NATURAL CONVECTION

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Chapter 9 Natural Convection 
Chapter 9 
NATURAL CONVECTION 
 
Physical Mechanisms of Natural Convection 
 
9-1C Natural convection is the mode of heat transfer that occurs between a solid and a fluid which moves 
under the influence of natural means. Natural convection differs from forced convection in that fluid 
motion in natural convection is caused by natural effects such as buoyancy. 
 
9-2C The convection heat transfer coefficient is usually higher in forced convection because of the higher 
fluid velocities involved. 
 
9-3C The hot boiled egg in a spacecraft will cool faster when the spacecraft is on the ground since there is 
no gravity in space, and thus there will be no natural convection currents which is due to the buoyancy 
force. 
 
9-4C The upward force exerted by a fluid on a body completely or partially immersed in it is called the 
buoyancy or “lifting” force. The buoyancy force is proportional to the density of the medium. Therefore, 
the buoyancy force is the largest in mercury, followed by in water, air, and the evacuated chamber. Note 
that in an evacuated chamber there will be no buoyancy force because of absence of any fluid in the 
medium. 
 
9-5C The buoyancy force is proportional to the density of the medium, and thus is larger in sea water than 
it is in fresh water. Therefore, the hull of a ship will sink deeper in fresh water because of the smaller 
buoyancy force acting upwards. 
 
9-6C A spring scale measures the “weight” force acting on it, and the person will weigh less in water 
because of the upward buoyancy force acting on the person’s body. 
 
9-7C The greater the volume expansion coefficient, the greater the change in density with temperature, the 
greater the buoyancy force, and thus the greater the natural convection currents. 
 
9-8C There cannot be any natural convection heat transfer in a medium that experiences no change in 
volume with temperature. 
 
9-9C The lines on an interferometer photograph represent isotherms (constant temperature lines) for a gas, 
which correspond to the lines of constant density. Closely packed lines on a photograph represent a large 
temperature gradient. 
 
9-10C The Grashof number represents the ratio of the buoyancy force to the viscous force acting on a fluid. 
The inertial forces in Reynolds number is replaced by the buoyancy forces in Grashof number. 
 9-1
Chapter 9 Natural Convection 
9-11 The volume expansion coefficient is defined as 
PT
⎟⎠
⎞⎜⎝
⎛−= ∂
∂ρ
ρβ
1 . For an ideal gas, P RT= ρ or 
ρ = P
RT
, and thus ( ) ( )
TTRT
P
TRT
P
T
RTP
P
1111/1
2
==⎟⎠
⎞⎜⎝
⎛=⎟⎠
⎞⎜⎝
⎛ −−=⎟⎠
⎞⎜⎝
⎛−= ρρρρ∂
∂
ρβ 
 
Natural Convection Over Surfaces 
 
9-12C Rayleigh number is the product of the Grashof and Prandtl numbers. 
 
9-13C A vertical cylinder can be treated as a vertical plate when D L
Gr
≥ 351 4/ . 
 
9-14C No, a hot surface will cool slower when facing down since the warmer air in this position cannot rise 
and escape easily. 
 
9-15C The heat flux will be higher at the bottom of the plate since the thickness of the boundary layer 
which is a measure of thermal resistance is the lowest there. 
 
 9-2
Chapter 9 Natural Convection 
9-16 A horizontal hot water pipe passes through a large room. The rate of heat loss from the pipe by natural 
convection and radiation is to be determined. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 4 The temperature of the outer surface of the pipe is constant. 
Properties The properties of air at 1 atm and the film temperature 
of (Ts+T∞)/2 = (65+22)/2 = 43.5°C are (Table A-15) 
Air 
T∞ = 22°C 
Pipe 
Ts = 65°C 
ε = 0.8 
L=10 m 
D = 6 cm 
1-
25
K 00316.0
K)2735.43(
11
7245.0Pr
/sm 10735.1
CW/m. 02688.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Analysis (a) The characteristic length in this case is the outer diameter of the pipe, Then, m. 06.0== DLc
 805,692)7245.0(
)/sm 10735.1(
)m 06.0)(K 2265)(K 00316.0)(m/s 81.9(Pr
)(
225
3-12
2
3
=×
−=−= −∞υ
β DTTg
Ra s 
 ( )[ ] ( )[ ] 15.137245.0/559.01 )805,692(387.06.0Pr/559.01 387.06.0
2
27/816/9
6/1
2
27/816/9
6/1
=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
+=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
+= RaNu 
 
2
2
m 885.1)m 10)(m 06.0(
C.W/m 893.5)15.13(
m 06.0
CW/m. 02688.0
===
°=°==
ππDLA
Nu
D
kh
s
 
 W477.6=°−°=−= ∞ C)2265)(m 885.1)(C.W/m 893.5()( 22TThAQ ss&
(b) The radiation heat loss from the pipe is [ ] W468.4=+−+×=−= − 44428244 )K 27322()K 27365().KW/m 1067.5)(m 885.1)(8.0()( surrssrad TTAQ σε&
 
 9-3
Chapter 9 Natural Convection 
9-17 A power transistor mounted on the wall dissipates 0.18 W. The surface temperature of the transistor is 
to be determined. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 Any heat 
transfer from the base surface is disregarded. 4 The local atmospheric pressure is 1 atm. 5 Air properties are 
evaluated at 100°C. 
Properties The properties of air at 1 atm and the given film 
temperature of 100°C are (Table A-15) 
 
1-
25
K 00268.0
K )273100(
11
7111.0Pr
/sm 10306.2
C W/m.03095.0
=+==β
=
×=υ
°=
−
fT
k
 
Analysis The solution of this problem requires a trial-and-error approach since the determination of the 
Rayleigh number and thus the Nusselt number depends on the surface temperature which is unknown. We 
start the solution process by “guessing” the surface temperature to be 165°C for the evaluation of h. This is 
the surface temperature that will give a film temperature of 100°C. We will check the accuracy of this 
guess later and repeat the calculations if necessary. 
Air 
35°C 
Power 
transistor, 0.18 W 
D = 0.4 cm 
ε = 0.1 
 The transistor loses heat through its cylindrical surface as well as its top surface. For convenience, 
we take the heat transfer coefficient at the top surface of the transistor to be the same as that of its side 
surface. (The alternative is to treat the top surface as a vertical plate, but this will double the amount of 
calculations without providing much improvement in accuracy since the area of the top surface is much 
smaller and it is circular in shape instead of being rectangular). The characteristic length in this case is the 
outer diameter of the transistor, m. 004.0== DLc Then, 
 6.292)7111.0(
)/sm 10306.2(
)m 004.0)(K 35165)(K 00268.0)(m/s 81.9(Pr
)(
225
3-12
2
3
=×
−=−= −∞υ
β DTTg
Ra s 
 ( )[ ] ( )[ ] 039.27111.0/559.01 )6.292(387.06.0Pr/559.01 387.06.0
2
27/816/9
6/1
2
27/816/9
6/1
=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
+=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
+= RaNu 
 
222
2
m 0000691.04/m) 004.0()m 0045.0)(m 004.0(4/
C.W/m 78.15)039.2(
m 004.0
CW/m. 03095.0
=+=+=
°=°==
ππππ DDLA
Nu
D
kh
s
 
and 
 [ ]
C187
)K 27325()273()1067.5)(m 0000691.0)(1.0(
C )35)(m 0000691.0)(C.W/m 8.15(W 18.0
)()(
4482
22
44
°=⎯→⎯
+−+×+
°−°=
−+−=
−
∞
s
s
s
surrssss
T
T
T
TTATThAQ σε&
which is relatively close to the assumed value of 165°C. To improve the accuracy of the result, we repeat 
the Rayleigh number calculation at new surface temperature of 187°C and determine the surface 
temperature to be 
Ts = 183°C 
Discussion W evaluated the air properties again at 100°C when repeating the calculation at the new surface 
temperature. It can be shown that the effect of this on the calculated surface temperature is less than 1°C. 
9-18 "!PROBLEM 9-18" 
 
