat Transfer from Extended SurfacesHeat Transfer Enhancement by
Fins
Bare surface Finned surface
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Typical finned-tube heat exchangers
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Straight fin of uniform cross
section
Straight fin of nonuniform cross section
Annular fin Pin fin
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Equation for Extended Surfaces
x
T∞, h
Ac(x)dx
dx
Tb
cond,inq cond,outq
conv,outq
cond,in cond,out conv,outq q q
dAs(x)
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dx
Ac(x)dAs(x)
cond,inq cond,outq
conv,outq
cond,in cond,out conv,outq q q
x
( ) ( )c c
dT d dTkA x kA x dx
dx dx dx
( ) ( )shdA x T x T
cond,inq ( )x c
dTq kA x
dx
cond,outq x dxq
conv,outq
T∞, h
T(x)
convdq
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When k = constant,
( ) ( ) ( ) 0c s
d dTkA x dx hdA x T x T
dx dx
( ) ( ) 0sc
dAd dTkA x h T x T
dx dx dx
( ) ( ) 0sc
dAd dT hA x T x T
dx dx k dx
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Fins of Uniform Cross-Sectional Area
Ac(x) = constant,
and dAs = Pdx
P: fin perimeter
x
Ac
Tb
L
dAsdx
,T h
( ) ( ) 0sc
dAd dT hA x T x T
dx dx k dx
2
2( ) 0
c
d T hPT x T
dx kA
P
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boundary conditionsat x =
0:
excess temperature : (x) = T(x) - T∞
2
2( ) 0
c
d T hPT x T
dx kA
22
20
dm
dx
where 2
c
hPm
kA
dxx
Tb
, T h
(0) bT T (0) (0)T T bT T b
L
T(x)
1 2( ) mx mxx C e C e 1 2sinh( ) cosh( )D mx D mx
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at x = L: 3 cases1) very long fin (L → ∞):
2) convection tip:
3) negligible heat loss: adiabatic tip
dxx
Tb, T h
L( ) ( )x T x T
( )T L T ( ) 0T T
( )L
dTk h T L T
dx ( ) 0L
d hL
dx k
0L
dTk
dx 0
L
d
dx
T(x)
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Temperature distribution
2) convection tip:
1) long fin:
3) adiabatic tip:
( ) mx
b
xe
cosh ( ) / sinh ( )( )
cosh / sinhb
m L x h mk m L xx
mL h mk mL
( ) cosh ( )
coshb
x m L x
mL
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Total heat loss by the fin
1) long fin:
3) adiabatic tip:
2) convection tip:
,
0
f c b
x
dTq kA
dx
or ( )f
f Aq h T x T dA
x
Ac
dAs
Tb
L
dx
P, T h
f c bq hPkA M
sinh / cosh
cosh / sinhf c b
mL h mk mLq hPkA
mL h mk mL
tanh tanhf c bq hPkA mL M mL
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Find: 1) Temperature distribution T(x) and heat loss qf when the fin is constr
ucted from: a) pure copper, b) 2024 aluminum alloy, and c) type AISI 316 stainless steel.
2) Estimate how long the rods must be for the assumption of infinite length to yield an accurate estimate of the heat loss.
