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Unformatted text preview: E 1 14 Solo/$0M it 3116 A commercially available heat sink is to be selected to keep the case temperature of a transistor below 55°C in an environment at 18°C. Assumptions 1 Steady operating conditions exist. 2 The transistor
case is isothermal at 55 ° C. 3 The contact resistance between the
transistor and the heat sink is negligible. Analysis The thermal resistance between the transistor attached to
the sink and the ambient air is determined to be AT ‘ T . —T... (55—18)°C a
'__—) Reuseambient = —'uln2itg___ = W = 1.5 C/W Q: Reese—ambient The thermal resistance of the heat sink must be below 1.5
horizontal and vertical positions, HS6071 in vertical position, positions can be selected. Problem 271
Tb = 100°C Ta = 20°C h = 20 W/m2 °c °C/W. Table 36 reveals that HSSOSO in both
and H86115 in both horizontal and vertical d = 2 mm L = 50 mm ~
Assumptions: 1. Steady state. 2. Constant properties. 3. Onedimensional temperature distribution. /ﬂ@ P=rd=nx0.002=6.283x10'3m . 2 _ 2
‘ A=i=n9;%°—2—=3.1416x105m 2/ x
From TableAl, for carbon steel, k = 60.5 W/mK, h = h = 20 W/m2 K C .
= 100  20 = 80 °c ' ab V
hP hrtd 4h 20 m = / = / = /_ = ____.—— = 25.71/meter
kAx 1“Edi/4 kd 60. 0.002 mL = 25.71 x 0205 = 1.286 Urb
>4 >4 (c) If the tip is insulated (he = 0) q = /h P k Ax 9b ta'nh mL = /20 x 6.283 x 10'3 x 60.5 x 3.1416 x 10'6 x 80 x tanh(1.286) q=0.335W $510: C170,E> _ b _ 80 _ o . . __ 0
611:0 — cosh mL — cosh 1.286 — 41'1 C " Tx=o — ex=o + Tea = 41'1 + 20 = 61'1 C 379 3123 A hot plate is to be cooled by attaching aluminum pin ﬁns on one side. The rate of heat transfer ﬁom
the 1 m by 1 m section of the plate and the effectiveness of the ﬁns are to be determined. Assumptions 1 Steady operating conditions exist. 2 The temperature along the ﬁns varies in one direction
only (normal to the plate). 3 Heat transfer ﬁ'om the ﬁn tips is negligible. 4 The heat transfer coefﬁcient is
constant and uniform over the entire ﬁn surface. 5 The thermal properties of the ﬁns are constant. 6 The heat transfer coefﬁcient accounts for the effect of radiation from the ﬁns. ‘ I
Properties The thermal conductivity of the aluminum plate and ﬁns is given to be k = 237 W/m°C. Analysis Noting that the crosssectional areas of the ﬁns are
constant, the efﬁciency of the circular ﬁns can be determined to be 2 a
m: h_p= hzrD ___ Eli: 4(35W/m .C) =15'37m4
kAc [c7702 /4 kD (237 W/m.°C)(0.0025 In)
 1
Uﬁn = tanh mL = tanh(_13.37 m x0.03 m) = 0935
mL 15.37 m" x 0.03 m The number of ﬁns, finned and unﬁnned surface areas,
and heat transfer rates ﬁom those areas are 2 "» D=0.25 cm 1m n = ——————— = 27,777
(0.006 m)(0.006 m) 2 2
Ah = 27777[7rDL +537] = 27777[7r(0.0025)(0.03) +—_”(°'O:25) ] =6.68m2 2 2
Aunﬁmd =1— 27777[”%) = 1—27777[”—(‘%2_5)—] = 035 m2 . Qﬁnned = 77meﬁn,max = UﬁuhAﬁn (Tb ‘77:»)
= 0.935(35 W/m2 .°C)(6.68 m2 )(100 — 30)°c
= 15,300 W 9‘“de = hAunﬁmd (Tb — T1,) = (35 W/m2 .°C)(0.86 m2 )(100—30)°C
= 2107 W Then the total heat transfer from the ﬁnned plate becomes Q'mmn = Q'ﬁnned + 9%.. = 15,300 +2107 =1.74><104 W = 17.4kW
The rate of heat transfer if there were no ﬁn attached to the plate would be
Anoﬁn = (1 m)(1m) =1m2
Q’noﬂn = hAnoﬁn (Tb — 7;, ) = (35 W/m2 .°C)(1m2)(100—30)°C = 2450 W Then the ﬁn effectiveness becomes Q'ﬁn _ 17,400 g = _ _
ﬁn Qnuﬁn = 7.10 O
R=2.Sm d=7m Tl=180C IV v 0W,”
T2 = k = DC Kgﬁ/I 1b
Assumptions: 1. Steady state 2. Cc‘mstant prope ' . 0.7/5 V 1905’ 3. Conduction shape factor applicable Solution: Entry 8, Table aw tion shape factor
for (amephere in an infin' medium «1’92;
Wt our law lc} q = heat transfer rate to nitrogen = Slc (T2  T1)
= 38.25 x 0.17 [10  (180)] = 1235 W
Mass rate of vaporization of liquid nitrogen q
1235 3
— E — m — 6219 x ‘0 kg/S Total mass of LN 2 = pV = 808.6 X[§]Tt x 2.53 = 5.292 x 10“ kg 3
_', LN2 Vapoﬁzed/hour = x 100 = 0_042% per hour
5.292 x10 kg V Ti = 20°C Tf = 95°C '  Air Ten Tm = 100°C h = 20 W/m2 °C 1 l ‘l,
l d = 1 cm L = 3 cm
For copper, from Table A1, k = 401 W/m K T cp = 385 J/kg °c p = 8933 kg/m3 Bi = ﬂ = W = 2.49x10'4 << 1 KW
k 401 L Lumped analysis is appropriate. : lg {n 0W” E30?“ ' Tr  Tm
From Eq. 2.8.2 Ti _ TN = exp  »
2 a. 2 :
As=ndL +2x%=n[0.015(0.03+2x0401]=1.1x10'3m2 f
0.012 ‘ m = pV = 8933 x n: x x 0.03 = 2.105 x 10'2 kg 4 . _ mp Tr‘Tm _ 2.105 x 10% 335 95100
“‘WlnTT “ 3 1“ 20—100=10218
s i co 20x1.lx10 My Ti1 = 30. °C ‘11 = 60 s
hI = 40 W/m2 °c Tal = 95°C
Tﬁ = temp. at the end of
,one minute in the first stream
h2 = 20 W/m2°c  T 2 = 20 °c 0
T = S . ' = \
‘2 Ti2 Tn ' ~
' W KWO V909?
‘ Tfl  Tml “:1 ’ 61111:l As
From Eq.2.8.2, = exp [ w ] = exp pdc ] E—
11 cml H 13
From Table A1, for 316'Stainless steel, p = 8238 kg/m3 cp = 468 Mg K
T  T 6h 1 . T  9s '
r1 cox H H __ 6x40x60 _ o
T_i"1"_T:; ‘ exp pdcp ] 30  95 ' “p [8238 x 0.004 x 468}: TH ‘ 6945 C For the second bath Ti2 = Tfl = 69.45 °'c T1322 = exp Ti2  Twz pdcp “‘22 _> Trz' 20 _ex  6 3020 x 60
" 697215"  2'0” ‘ P O
'82‘3"8——x 0._00‘_‘4 x 46—8] sz ‘ 51 C ...
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 Spring '08
 Okamoto
 Heat Transfer, Thermal conductivity, heat sink

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