"GIVEN" 
Q_dot=0.18 "[W]" 
 9-4
Chapter 9 Natural Convection 
"T_infinity=35 [C], parameter to be varied" 
L=0.0045 "[m]" 
D=0.004 "[m]" 
epsilon=0.1 
T_surr=T_infinity-10"[C]" 
 
"PROPERTIES" 
Fluid$='air' 
k=Conductivity(Fluid$, T=T_film) 
Pr=Prandtl(Fluid$, T=T_film) 
rho=Density(Fluid$, T=T_film, P=101.3) 
mu=Viscosity(Fluid$, T=T_film) 
nu=mu/rho 
beta=1/(T_film+273) 
T_film=1/2*(T_s+T_infinity) 
sigma=5.67E-8 "[W/m^2-K^4], Stefan-Boltzmann constant" 
g=9.807 "[m/s^2], gravitational acceleration" 
 
"ANALYSIS" 
delta=D 
Ra=(g*beta*(T_s-T_infinity)*delta^3)/nu^2*Pr 
Nusselt=(0.6+(0.387*Ra^(1/6))/(1+(0.559/Pr)^(9/16))^(8/27))^2 
h=k/delta*Nusselt 
A=pi*D*L+pi*D^2/4 
Q_dot=h*A*(T_s-T_infinity)+epsilon*A*sigma*((T_s+273)^4-(T_surr+273)^4) 
 
 
 
 
T∞ [C] Ts [C] 
10 159.9 
12 161.8 
14 163.7 
16 165.6 
18 167.5 
20 169.4 
22 171.3 
24 173.2 
26 175.1 
28 177 
30 178.9 
32 180.7 
34 182.6 
36 184.5 
38 186.4 
40 188.2 
 
 
 
 9-5
Chapter 9 Natural Convection 
10 15 20 25 30 35 40
155
160
165
170
175
180
185
190
T∞ [C]
T s
 [
C
]
 
 
 
 9-6
Chapter 9 Natural Convection 
9-19E A hot plate with an insulated back is considered. The rate of heat loss by natural convection is to be 
determined for different orientations. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 
Properties The properties of air at 1 atm and the film temperature of 
(Ts+T∞)/2 = (130+75)/2 = 102.5°F are (Table A-15) 
 
1-
23
R 001778.0
R)4605.102(
11
7256.0Pr
/sft 101823.0
FBtu/h.ft. 01535.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Analysis (a) When the plate is vertical, the characteristic length is 
the height of the plate. Then, ft. 2== LLc
 8223
3-12
2
3
10503.5)7256.0(
)/sft 101823.0(
)ft 2)(R 75130)(R 001778.0)(ft/s 2.32(Pr
)( ×=×
−=−= −∞υ
β LTTg
Ra s
 6.102
7256.0
492.01
)10503.5(387.0
825.0
Pr
492.01
Ra387.0825.0
2
27/816/9
6/18
2
27/816/9
6/1
=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
×+=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
+=Nu 
Q&
Insulation 
Air 
T∞ = 75°F 
Plate 
Ts = 130°F 
 
 L = 2 ft 
 
222
2
ft 4)ft 2(
F.Btu/h.ft 7869.0)6.102(
ft 2
FBtu/h.ft. 01535.0
===
°=°==
LA
Nu
L
kh
s
 
and 
 Btu/h 173.1=°−°=−= ∞ C)75130)(ft 4)(F.Btu/h.ft 7869.0()( 22TThAQ ss&
(b) When the plate is horizontal with hot surface facing up, the characteristic length is determined from 
 ft 5.0
4
ft 2
44
2
===== L
L
L
P
A
L ss . 
Then, 
 6223
3-12
2
3
10598.8)7256.0(
)/sft 101823.0(
)ft 5.0)(R 75130)(R 001778.0)(ft/s 2.32(Pr
)( ×=×
−=−= −∞υ
β cs LTTgRa 
 24.29)10598.8(54.054.0 4/164/1 =×== RaNu
 F.Btu/h.ft 8975.0)24.29(
ft 5.0
FBtu/h.ft. 01535.0 2 °=°== Nu
L
kh
c
 
and 
 Btu/h 197.4=°−°=−= ∞ C)75130)(ft 4)(F.Btu/h.ft 8975.0()( 22TThAQ ss&
(c) When the plate is horizontal with hot surface facing down, the characteristic length is again δ = 
and the Rayleigh number is . Then, 
0 5. ft
610598.8 ×=Ra
 62.14)10598.8(27.027.0 4/1624/1 =×== RaNu
 F.Btu/h.ft 4487.0)62.14(
ft 5.0
FBtu/h.ft. 01535.0 2 °=°== Nu
L
kh
c
 
and 
 9-7
Chapter 9 Natural Convection 
 Btu/h 98.7=°−°=−= ∞ C)75130)(ft 4)(F.Btu/h.ft 4487.0()( 22TThAQ ss&
 
 9-8
Chapter 9 Natural Convection 
9-20E "!PROBLEM 9-20E" 
 
"GIVEN" 
L=2 "[ft]" 
T_infinity=75 "[F]" 
"T_s=130 [F], parameter to be varied" 
 
"PROPERTIES" 
Fluid$='air' 
k=Conductivity(Fluid$, T=T_film) 
Pr=Prandtl(Fluid$, T=T_film) 
rho=Density(Fluid$, T=T_film, P=14.7) 
mu=Viscosity(Fluid$, T=T_film)*Convert(lbm/ft-h, lbm/ft-s) 
nu=mu/rho 
beta=1/(T_film+460) 
T_film=1/2*(T_s+T_infinity) 
g=32.2 "[ft/s^2], gravitational acceleration" 
 
"ANALYSIS" 
"(a), plate is vertical" 
delta_a=L 
Ra_a=(g*beta*(T_s-T_infinity)*delta_a^3)/nu^2*Pr 
Nusselt_a=0.59*Ra_a^0.25 
h_a=k/delta_a*Nusselt_a 
A=L^2 
Q_dot_a=h_a*A*(T_s-T_infinity) 
"(b), plate is horizontal with hot surface facing up" 
delta_b=A/p 
p=4*L 
Ra_b=(g*beta*(T_s-T_infinity)*delta_b^3)/nu^2*Pr 
Nusselt_b=0.54*Ra_b^0.25 
h_b=k/delta_b*Nusselt_b 
Q_dot_b=h_b*A*(T_s-T_infinity) 
"(c), plate is horizontal with hot surface facing down" 
delta_c=delta_b 
Ra_c=Ra_b 
Nusselt_c=0.27*Ra_c^0.25 
h_c=k/delta_c*Nusselt_c 
Q_dot_c=h_c*A*(T_s-T_infinity) 
 9-9
Chapter 9 Natural Convection 
 
Ts [F] Qa [Btu/h] Qb [Btu/h] Qc [Btu/h] 
80 7.714 9.985 4.993 
85 18.32 23.72 11.86 
90 30.38 39.32 19.66 
95 43.47 56.26 28.13 
100 57.37 74.26 37.13 
105 71.97 93.15 46.58 
110 87.15 112.8 56.4 
115 102.8 133.1 66.56 
120 119 154 77.02 
125 135.6 175.5 87.75 
130 152.5 197.4 98.72 
135 169.9 219.9 109.9 
140 187.5 242.7 121.3 
145 205.4 265.9 132.9 
150 223.7 289.5 144.7 
155 242.1 313.4 156.7 
160 260.9 337.7 168.8 
165 279.9 362.2 181.1 
170 299.1 387.1 193.5 
175 318.5 412.2 206.1 
180 338.1 437.6 218.8 
 
80 100 120 140 160 180
0
50
100
150
200
250
300
350
400
450
500
Ts [F]
Q
 [
B
tu
/h
]
Qa
Qb
Qc
 
 
 
 
 
 9-10
Chapter 9 Natural Convection 
9-21 A cylindrical resistance heater is placed horizontally in a fluid. The outer surface temperature of the 
resistance wire is to be determined for two different fluids. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 4 Any heat transfer by radiation is ignored. 5 Properties are evaluated at 
500°C for air and 40°C for water. 
Properties The properties of air at 1 atm and 500°C are (Table A-15) 
 