Assumption:very long fin
Example 3.9
, , 5mmk L D
C100bT 2
25 C100 W/m K
Th
air
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1) For a very long fin
heat loss:
conductivity at2
bT TT
Copper: k = 398 W/m.KAluminum alloy: k = 180 W/m.KStainless steel: k = 14 W/m.K
Copper: 8.3 W
Aluminum alloy: 5.6 W
Stainless steel: 1.6 W
qf
( ) mx
b
xe
( )
b
T
T
T
T
x
( ) mx
bT T T eT x
, , 5mmk L D
C100bT 2
25 C100 W/m K
Th Air
c
hPm
kA
4h
kD
2
,4c
DP D A
cf bhPkAq
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2)
1/ 22.65
2.65 ckAL
m hP
To get an accuracy over 99%
For the adiabatic condition at the tip
qf = MtanhmL (long fin: qf = M)
Copper: 0.19 m
Aluminum alloy: 0.13 m
Stainless steel: 0.04 m
tanh 0.99mL 2.65mL or
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Fins of Nonuniform Cross-Sectional Area : Annular Fin
T∞, h2r t
cond,in cond,out conv,outq q q
bT
dr
1rr
cond,inqcond,outq
conv,outq
c 2A rt
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T∞, h
1r
2rrdr
t
conv,outq
cond,outq cond,inq
2r
dTq k rt
dr
cond,outq 2 2r dr
dT d dTq k rt k rt dr
dr dr dr
cond,inq
conv,outq conv 2 2 ( )dq h rdr T r T
T(r)
c 2A rt
bT
2 2sdA rdr
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When k = const,
boundary conditions: when an adiabatic tip is presumed
2 4 ( ) 0d dT
k rt h r T r Tdr dr
2( ) 0
d dT hr r T r T
dr dr kt
in terms of excess temperature
( ) ( )r T r T
2 0d d
r m rdr dr
where 2 2hm
kt
1( ) ,br 2
0r r
d
dr
( ) ( ) 0sc
dAd dT hA x T x T
dx dx k dx
2r tdr
1rr
c 2A rt
2 2sdA rdr
42 ( ) 0
d dT h rdrrt T x T
dr dr k dr
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Particular solutions
: real : real : zero or integer
J andand
(or )J Y
nJ nY
: imaginary : fractional
: zero or integer
I and
and
(or )I K
nI nK
Solutions to generalized Bessel equations
2 0, 2 0d d
r rdr dr
General Solution:
/ 1/( ) ,r r Z r
where (1 ) /( 2), 2 /( 2), / (1 ) / 2
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present case:
boundary conditions:
2 0d d
r m rdr dr
2 0, 2 0d d
r rdr dr
2 21, m
Thus,
, 0, mi
( )r Z mr 1 0 2 0( ) ( )r C I mr C K mr
1 1 0 1 2 0 1( ) ( ) br C I mr C K mr
2 2 2
0 01 2
( ) ( )0
r r r r r r
dI mr dK mrdC C
dr dr dr
/ 1/( )r r Z r
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1( ) ( ),n nn n
dx I x x I x
dx
1( ) ( )n nn n
dx K x x K x
dx
2 2
0 01 2
( ) ( )0
r r r r
dI mr dK mrC C
dr dr
01
( )( ),
dI mrmI mr
dx 0
1
( )( )
dK mrmK mr
dx
1 1 2 2 1 2( ) ( ) 0C I mr C K mr
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1 21
0 1 1 2 0 1 1 2
( ),
( ) ( ) ( ) ( )bK mr
CI mr K mr K mr I mr
1 22
0 1 1 2 0 1 1 2
( )
( ) ( ) ( ) ( )bI mr
CI mr K mr K mr I mr
1 2 0 1 2 0
0 1 1 2 0 1 1 2
( ) ( ) ( ) ( )( )
( ) ( ) ( ) ( )b
K mr I mr I mr K mrr
I mr K mr K mr I mr
1 0 2 0( ) ( )r C I mr C K mr
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Heat loss from the fin
1
,f c b
r r
dTq kA
dr
1
12r r
dk r t
dr
1 1 1 2 1 1 1 21
0 1 1 2 0 1 1 2
( ) ( ) ( ) ( )2
( ) ( ) ( ) ( )f b
K mr I mr I mr K mrq kr t
K mr I mr I mr K mr
T∞, h
1r
2rrdr
t
T(r)
c 2A rtbT
1 2 0 1 2 0
0 1 1 2 0 1 1 2
( ) ( ) ( ) ( )( )
( ) ( ) ( ) ( )b
K mr I mr I mr K mrr
I mr K mr K mr I mr
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Fin Performance
• fin effectiveness
• fin resistance
• fin efficiency
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heat loss without fin
Tb
T∞, h
Ac,b: fin cross-sectional area at the base
Ac,b
1. Fin effectiveness
fin effectiveness:
design criteria:
, ,b c b b c b bq hA T T hA
,
ff
c b b
q
hA
(rule of a thumb)
2f
Assume hs are the same for with or without fin.