1-
25
K 001294.0
K)273500(
11
6986.0Pr
/sm 10804.7
C W/m.05572.0
=+==β
=
×=υ
°=
−
fT
k
 Air 
T∞ = 20°C 
Resistance 
heater, Ts
400 W 
L =1 m 
D = 0.5 cm 
The properties of water at 40°C are 
 
1-
26
K 000377.0
32.4Pr
/sm 106582.0/
C W/m.631.0
=β
=
×=ρμ=υ
°=
−
k
Analysis (a) The solution of this problem requires a trial-and-error approach since the determination of the 
Rayleigh number and thus the Nusselt number depends on the surface temperature which is unknown. We 
start the solution process by “guessing” the surface temperature to be 1200°C for the calculation of h. We 
will check the accuracy of this guess later and repeat the calculations if necessary. The characteristic length 
in this case is the outer diameter of the wire, m. 005.0== DLc Then, 
 7.214)6986.0(
)/sm 10804.7(
)m 005.0(C)201200)(K 001294.0)(m/s 81.9(
Pr
)(
 225
3-12
2
3
=×
°−=−= −∞υ
β DTTg
Ra s 
 ( )[ ] ( )[ ] 919.16986.0/559.01 )7.214(387.06.0Pr/559.01 387.06.0
2
27/816/9
6/1
2
27/816/9
6/1
=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
+=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
+= RaNu 
 
2
2
m 01571.0)m 1)(m 005.0(
C.W/m 38.21)919.1(
m 005.0
CW/m. 05572.0
===
°=°==
ππDLA
Nu
D
kh
s
 
and 
 
C1211°=
°−°=
−= ∞
s
s
ss
T
T
TThAQ
C)20)(m 01571.0)(C.W/m 38.21(W 400
)(
22
&
which is sufficiently close to the assumed value of 1200°C used in the evaluation of h, and thus it is not 
necessary to repeat calculations. 
(b) For the case of water, we “guess” the surface temperature to be 40°C. The characteristic length in this 
case is the outer diameter of the wire, m. 005.0== DLc Then, 
 197,92)32.4(
)/sm 106582.0(
)m 005.0)(K 2040)(K 000377.0)(m/s 81.9(
Pr
)(
226
3-12
2
3
=×
−=−= −∞υ
β DTTg
Ra s 
 ( )[ ] ( )[ ] 986.832.4/559.01 )197,92(387.06.0Pr/559.01 387.06.0
2
27/816/9
6/1
2
27/816/9
6/1
=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
+=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
+= RaNu 
 9-11
Chapter 9 Natural Convection 
 C.W/m 1134)986.8(m 005.0
CW/m. 631.0 2 °=°== Nu
D
kh 
and 
 
C42.5°=
°−°=
−= ∞
s
22 C)20)(m 01571.0)(C.W/m 1134(W 400
)(
T
T
TThAQ
s
ss
&
which is sufficiently close to the assumed value of 40°C in the evaluation of the properties and h. The film 
temperature in this case is (Ts+T∞)/2 = (42.5+20)/2 =31.3°C, which is close to the value of 40°C used in the 
evaluation of the properties. 
 9-12
Chapter 9 Natural Convection 
9-22 Water is boiling in a pan that is placed on top of a stove. The rate of heat loss from the cylindrical side 
surface of the pan by natural convection and radiation and the ratio of heat lost from the side surfaces of the 
pan to that by the evaporation of water are to be determined. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas 
with constant properties. 3 The local atmospheric pressure is 1 atm. 
Properties The properties of air at 1 atm and the film temperature of 
(Ts+T∞)/2 = (98+25)/2 = 61.5°C are (Table A-15) 
Vapor 
2 kg/h 
Water 
100°C 
Pan 
Ts = 98°C 
ε = 0.95 
Air 
T∞ = 25°C 
1-
25
K 00299.0
K)2735.61(
11
7198.0Pr
/sm 10910.1
CW/m. 02819.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Analysis (a) The characteristic length in this case is the height of the pan, m. 12.0== LLc Then, 
6
225
3-12
2
3
10299.7)7198.0(
)/sm 10910.1(
)m 12.0)(K 2598)(K 00299.0)(m/s 81.9(
Pr
)( ×=×
−=−= −∞υ
β LTTg
Ra s 
We can treat this vertical cylinder as a vertical plate since 
 4/14/164/1
35 and thus 0.25< 07443.0
)7198.0/10299.7(
)12.0(3535
Gr
LD
Gr
L ≥=×= 
Therefore, 
 60.28
7198.0
492.01
)10299.7(387.0
825.0
Pr
492.01
Ra387.0825.0
2
27/816/9
6/16
2
27/816/9
6/1
=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
×+=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
+=Nu 
 
2
2
m 09425.0)m 12.0)(m 25.0(
C.W/m 720.6)60.28(
m 12.0
CW/m. 02819.0
===
°=°==
ππDLA
Nu
L
kh
s
 
and 
 W46.2=°−°=−= ∞ C)2598)(m 09425.0)(C.W/m 720.6()( 22TThAQ ss&
(b) The radiation heat loss from the pan is 
 [ ] W56.1=+−+×= −= − 444282
44
)K 27325()K 27398().KW/m 1067.5)(m 09425.0)(95.0(
)( surrssrad TTAQ σε&
(c) The heat loss by the evaporation of water is 
 W 1254 kW254.1) kJ/kg2257)( kg/s3600/2( ==== fghmQ &&
Then the ratio of the heat lost from the side surfaces of the pan to that by the evaporation of water then 
becomes 
 8.2%==+= 082.0
1254
1.562.46f 
 9-13
Chapter 9 Natural Convection 
9-23 Water is boiling in a pan that is placed on top of a stove. The rate of heat loss from the cylindrical side 
surface of the pan by natural convection and radiation and the ratio of heat lost from the side surfaces of the 
pan to that by the evaporation of water are to be determined. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas 
with constant properties. 3 The local atmospheric pressure is 1 atm. 
Properties The properties of air at 1 atm and the film temperature of 
(Ts+T∞)/2 = (98+25)/2 = 61.5°C are (Table A-15) 
 
1-
25
K 00299.0
K)2735.61(
11
7198.0Pr
/sm 10910.1
CW/m. 02819.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Analysis (a) The characteristic length in this case is the height of the pan, m. 12.0== LLc Then, 
Vapor 
2 kg/h 
Water 
100°C 
Pan 
Ts = 98°C 
ε = 0.1 
Air 
T∞ = 25°C 
6
225
3-12
2
3
10299.7)7198.0(
)/sm 10910.1(
)m 12.0)(K 2598)(K 00299.0)(m/s 81.9(
Pr
)( ×=×
−=−= −∞υ
β LTTg
Ra s 
We can treat this vertical cylinder as a vertical plate since 
 4/14/164/1
35 and thus 0.25< 07443.0
)7198.0/10299.7(
)12.0(3535
Gr
LD
Gr
L ≥=×= 
Therefore, 
 60.28
7198.0
492.01
)10299.7(387.0
825.0
Pr
492.01
Ra387.0825.0
2
27/816/9
6/16
2
27/816/9
6/1
=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
×+=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
+=Nu 
 
2
2
m 09425.0)m 12.0)(m 25.0(
C.W/m 720.6)60.28(
m 12.0
CW/m. 02819.0
===
°=°==
ππDLA
Nu
L
kh
s
 
and 
 W46.2=°−°=−= ∞ C)2598)(m 09425.0)(C.W/m 720.6()( 22TThAQ ss&
(b) The radiation heat loss from the pan is 
 [ ] W5.9=+−+×= −= − 444282
44
)K 27325()K 27398().KW/m 1067.5)(m 09425.0)(10.0(
)( surrssrad TTAQ σε&
(c) The heat loss by the evaporation of water is 
 W 1254 kW254.1) kJ/kg2257)( kg/s3600/2( ==== fghmQ &&
Then the ratio of the heat lost from the side surfaces of the pan to that by the evaporation of water then 
becomes 
 4.2%==+= 042.0
1254
9.52.46f 
 
 9-14
Chapter 9 Natural Convection 
9-24 Some cans move slowly in a hot water container made of sheet metal. The rate of heat loss from the 
four side surfaces of the container and the annual cost of those heat losses are to be determined. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 3 Heat loss from the top surface is disregarded. 
Properties The properties of air at 1 atm and the film temperature of 
(Ts+T∞)/2 = (55+20)/2 = 37.5°C are (Table A-15) 
Water bath 
55°C 
Aerosol can 
 
1-
25
K 003221.0
K)2735.37(
11
7261.0Pr
/sm 10678.1
CW/m. 02644.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Analysis The characteristic length in this case is the height of the bath, 
 Then, m. 5.0== LLc
 8225
3-12
2
3
10565.3)7261.0(
)/sm 10678.1(
)m 5.0)(K 2055)(K 003221.0)(m/s 81.9(
Pr
)( ×=×
−=−= −∞υ
β LTTg
Ra s 
 84.89
7261.0
492.01
)10565.3(387.0
825.0
Pr
492.01
Ra387.0825.0
2
27/816/9
6/18
2
27/816/9
6/1
=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
×+=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
+=Nu 
 
[ ] 2
2
m 5.4)m 5.3)(m 5.0()m 1)(m 5.0(2
C.W/m 75.4)84.89(
m 5.0
CW/m. 02644.0
=+=
°=°==
sA
Nu
L
kh
 
and 
 W 1.748C)2055)(m 5.4)(C.W/m 75.4()( 22 =°−°=−= ∞TThAQ ss&
The radiation heat loss is 
 [ ] W9.750)K 27320()K 27355().KW/m 1067.5)(m 5.4)(7.0( )( 444282
44
 =+−+×=
−=
−
surrssrad TTAQ σε&
Then the total rate of heat loss becomes 
 W1499=+=+= 9.7501.748rad
convection
naturaltotal QQQ &&&
The amount and cost of the heat loss during one year is 
 kWh131,13 h)8760)( kW499.1( ==Δ= tQQ totaltotal &
 $1116== )kWh/085.0)($ kWh131,13(Cost 
 9-15
Chapter 9 Natural Convection 
9-25 Some cans move slowly in a hot water container made of sheet metal. It is proposed to insulate the 
side and bottom surfaces of the container for $350. The simple payback period of the insulation to pay for 
itself from the energy it saves is to be determined. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 3 Heat loss from the top surface is disregarded. 
Properties Insulation will drop the outer surface temperature to a value close to the ambient temperature. 
The solution of this problem requires a trial-and-error approach since the determination of the Rayleigh 
number and thus the Nusselt number depends on the surface temperature, which is unknown. We assume 
the surface temperature to be 26°C. The properties of air at the anticipated film temperature of 
(26+20)/2=23°C are (Table A-15) 
 
 
1-
25
K 00338.0
K)27323(
11
7301.0Pr
/sm 10543.1
CW/m. 02536.0
=+==
=
×=
°=
−
fT
k
β
υ
 
 
Analysis We start the solution process by “guessing” the outer surfacetemperature to be 26 ° . We will 
check the accuracy of this guess later and repeat the calculations if necessary with a better guess based on 
the results obtained. The characteristic length in this case is the height of the tank, Then, 
C
m. 5.0== LLc
Aerosol can 
 
insulation 
Water bath 
55°C 
 7225
3-12
2
3
10622.7)7301.0(
)/sm 10543.1(
)m 5.0)(K 2026)(K 00338.0)(m/s 81.9(
Pr
)( ×=×
−=−= −∞υ
β LTTg
Ra s 
 53.56
7301.0
492.01
)10622.7(387.0
825.0
Pr
492.01
Ra387.0825.0Nu
2
27/816/9
6/17
2
27/816/9
6/1
=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
×+=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
+= 
 
[ ] 2
2
m 7.4)m 60.3)(m 5.0()m 10.1)(m 5.0(2
C.W/m 868.2)53.56(
m 5.0
CW/m. 02536.0
=+=
°=°==
sA
Nu
L
kh
 
Then the total rate of heat loss from the outer surface of the insulated tank by convection and radiation 
becomes 
W5.97
])K 27320()K 27326)[(.KW/m 1067.5)(m 7.4)(1.0(+
C)2026)(m 7.4)(C.W/m 868.2(
)()(
444282
22
44
 =
+−+×
°−°=
−+−=+=
−
∞ surrssssradconv TTATThAQQQ σε&&&
 
In steady operation, the heat lost by the side surfaces of the tank must be equal to the heat lost from the 
exposed surface of the insulation by convection and radiation, which must be equal to the heat conducted 
through the insulation. The second conditions requires the surface temperature to be 
 
m 05.0
C)(55
)m C)(4.7W/m. 035.0(W 97.5 2tank
°−°=→−== sssinsulation TL
TT
kAQQ && 
It gives Ts = 25.38°C, which is very close to the assumed temperature, 26°C. Therefore, there is no need to 
repeat the calculations. 
 The total amount of heat loss and its cost during one year are 
 kWh7.853 h)8760)(W 5.97( ==Δ= tQQ totaltotal &
 9-16
Chapter 9 Natural Convection 
 $72.6)kWh/085.0)($ kWh7.853(Cost == 
Then money saved during a one-year period due to insulation becomes 
 1043$6.72$1116$CostCostsaved Money =−=−=
insulation
with
insulation
without 
where $1116 is obtained from the solution of Problem 9-24. 
The insulation will pay for itself in 
 days 122 =yr 0.3354===
yr/1043$
350$
saved Money
CostriodPayback pe 
Discussion We would definitely recommend the installation of insulation in this case. 
 9-17
Chapter 9 Natural Convection 
9-26 A printed circuit board (PCB) is placed in a room. The average temperature of the hot surface of the 
board is to be determined for different orientations. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with 
constant properties. 3 The local atmospheric pressure is 1 atm. 3 The heat 
loss from the back surface of the board is negligible. 
Properties The properties of air at 1 atm and the anticipated film 
temperature of (Ts+T∞)/2 = (45+20)/2 = 32.5°C are (Table A-15) 
 
1-
25
K 003273.0
K)2735.32(
11
7275.0Pr
/sm 10631.1
CW/m. 02607.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Analysis The solution of this problem requires a trial-and-error approach since the determination of the 
Rayleigh number and thus the Nusselt number depends on the surface temperature which is unknown 
 L = 0.2 m 
Insulation 
Air 
T∞ = 20°C 
PCB, Ts 
8 W 
(a) Vertical PCB . We start the solution process by “guessing” the surface temperature to be 45°C for the 
evaluation of the properties and h. We will check the accuracy of this guess later and repeat the calculations 
if necessary. The characteristic length in this case is the height of the PCB, m. 2.0== LLc Then, 
 7225
3-12
2
3
10756.1)7275.0(
)/sm 10631.1(
)m 2.0)(K 2045)(K 003273.0)(m/s 81.9(Pr
)( ×=×
−=−= −∞υ
β LTTg
Ra s 
 78.36
7275.0
492.01
)10756.1(387.0825.0
Pr
492.01
Ra387.0825.0Nu
2
27/816/9
6/17
2
27/816/9
6/1
=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
×+=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
+= 
 
2
2
m 03.0)m 2.0)(m 15.0(
C.W/m 794.4)78.36(
m 2.0
CW/m. 02607.0
==
°=°==
sA
Nu
L
kh
 