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Ex) long straight fin with uniform cross- sectional area
In order to get high fin performance
• installation of fins at the lower h side
• large k material
• thin shape
f c bq hPkA
,
c bf
c b b
hPkA
hA
c
kP
hA
![Page 27: Heat Transfer from Extended Surfaces Heat Transfer Enhancement by Fins Bare surfaceFinned surface.](https://reader036.fdocuments.us/reader036/viewer/2022081417/56649f495503460f94c6b93a/html5/thumbnails/27.jpg)
provides upper limit of f, which is reached as L approaches infinity.
Practically qf for the adiabatic tip reaches 9
8% of heat transfer when mL = 2.3.
Thus, the fin length longer than L = 2.3/m is not effective.
f
c
kP
hA
f c bq hPkA long fin
c
hPm
kAtanh ,f c bq hPkA mLadia. tip
![Page 28: Heat Transfer from Extended Surfaces Heat Transfer Enhancement by Fins Bare surfaceFinned surface.](https://reader036.fdocuments.us/reader036/viewer/2022081417/56649f495503460f94c6b93a/html5/thumbnails/28.jpg)
2. Fin resistance
b: driving potential
Thermal resistance due to convection at the exposed base: Rt,b
,
bf
t f
qR
,t fb
f
Rq
,b
t bb
Rq
,
b
c b bhA
,
1
c bhA
Tb
T∞, h
Ac,b
![Page 29: Heat Transfer from Extended Surfaces Heat Transfer Enhancement by Fins Bare surfaceFinned surface.](https://reader036.fdocuments.us/reader036/viewer/2022081417/56649f495503460f94c6b93a/html5/thumbnails/29.jpg)
Ex) straight fin of uniform cross-sectional area with an adiabatic tip
3. Fin efficiency
qmax: heat loss when the whole fin is assumed at Tb
max
ff
q
q f
f b
q
hA
tanhc b
b
hPkA mL
hPL
ff
f b
q
hA
tanh mL
mL
x
Ac
dAs
Tb
L
dx
P, T h
![Page 30: Heat Transfer from Extended Surfaces Heat Transfer Enhancement by Fins Bare surfaceFinned surface.](https://reader036.fdocuments.us/reader036/viewer/2022081417/56649f495503460f94c6b93a/html5/thumbnails/30.jpg)
For an active tip, the above relation can be used with fin length correction.rectangular fin:
pin fin:
tanhtanh , c
cf
c
f
mq M m
Lm
LL
Errors can be negligible if
or /ht k / 2 0.0625hD k
2c
tL L
4c
DL L
cf mL
Tb
x, T h
L
t D
![Page 31: Heat Transfer from Extended Surfaces Heat Transfer Enhancement by Fins Bare surfaceFinned surface.](https://reader036.fdocuments.us/reader036/viewer/2022081417/56649f495503460f94c6b93a/html5/thumbnails/31.jpg)
When w >> t, P ~ 2w,
Lc
wt
Corrected fin profile area
cA wt
1/ 2
c cc
hPmL L
kA
1/ 22
c
h wL
kwt
1/ 22
c
hL
kt
pp c
c
AA L t t
L
1/ 22
c c
hmL L
kt
1/ 2
2 cc
p
hLL
kA
1/ 2
3 / 22c
p
hL
kA
1/ 23 / 2 2 /f c pf L h kA
Ap
![Page 32: Heat Transfer from Extended Surfaces Heat Transfer Enhancement by Fins Bare surfaceFinned surface.](https://reader036.fdocuments.us/reader036/viewer/2022081417/56649f495503460f94c6b93a/html5/thumbnails/32.jpg)
Efficiency of straight fins (rectangular, triangular, and parabolic
profile)
![Page 33: Heat Transfer from Extended Surfaces Heat Transfer Enhancement by Fins Bare surfaceFinned surface.](https://reader036.fdocuments.us/reader036/viewer/2022081417/56649f495503460f94c6b93a/html5/thumbnails/33.jpg)