Heat loss by both natural convection and radiation heat can be expressed as 
 [ ]448222
44
)K 27320()273()1067.5)(m 03.0)(8.0(C)20)(m 03.0)(C.W/m 794.4(W 8
)()(
+−+×+°−°=
−+−=
−
∞
ss
surrssss
TT
TTATThAQ σε&
Its solution is 
 Ts = °46.6 C
which is sufficiently close to the assumed value of 45°C for the evaluation of the properties and h. 
(b) Horizontal, hot surface facing up Again we assume the surface temperature to be 45 and use the 
properties evaluated above. The characteristic length in this case is 
°C
 m. 0429.0
)m 15.0m 2.0(2
)m 15.0)(m 20.0( =+== p
A
L sc 
Then, 
5
225
3-12
2
3
10728.1)7275.0(
)/sm 10631.1(
)m 0429.0)(K 2045)(K 003273.0)(m/s 81.9(Pr
)( ×=×
−=−= −∞υ
β cs LTTgRa 
 01.11)10728.1(54.054.0 4/154/1 =×== RaNu
 C.W/m 696.6)01.11(
m 0429.0
CW/m. 02607.0 2 °=°== Nu
L
kh
c
 
 9-18
Chapter 9 Natural Convection 
Heat loss by both natural convection and radiation heat can be expressed as 
 
])K 27320()273)[(1067.5)(m 03.0)(8.0(C)20)(m 03.0)(C.W/m 696.6(W 8
)()(
448222
44
+−+×+°−°=
−+−=
−
∞
ss
surrssss
TT
TTATThAQ σε&
Its solution is 
 Ts = °42.6 C
which is sufficiently close to the assumed value of 45°C in the evaluation of the properties and h. 
(c) Horizontal, hot surface facing down This time we expect the surface temperature to be higher, and 
assume the surface temperature to be 50 . We will check this assumption after obtaining result and 
repeat calculations with a better assumption, if necessary. The properties of air at the film temperature of 
°C
C35
2
2050
2
°=+=+= ∞TTT sf are (Table A-15) 
 
1-
25
K 003247.0
K)27335(
11
7268.0Pr
/sm 10655.1
CW/m. 02625.0
=+==
=
×=
°=
−
fT
k
β
υ
 
The characteristic length in this case is, from part (b), Lc = 0.0429 m. Then, 
 379,166)7268.0(
)/sm 10655.1(
)m 0429.0)(K 2050)(K 003247.0)(m/s 81.9(Pr
)(
225
3-12
2
3
=×
−=−= −∞υ
β cs LTTgRa 
 453.5)379,166(27.027.0 4/14/1 === RaNu
 C.W/m 340.3)453.5(
m 0429.0
CW/m. 02625.0 2 °=°== Nu
L
kh
c
 
Considering both natural convection and radiation heat loses 
 
])K 27320()273)[(1067.5)(m 03.0)(8.0(C)20)(m 03.0)(C.W/m 340.3(W 8 
)()(
448222
44
+−+×+°−°=
−+−=
−
∞
ss
surrssss
TT
TTATThAQ σε&
Its solution is 
 Ts = °50.7 C
which is very close to the assumed value. Therefore, there is no need to repeat calculations. 
 
 9-19
Chapter 9 Natural Convection 
9-27 "!PROBLEM 9-27" 
 
"GIVEN" 
L=0.2 "[m]" 
w=0.15 "[m]" 
"T_infinity=20 [C], parameter to be varied" 
Q_dot=8 "[W]" 
epsilon=0.8 "parameter to be varied" 
T_surr=T_infinity 
 
"PROPERTIES" 
Fluid$='air' 
k=Conductivity(Fluid$, T=T_film) 
Pr=Prandtl(Fluid$, T=T_film) 
rho=Density(Fluid$, T=T_film, P=101.3) 
mu=Viscosity(Fluid$, T=T_film) 
nu=mu/rho 
beta=1/(T_film+273) 
T_film=1/2*(T_s_a+T_infinity) 
sigma=5.67E-8 "[W/m^2-K^4], Stefan-Boltzmann constant" 
g=9.807 "[m/s^2], gravitational acceleration" 
 
"ANALYSIS" 
"(a), plate is vertical" 
delta_a=L 
Ra_a=(g*beta*(T_s_a-T_infinity)*delta_a^3)/nu^2*Pr 
Nusselt_a=0.59*Ra_a^0.25 
h_a=k/delta_a*Nusselt_a 
A=w*L 
Q_dot=h_a*A*(T_s_a-T_infinity)+epsilon*A*sigma*((T_s_a+273)^4-(T_surr+273)^4) 
"(b), plate is horizontal with hot surface facing up" 
delta_b=A/p 
p=2*(w+L) 
Ra_b=(g*beta*(T_s_b-T_infinity)*delta_b^3)/nu^2*Pr 
Nusselt_b=0.54*Ra_b^0.25 
h_b=k/delta_b*Nusselt_b 
Q_dot=h_b*A*(T_s_b-T_infinity)+epsilon*A*sigma*((T_s_b+273)^4-(T_surr+273)^4) 
"(c), plate is horizontal with hot surfacefacing down" 
delta_c=delta_b 
Ra_c=Ra_b 
Nusselt_c=0.27*Ra_c^0.25 
h_c=k/delta_c*Nusselt_c 
Q_dot=h_c*A*(T_s_c-T_infinity)+epsilon*A*sigma*((T_s_c+273)^4-(T_surr+273)^4) 
 
 9-20
Chapter 9 Natural Convection 
 
T∞ [F] Ts,a [C] Ts,b [C] Ts,c [C] 
5 32.54 28.93 38.29 
7 34.34 30.79 39.97 
9 36.14 32.65 41.66 
11 37.95 34.51 43.35 
13 39.75 36.36 45.04 
15 41.55 38.22 46.73 
17 43.35 40.07 48.42 
19 45.15 41.92 50.12 
21 46.95 43.78 51.81 
23 48.75 45.63 53.51 
25 50.55 47.48 55.21 
27 52.35 49.33 56.91 
29 54.16 51.19 58.62 
31 55.96 53.04 60.32 
33 57.76 54.89 62.03 
35 59.56 56.74 63.74 
 
 
 
5 10 15 20 25 30 35
25
30
35
40
45
50
55
60
65
T∞ [C]
T s
 [
C
]
Ts,a
Ts,b
Ts,c
 
 
 9-21
Chapter 9 Natural Convection 
9-28 Absorber plates whose back side is heavily insulated is placed horizontally outdoors. Solar radiation is 
incident on the plate. The equilibrium temperature of the plate is to be determined for two cases. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 
Properties The properties of air at 1 atm and the anticipated film 
temperature of (Ts+T∞)/2 = (115+25)/2 = 70°C are (Table A-15) 
Insulation 
Air 
T∞ = 25°C 
Absorber plate 
αs = 0.87 
ε = 0.09 
700 W/m2 
 L = 1.2 m 
1-
25
K 002915.0
K)27370(
11
7177.0Pr
/sm 10995.1
CW/m. 02881.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Analysis The solution of this problem requires a trial-and-error approach since the determination of the 
Rayleigh number and thus the Nusselt number depends on the surface temperature which is unknown. We 
start the solution process by “guessing” the surface temperature to be 115°C for the evaluation of the 
properties and h. We will check the accuracy of this guess later and repeat the calculations if necessary. 
The characteristic length in this case is m. 24.0
)m 8.0m 2.1(2
)m 8.0)(m 2.1( =+== p
AL sc Then, 
 
7
225
3-12
2
3
10414.6)7177.0(
)/sm 10995.1(
)m 24.0)(K 25115)(K 002915.0)(m/s 81.9(Pr
)( ×=×
−=−= −∞υ
β cs LTTgRa 
 33.48)10414.6(54.054.0 4/174/1 =×== RaNu
 C.W/m 801.5)33.48(
m 24.0
CW/m. 02881.0 2 °=°== Nu
L
kh
c
 
 2m 96.0)m 2.1)(m 8.0( ==sA
In steady operation, the heat gain by the plate by absorption of solar radiation 
must be equal to the heat loss by natural convection and radiation. Therefore, 
 W 6.584)m 96.0)(W/m 700)(87.0( 22 === sAqQ && α
])K 27310()273)[(1067.5)(m 96.0)(09.0(C)25)(m 96.0)(C.W/m 801.5(W 584.6
)()(
448222
44
+−+×+°−°=
−+−=
−
∞
ss
skyssss
TT
TTATThAQ σε&
Its solution is Ts = °115.6 C
which is identical to the assumed value. Therefore there is no need to repeat calculations. 
 If the absorber plate is made of ordinary aluminum which has a solar absorptivity of 0.28 and an 
emissivity of 0.07, the rate of solar gain becomes 
 W 2.188)m 96.0)(W/m 700)(28.0( 22 === sAqQ && α
Again noting that in steady operation the heat gain by the plate by absorption of solar radiation must be 
equal to the heat loss by natural convection and radiation, and using the convection coefficient determined 
above for convenience, 
])K 27310()273)[(1067.5)(m 96.0)(07.0(C)25)(m 96.0)(C.W/m 801.5(W 188.2
)()(
448222
44
+−+×+°−°=
−+−=
−
∞
ss
skyssss
TT
TTATThAQ σε&
 
Its solution is Ts = 55.2°C 
Repeating the calculations at the new film temperature of 40°C, we obtain 
h = 4.524 W/m2.°C and Ts = 62.8°C 
 9-22
Chapter 9 Natural Convection 
9-29 An absorber plate whose back side is heavily insulated is placed horizontally outdoors. Solar radiation 
is incident on the plate. The equilibrium temperature of the plate is to be determined for two cases. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 
Insulation 
Air 
T∞ = 25°C 
Absorber plate 
αs = 0.98 
ε = 0.98 
700 W/m2
 L = 1.2 m 
Properties The properties of air at 1 atm and the anticipated film 
temperature of (Ts+T∞)/2 = (70+25)/2 = 47.5°C are (Table A-15) 
 
1-
25
K 00312.0
K)2735.47(
11
7235.0Pr
/sm 10774.1
CW/m. 02717.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Analysis The solution of this problem requires a trial-and-error approach since the determination of the 
Rayleigh number and thus the Nusselt number depends on the surface temperature which is unknown. We 
start the solution process by “guessing” the surface temperature to be 70°C for the evaluation of the 
properties and h. We will check the accuracy of this guess later and repeat the calculations if necessary. 
The characteristic length in this case is m. 24.0
)m 8.0m 2.1(2
)m 8.0)(m 2.1( =+== p
AL sc Then, 
 7225
3-12
2
3
10379.4)7235.0(
)/sm 10774.1(
)m 24.0)(K 2570)(K 00312.0)(m/s 81.9(Pr
)( ×=×
−=−= −∞υ
β cs LTTgRa 
 93.43)10379.4(54.054.0 4/174/1 =×== RaNu
 C.W/m 973.4)93.43(
m 24.0
CW/m. 02717.0 2 °=°== Nu
L
kh
c
 
 2m 96.0)m 2.1)(m 8.0( ==sA
In steady operation, the heat gain by the plate by absorption of solar radiation must be equal to the heat loss 
by natural convection and radiation. Therefore, 
 W 6.658)m 96.0)(W/m 700)(98.0( 22 === sAqQ && α
])K 27310()273)[(1067.5)(m 96.0)(98.0(C)25)(m 96.0)(C.W/m 973.4(W 658.6
)()(
448222
44
+−+×+°−°=
−+−=
−
∞
ss
surrssss
TT
TTATThAQ σε&
Its solution is Ts = °73.5 C
which is close to the assumed value. Therefore there is no need to repeat calculations. 
 For a white painted absorber plate, the solar absorptivity is 0.26 and the emissivity is 0.90. Then 
the rate of solar gain becomes 
 W 7.174)m 96.0)(W/m 700)(26.0( 22 === sAqQ && α
Again noting that in steady operation the heat gain by the plate by absorption of solar radiation must be 
equal to the heat loss by natural convection and radiation, and using the convection coefficient determined 
above for convenience (actually, we should calculate the new h using data at a lower temperature, and 
iterating if necessary for better accuracy), 
])K 27310()273)[(1067.5)(m 96.0)(90.0(C)25)(m 96.0)(C.W/m 973.4(=W 174.7 
)()(
448222
44
+−+×+°−°
−+−=
−
∞
ss
surrssss
TT
TTATThAQ σε&
Its solution is Ts = °35.0 C
Discussion If we recalculated the h using air properties at 30°C, we would obtain 
h = 3.47 W/m2.°C and Ts = 36.6°C. 
9-30 A resistance heater is placed along the centerline of a horizontal cylinder whose two circular side 
surfaces are well insulated. The natural convection heat transfer coefficient and whether the radiation effect 
is negligible are to be determined. 
 9-23
Chapter 9 Natural Convection 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas 
with constant properties. 3 The local atmospheric pressure is 1 atm. 
Analysis The heat transfer surface area of the cylinder is 
 2m 05027.0)m 8.0)(m 02.0( === ππDLA
Noting that in steady operation the heat dissipated from the outer 
surface must equal to the electric power consumed, and radiation 
is negligible, the convection heat transfer is determined to be 
Air 
T∞ = 20°C 
Cylinder 
Ts = 120°C 
ε = 0.1 
L = 0.8 m 
D = 2 cm 
Resistance 
heater, 40 W 
 C. W/m7.96 2 °=°−=−=→−= ∞∞ C)20120)(m 05027.0(
W 40
)(
 )( 2TTA
QhTThAQ
ss
ss
&& 
The radiation heat loss from the cylinder is 
 
W7.4])K 27320()K 273120)[(.KW/m 1067.5)(m 05027.0)(1.0(
)(
444282
44
 =+−+×=
−=
−
surrssrad TTAQ σε&
Therefore, the fraction of heat loss by radiation is 
 %8.111175.0
W 40
W 7.4fraction Radiation ====
total
radiation
Q
Q
&
&
 
which is greater than 5%. Therefore, the radiation effect is still more than acceptable,and corrections must 
be made for the radiation effect. 
 9-24
Chapter 9 Natural Convection 
9-31 A thick fluid flows through a pipe in calm ambient air. The pipe is heated electrically. The power 
rating of the electric resistance heater and the cost of electricity during a 10-h period are to be determined.√ 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 
Properties The properties of air at 1 atm and the film temperature of 
(Ts+T∞)/2 = (25+0)/2 = 12.5°C are (Table A-15) 
Asphalt
L = 100 m 
 
 D =30 cm 
Ts = 25°C 
ε = 0.8 
Tsky = -30°C
T∞ = 0°C 
 
1-
25
K 003503.0
K)2735.12(
11
7330.0Pr
/sm 10448.1
CW/m. 02458.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Analysis The characteristic length in this case is the outer diameter of the pipe, m. 3.0== DLc Then, 
 7225
3-12
2
3
10106.8)7330.0(
)/sm 10448.1(
)m 3.0)(K 025)(K 003503.0)(m/s 81.9(Pr
)( ×=×
−=−= −∞υ
β cs LTTgRa 
 ( )[ ] ( )[ ] 29.537330.0/559.01 )10106.8(387.06.0Pr/559.01 387.06.0
2
27/816/9
6/17
2
27/816/9
6/1
=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
×+=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
+= RaNu 
 
2
2
m 25.94)m 100)(m 3.0(
C.W/m366.4)29.53(
m 3.0
CW/m. 02458.0
===
°=°==
ππDLA
Nu
L
kh
s
c
 
 
and 
 W 287,10C)025)(m 25.94)(C.W/m 366.4()( 22 =°−°=−= ∞TThAQ ss&
The radiation heat loss from the cylinder is 
 
W808,18])K 27330()K 27325)[(.KW/m 1067.5)(m 25.94)(8.0(
)(
444282
44
 =+−−+×=
−=
−
surrssrad TTAQ σε&
Then, 
 kW 29.1==+=+= W094,29808,18287,10radiation
convection
naturaltotal QQQ &&&
The total amount and cost of heat loss during a 10 hour period is 
 kWh9.290h) kW)(10 1.29( ==Δ= tQQ &
 $26.18== /kWh)kWh)($0.09 9.290(Cost 
 
 
 