Efficiency of annular fins of rectangular profile
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Overall Surface Efficiency
overall efficiency of array of fins:
At : area of fins + exposed portion of the base
single fin efficiency:
ff
f b
q
hA
t f bA NA A
max
to
q
q t
t b
q
hA
![Page 35: Heat Transfer from Extended Surfaces Heat Transfer Enhancement by Fins Bare surfaceFinned surface.](https://reader036.fdocuments.us/reader036/viewer/2022081417/56649f495503460f94c6b93a/html5/thumbnails/35.jpg)
f f b b bN hA hA
tqf b bNq hA f
ff b
q
hA
b f f t fh N A A NA
1f ft b f
t t
NA NAhA
A A
1 1ft b f
t
NAhA
A
1 1ft
t b
o f
t
q
hA
NA
A
t f bA NA A
![Page 36: Heat Transfer from Extended Surfaces Heat Transfer Enhancement by Fins Bare surfaceFinned surface.](https://reader036.fdocuments.us/reader036/viewer/2022081417/56649f495503460f94c6b93a/html5/thumbnails/36.jpg)
In the case of press fit: thermal contact resistance
Tb T∞Tc
(
x
(
a
))
m
tc
co
q
q ( )t c
t b
q
hA
( ) ( )t c f c b bq Nq hA
( ), ,
bf c
t c t f
qR R
( ),
b cf c
t c
T Tq
R
( ) ( ) ,
, ,/b c
f c f c c bt c c b
T Tq q A
R A
, , ,/t c t c c bR R A
,t cR ,t fR( )f cq
bT cT T
![Page 37: Heat Transfer from Extended Surfaces Heat Transfer Enhancement by Fins Bare surfaceFinned surface.](https://reader036.fdocuments.us/reader036/viewer/2022081417/56649f495503460f94c6b93a/html5/thumbnails/37.jpg)
, , fbt f f
f f b
qR
q hA
,
1t f
f f
RhA
( ), ,/ 1/
bf c
t c c b f f
qR A hA
( ) ( )t c f c b bq Nq hA
, ,/ 1/b
b bt c c b f f
NhA
R A hA
, ,1 /f f b
b bf f t c c b
N hAhA
hA R A
, ,1 /f f
b bf f t c c b
N Ah A
hA R A
![Page 38: Heat Transfer from Extended Surfaces Heat Transfer Enhancement by Fins Bare surfaceFinned surface.](https://reader036.fdocuments.us/reader036/viewer/2022081417/56649f495503460f94c6b93a/html5/thumbnails/38.jpg)
let , , 11 /f f t c c bhA R A C
( )
1
f ft c b b
N Aq h A
C
1
f f t ft b
t t
N A A NAhA
C A A
1
1 1f ft b
t
NAhA
A C
(
x
(
a
))
m
tc
co
q
q ( )t c
t b
q
hA
1
1 1f f
t
NA
A C
![Page 39: Heat Transfer from Extended Surfaces Heat Transfer Enhancement by Fins Bare surfaceFinned surface.](https://reader036.fdocuments.us/reader036/viewer/2022081417/56649f495503460f94c6b93a/html5/thumbnails/39.jpg)
Find: Increase in heat transfer, q = qt – qwo, associated
with using fins
Example 3.10
.0 15mH
2300K50 W/m K
Th
air
S
500 KbT
6mmt
1 25mmr 20mmL
2 45mmr
Engine cylinder
Cross-section
(2024 T6 Al alloy)
Annual fins
![Page 40: Heat Transfer from Extended Surfaces Heat Transfer Enhancement by Fins Bare surfaceFinned surface.](https://reader036.fdocuments.us/reader036/viewer/2022081417/56649f495503460f94c6b93a/html5/thumbnails/40.jpg)
1 1ft f
tt bA
NAh
Aq
tA f bNA A
1) Heat transfer rate
12fNA r H Nt
fA 2 22 12 cr r
2cr 2 2
tr
2 2 22 0.048 0.025 0.0105 mfA
25 0.0105 2 0.025 0.15 5 0.006 0.0716 mtA
0.0060.045 0.048 m
2
1 25mmr 20mmL
2 45mmr
H =
0.1
5 m
t = 6
mm
500 KbT
2300K50 W/m K
Th
f: known
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To get f, use Fig. 3.19.