 9-25
Chapter 9 Natural Convection 
9-32 A fluid flows through a pipe in calm ambient air. The pipe is heated electrically. The thickness of the 
insulation needed to reduce the losses by 85% and the money saved during 10-h are to be determined. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 
Properties Insulation will drop the outer surface temperature to a value close to the ambient temperature, 
and possible below it because of the very low sky temperature for radiation heat loss. For convenience, we 
use the properties of air at 1 atm and 5°C (the anticipated film temperature) (Table A-15), 
 
1-
25
K 003597.0
K)2735(
11
7350.0Pr
/sm 10382.1
CW/m. 02401.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Asphalt
L = 100 m 
 
 D + 2tins 
25°C 
Insulation 
ε = 0.1 
Tsky = -30°C
T∞ = 0°C 
Analysis The rate of heat loss in the previous problem was 
obtained to be 29,094 W. Noting that insulation will cut down 
the heat losses by 85%, the rate of heat loss will be 
 W 4364W 094,2915.0)85.01( insulation no =×=−= QQ &&
The amount of energy and money insulation will save during a 10-h period is simply determined from 
 kWh3.247 h) kW)(10094.2985.0(, =×=Δ= tQQ savedtotalsaved &
 $22.26== )kWh/09.0)($ kWh3.247(=energy) of cost tsaved)(Uni Energy(saved Money 
The characteristic length in this case is the outer diameter of the insulated pipe, 
 where tinsulinsulc ttDL 23.02 +=+= insul is the thickness of insulation in m. Then the problem can be 
formulated for Ts and tinsul as follows: 
 )7350.0(
)/sm 10382.1(
)23.0(K])273)[(K 003597.0)(m/s 81.9(
Pr
)(
225
3-12
2
3
−
∞
×
+−=−= insulscs tTLTTgRa υ
β
 
( )[ ] ( )[ ]
2
27/816/9
6/1
2
27/816/9
6/1
7350.0/559.01
387.06.0
Pr/559.01
387.06.0
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
+=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
+= RaRaNu 
 
m) )(10023.0(
CW/m. 02401.0
0 insuls
cc
tLDA
Nu
L
Nu
L
kh
+==
°==
ππ
 
The total rate of heat loss from the outer surface of the insulated pipe by convection and radiation becomes 
 
])K 27330()[.KW/m 1067.5()1.0(+)273(4364
)()(
44428
44
+−−×−=
−+−=+=
−
∞
ssss
surrssssradconv
TAThA
TTATThAQQQ σε&&&
In steady operation, the heat lost by the side surfaces of the pipe must be equal to the heat lost from the 
exposed surface of the insulation by convection and radiation, which must be equal to the heat conducted 
through the insulation. Therefore, 
 
]3.0/)23.0ln[(
K)m)(298 C)(100W/m. 035.0(2
W 4364 
)/ln(
)(2 tank
insul
s
o
s
insulation t
T
DD
TTkL
QQ +
−°=→−== ππ&& 
The solution of all of the equations above simultaneously using an equation solver gives Ts = 281.5 K = 
8.5°C and tinsul = 0.013 m = 1.3 cm. 
Note that the film temperature is (8.5+0)/2 = 4.25°C which is very close to the assumed value of 
5°C. Therefore, there is no need to repeat the calculations using properties at this new film temperature. 
9-33E An industrial furnace that resembles a horizontal cylindrical enclosure whose end surfaces are well 
insulated. The highest allowable surface temperature of the furnace and the annual cost of this loss to the 
plant are to be determined. 
 9-26
Chapter 9 Natural Convection 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 
L = 13 ft 
Furnace 
ε = 0.1 
Air 
T∞ = 75°F 
D = 8 ft 
Properties The properties of air at 1 atm and the anticipated film 
temperature of (Ts+T∞)/2=(140+75)/2=107.5°F are (Table A-15) 
 
1-
23
R 001762.0
R)4605.107(
11
7249.0Pr
/sft 101851.0
FBtu/h.ft. 01546.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Analysis The solution of this problem requires a trial-and-error approach since the determination of the 
Rayleigh number and thus the Nusselt number depends on the surface temperature which is unknown. We 
start the solution process by “guessing” the surface temperature to be 140°F for the evaluation of the 
properties and h. We will check the accuracy of this guess later and repeat the calculations if necessary. 
The characteristic length in this case is the outer diameter of the furnace, ft. 8== DLc Then, 
 10223
3-12
2
3
10996.3)7249.0(
)/sft 101851.0(
)ft 8)(R 75140)(R 001762.0)(ft/s 2.32(Pr
)( ×=×
−=−= −∞υ
β DTTg
Ra s 
 ( )[ ] ( )[ ] 9.3767249.0/559.01 )10996.3(387.06.0Pr/559.01 387.06.0
2
27/816/9
6/110
2
27/816/9
6/1
=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
×+=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
+= RaNu 
 
2
2
ft 7.326)ft 13)(ft 8(
F.Btu/h.ft 7287.0)9.376(
ft 8
FBtu/h.ft. 01546.0
===
°=°==
ππDLA
Nu
D
kh
s
 
The total rate of heat generated in the furnace is 
 Btu/h 10936.3Btu/therm) 100,000( therms/h)48)(82.0( 6×==genQ&
Noting that 1% of the heat generated can be dissipated by natural convection and radiation , 
 Btu/h 360,39Btu/h) 10936.3)(01.0( 6 =×=Q&
The total rate of heat loss from the furnace by natural convection and radiation can be expressed as 
 
])R 46075()[.RBtu/h.ft 101714.0)(m 7.326)(85.0( 
)]R 46075()[ft 7.326(F).Btu/h.ft 7287.0(Btu/h 360,39
)()(
444282
22
44
+−×+
+−°=
−+−=
−
∞
s
s
surrssss
T
T
TTATThAQ σε&
Its solution is 
 F141.8°== R 8.601sT
which is very close to the assumed value. Therefore, there is no need to repeat calculations. 
 The total amount of heat loss and its cost during a-2800 hour period is 
 Btu10102.1 h)2800)(Btu/h 360,39( 8 ×==Δ= tQQ totaltotal &
 $716.4=×= therm)/65.0)($ therm000,100/10102.1(Cost 8
 9-27
Chapter 9 Natural Convection 
9-34 A glass window is considered. The convection heat transfer coefficient on the inner side of the 
window, the rate of total heat transfer through the window, and the combinednatural convection and 
radiation heat transfer coefficient on the outer surface of the window are to be determined. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas 
with constant properties. 3 The local atmospheric pressure is 1 atm. 
Q&
Outdoors 
-5°C 
Glass 
Ts = 5°C 
ε = 0.9 
 L = 1.2 m 
Room 
T∞ = 25°C Properties The properties of air at 1 atm and the film temperature of 
(Ts+T∞)/2 = (5+25)/2 = 15°C are (Table A-15) 
 
1-
25
K 003472.0
K)27315(
11
7323.0Pr
/sm 10471.1
CW/m. 02476.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Analysis (a) The characteristic length in this case is the height of the window, m. 2.1== LLc Then, 
 9225
3-12
2
3
10986.3)7323.0(
)/sm 10471.1(
)m 2.1)(K 525)(K 34720.0)(m/s 81.9(Pr
)( ×=×
−=−= −∞
0
υ
β cs LTTgRa 
 7.189
7323.0
492.01
)10986.3(387.0
825.0
Pr
492.01
Ra387.0825.0
2
27/816/9
6/19
2
27/816/9
6/1
=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
×+=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
+=Nu 
 
2m 4.2m) m)(2 2.1(
)7.189(
m 2.1
CW/m. 02476.0
==
°=°==
sA
Nu
L
kh C. W/m3.915 2
 
(b) The sum of the natural convection and radiation heat transfer from the room to the window is 
 W 9.187C)525)(m 4.2)(C.W/m 915.3()( 22convection =°−°=−= ∞ ss TThAQ&
 