Parameters:
2
1
0.0481.92
0.025cr
r
1/ 2
1/ 2 3 / 23 / 24
50/ 0.023 0.15
186 1.38 10c pL h kA
cL2
tL
0.0060.02 0.023 m
2
pA cL t 4 20.023 0.006 1.38 10 m
1 25mmr 20mmL
2 45mmr
H =
0.1
5 m
t = 6
mm
2024 T6 Alk = 186 at 400 K
2
1
,cr
r 1/ 23 / 2 /c pL h kA
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1/ 23 / 2 / 0.15c pL h kA
2
1
1.92cr
r
0.95f
0.15
0.95
![Page 43: Heat Transfer from Extended Surfaces Heat Transfer Enhancement by Fins Bare surfaceFinned surface.](https://reader036.fdocuments.us/reader036/viewer/2022081417/56649f495503460f94c6b93a/html5/thumbnails/43.jpg)
Without fins
wo 454 Wt qq q
5 0.010550 0.0716 1 1 0.95 500 300 690 W
0.0716
1 1ft f b
ttq
NAhA
A
woq 12 bh r H 236 W
The amount of increase in heat transfer
wo
6902.67
236tq
q
1 25mmr 20mmL
2 45mmr H
= 0
.15
m
t = 6
mm
500 KbT
2300K50 W/m K
Th
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Comments:
Fixed fin thickness : 6 mm, Minimum fin gap : 4 mm Nmax= H/S =15
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Fixed fin gap : 4 mm, Minimum fin thickness : 2 mm Nmax= H/S =25
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Example 3.11Hydrogen-air Proton Exchange Membrane (PEM) fuel cell
Known: 1) Dimensions of a fuel cell and finned heat sink2) Fuel cell operating temperature3) Rate of thermal energy generation: 11.25 W
4) Power production: P = 9 W
5) Relationship between the convection coefficient and the air channel dimensions
50 mm 50 mm 6 mm
10 mm gaps50 mm 26 mm
56.4 CcT
9.4 m/s, 25 CV T
Without finned heat sink
With finned heat sink
air1.78 f fh k L a L a 3/ 1000 W/(m s)f fP C
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Assumptions: 1) Steady-state conditions2) Negligible heat transfer from the edges of the fuel
cell, as well as from the front and back faces of the finned heat sink
3) 1D heat transfer through the heat sink4) Adiabatic fin tips5) Negligible radiation when the heat sink is in place.
Find: 1) Net power of the fuel cell-fan system for no heat sink, Pnet = P – Pf
2) # of fins N needed to reduce the fan power consumption by 50%
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Volumetric flow rate of cooling air: ,cf VA c cA W H t
f cV W H t 9.4m/s 0.05m (0.026m 0.006m) 3 39.4 10 m /s
net
fPP C 3 -3 39.0 W 1000 W/(m /s) 9.4 10 m /s
9.0 W 9.4 W 0.4 W
Fan power consumption:
3/ 1000 W/(m s)f fP C
9.4 m/s, 25 CV T
The fan consumes more power than is generated by the fuel cell, and the system cannot produce net power.
P = 9 W
fP C net fPP P 1.
Fuel cell
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3/ 1000 W/(m s)f fP C
Aluminum fined sink: k = 200 W/m.K
air1.78 f fh k L a L a
+ finned sink base(conduction)
+ exposed base of finned side(convection)
Lc = 50 mm
+ fins(conv+cond)
11 1equiv , , ( )t b t f NR R R
= 11.25 W
2. To reduce the fan power consumption by 50%, 3 34.7 10 m /sf
9.4 W / 2 4.7 WfP
, ,base equiv
c
t c t
T Tq
R R R
Thermal circuit
3 2, 10 m K/Wt cR
contact joint(contact)
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3 2, 10 m K/Wt cR
Aluminum fined sink: k = 200 W/m.K
Lc = 50 mm
,
,c b
t c
T Tq
R
q Aq, /
c b
t c
T T
R A
,
c b
t c
T T
R
3 2(10 m K/W)/(2 0.05m 0.05m)=0.2K/W
, , /t c t cR R A , / 2t c c cR L W : 2 sides of the heat sink assembly
,basetR /L kA /(2 )b c ct kL W
(0.02m)/(2 200W/m K 0.05m 0.05m) = 0.002K/W
, :t cR
,base :tR
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N, h are needed to evaluate Rt,b
1
(2 0.05m 0.001m) 0.05 mNh
,t bR1
hA
1
2 c f ch W LNt
1
0.005 0.0005 Nh
, :t bR
3 2, 10 m K/Wt cR
Aluminum fined sink: k = 200 W/m.K
Lc = 50 mm
air1.78 f fh k L a L a
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, ( ) :t f NR, ( )
b
t f N
T T
R
( )f Nq fNq
,
b
t f
T TN
R
,, ( )
t ft f N
R
NR
For a single fin,
, /t f b fR q
For a fin with an insulated fin tip,
tanhf c b fq PkA mh L
,
1,
tanhb
t ff c f
Rq PkA mh L
3 2, 10 m K/Wt cR
Aluminum fined sink: k = 200 W/m.K
Lc = 50 mm
c
mhP
kA
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2 c fL t
c fL t
2
0.102m10.2
200W/m K 0.00005mc
Pm
kA
h hh
Lc = 50 mm
Aluminum fined sink: k = 200 W/m.K
2 (0.05m 0.001m) 0.102m P
cA 20.05m 0.001m =0.00005m
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2
1
0.102m 200W/m K 0.00005m tanh( 10.2 0.008 m)h h
For N fins,
Aluminum fined sink: k = 200 W/m.K
N, h are also needed to evaluate Rt,f
,
1
tanht f
c f
RPkA Lh m
,, ( )
t ft f N
R
NR
1
0.00102 tanh(0.008 10.2 )hN h
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11 1equiv , , ( )t b t f NR R R
The equivalent fin resistance, Reqiuv
tot , ,ba use eq iv
11.25 Wc c
t c t
T T T Tq
R R R R
56.4 CcT
25 CT
equiv , ,basec
t c t
T TR R R
q
56.4 C 25 C(0.2 0.02)K/W 2.59K/W
11.25W
The total thermal resistance, Rtot
tot , ,base equivt c tR R R R
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1 1, , ( )
12.59K/W
t b t f NR R
,
1,
0.005 0.0005t b NR
h
, ( )
1
0.00102 tanh(0.008 10.2 )t f N
hR
N h
air1.78 f fk Lh a L a
2 0.05m 0.001m 0.1 0.001N N
N N
a
2 c fW N
N
t
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air1.78 f fk Lh a L a
Properties: Table A.4. air( 300K)T
air 0.0263W/m Kk
0.1 0.001 0.1 0.0011.78 0.0263 0.08 0.08
N N
Nh
N
1 1, , ( )
12.59K/W
t b t f NR R
,
1
0.005 0.0005t b h NR
, ( )
1
0.00102 tanh(0.008 10.2 )t f N
hR
N h
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For N =
22, 2 -10.0035 m, 19.1W/m K, 13.9ma h m
, ( ) ,2.94K/W, 13.5K/Wt f N t bR R
equiv tot2.41K/W, 2.61K/WR R
54.4 CcT
For N =
20,
For N =
24,
58.9 CcT
50.7 CcT
11 on top and 11 on the bottom,
net 9.0W 4.7W 4.3WfP P P
( 56.4 C)cT