W3.234])K 2735()K 27325)[(.KW/m 1067.5)(m 4.2)(9.0(
)(
444282
44
radiation
 =+−+×=
−=
−
ssurrs TTAQ σε&
 W422.2=+=+= 3.2349.187radiationconvectiontotal QQQ &&&
(c) The outer surface temperature of the window can be determined from 
 C65.3
)m 4.2)(CW/m. 78.0(
)m 006.0)(W 346(C5)( 2
total
,,,,total °=°−°=−=⎯→⎯−= sisososis
s
kA
tQ
TTTT
t
kA
Q
&& 
Then the combined natural convection and radiation heat transfer coefficient on the outer window surface becomes 
C. W/m20.35 2 °=°−−=−=
−=
∞
∞
C)]5(65.3)[m 4.2(
W 346
)(
 or 
)(
2
,,
total
combined
,,combinedtotal
ooss
ooss
TTA
Q
h
TTAhQ
&
&
 
Note that and thus the thermal resistance R of a layer is proportional to the temperature drop 
across that layer. Therefore, the fraction of thermal resistance of the glass is equal to the ratio of the 
temperature drop across the glass to the overall temperature difference, 
ΔT QR= &
 4.5%)(or 045.0
)5(25
65.35
total
glass
total
glass =−−
−=Δ
Δ=
TR
T
R
R
 
which is low. Thus it is reasonable to neglect the thermal resistance of the glass. 
 9-28
Chapter 9 Natural Convection 
9-35 An insulated electric wire is exposed to calm air. The temperature at the interface of the wire and the 
plastic insulation is to be determined. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 
Properties The properties of air at 1 atm and the anticipated film 
temperature of (Ts+T∞)/2 = (50+30)/2 = 40°C are (Table A-15) Air 
T∞ = 30°C 
Ts 
ε = 0.9 
L = 12 m 
D = 6 mm 
Resistance 
heater 
 
1-
25
K 003195.0
K)27340(
11
7255.0Pr
/sm 10702.1
CW/m. 02662.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Analysis The solution of this problem requires a trial-and-error approach since the determination of the 
Rayleigh number and thus the Nusselt number depends on the surface temperature which is unknown. We 
start the solution process by “guessing” the surface temperature to be 50°C for the evaluation of the 
properties and h. We will check the accuracy of this guess later and repeat the calculations if necessary. 
The characteristic length in this case is the outer diameter of the insulated wire Lc = D = 0.006 m. Then, 
 3.339)7255.0(
)/sm 10702.1(
)m 006.0)(K 3050)(K 003195.0)(m/s 81.9(
Pr
)(
225
3-12
2
3
=×
−=−= −∞υ
β DTTg
Ra s 
 ( )[ ] ( )[ ] 101.27255.0/559.01 )3.339(387.06.0Pr/559.01 387.06.0
2
27/816/9
6/1
2
27/816/9
6/1
=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
+=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
+= RaNu 
 
2
2
m 2262.0m) m)(12 006.0(
C.W/m 327.9)101.2(
m 006.0
CW/m. 02662.0
===
°=°==
ππDLA
Nu
D
kh
s
 
The rate of heat generation, and thus the rate of heat transfer is 
 & (Q VI= = =8 8 V)(10 A) W0
Considering both natural convection and radiation, the total rate of heat loss can be expressed as 
 
])K 27330()273)[(.KW/m 1067.5)(m 2262.0)(9.0( 
C)30)(m 226.0)(C.W/m 327.9(W 80
)()(
444282
22
44
+−+×+
°−°=
−+−=
−
∞
s
s
surrssss
T
T
TTATThAQ σε&
Its solution is 
 C6.52 °=sT
which is close to the assumed value of 50°C. Then the temperature at the interface of the wire and the 
plastic cover in steady operation becomes 
C57.5°=°°=+=⎯→⎯−= )m 12)(CW/m. 15.0(2
)3/6ln()W 80(
+C6.52
2
)/ln(
)(
)/ln(
2 12
12 ππ
π
kL
DDQ
TTTT
DD
kLQ sisi
&& 
 9-29
Chapter 9 Natural Convection 
9-36 A steam pipe extended from one end of a plant to the other with no insulation on it. The rate of heat 
loss from the steam pipe and the annual cost of those heat losses are to be determined. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 
Properties The properties of air at 1 atm and the film temperature of 
(Ts+T∞)/2 = (170+20)/2 = 95°C are (Table A-15) 
Steam 
L = 60 m 
 
 D =6.03 cm 
Ts = 170°C 
ε = 0.7 
Air 
T∞ = 20°C 
 
1-
25
K 002717.0
K)27395(
11
7121.0Pr
/sm 10252.2
CW/m. 0306.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Analysis The characteristic length in this case is the outer diameter of the pipe, m 0.0603== DLc . Then, 
6
225
3-12
2
3
10231.1)7121.0(
)/sm 10252.2(
)m 0603.0)(K 20170)(K 002717.0)(m/s 81.9(
Pr
)( ×=×
−=−= −∞υ
β DTTg
Ra s 
 ( )[ ] ( )[ ] 42.157121.0/559.01 )10231.1(387.06.0Pr/559.01 387.06.0
2
27/816/9
6/16
2
27/816/9
6/1
=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
×+=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
+= RaNu 
 
2
2
m 37.11m) m)(60 0603.0(
C.W/m 823.7)42.15(
m 0603.0
CW/m. 0306.0
===
°=°==
ππDLA
Nu
D
kh
s
 
Then the total rate of heat transfer by natural convection and radiation becomes 
 
kW 27.4==
+−+×+
°−°=
−+−=
−
∞
W
TTATThAQ surrssss
 27,388 
])K 27320()K 273170)[(.KW/m 1067.5)(m 37.11)(7.0( 
C)20170)(m 37.11)(C.W/m 823.7( 
)()(
444282
22
44σε&
The total amount of gas consumption and its cost during a one-year period is 
 therms/yr496,10s/h) 3600h/yr 8760(
kJ 105,500
 therm1
78.0
kJ/s 388.27 =×⎟⎟⎠
⎞⎜⎜⎝
⎛=η
Δ= tQQgas
&
 
 $5647/yr== therm)/538.0)($ therms/yr496,10(Cost 
 
 9-30
Chapter 9 Natural Convection 
9-37 "!PROBLEM 9-37" 
 
"GIVEN" 
L=60 "[m]" 
D=0.0603 "[m]" 
T_s=170 "[C], parameter to be varied" 
T_infinity=20 "[C]" 
epsilon=0.7 
T_surr=T_infinity 
eta_furnace=0.78 
UnitCost=0.538 "[$/therm]" 
time=24*365 "[h]" 
 
"PROPERTIES" 
Fluid$='air' 
k=Conductivity(Fluid$, T=T_film) 
Pr=Prandtl(Fluid$, T=T_film) 
rho=Density(Fluid$, T=T_film, P=101.3) 
mu=Viscosity(Fluid$, T=T_film) 
nu=mu/rho 
beta=1/(T_film+273) 
T_film=1/2*(T_s+T_infinity) 
sigma=5.67E-8 "[W/m^2-K^4], Stefan-Boltzmann constant" 
g=9.807 "[m/s^2], gravitational acceleration" 
 
"ANALYSIS" 
delta=D 
Ra=(g*beta*(T_s-T_infinity)*delta^3)/nu^2*Pr 
Nusselt=(0.6+(0.387*Ra^(1/6))/(1+(0.559/Pr)^(9/16))^(8/27))^2 
h=k/delta*Nusselt 
A=pi*D*L 
Q_dot=h*A*(T_s-T_infinity)+epsilon*A*sigma*((T_s+273)^4-(T_surr+273)^4) 
Q_gas=(Q_dot*time)/eta_furnace*Convert(h, s)*Convert(J, kJ)*Convert(kJ, therm) 
Cost=Q_gas*UnitCost 
 
 9-31
Chapter 9Natural Convection 
 
Ts [C] Q [W] Cost [$] 
100 11636 2399 
105 12594 2597 
110 13577 2799 
115 14585 3007 
120 15618 3220 
125 16676 3438 
130 17760 3661 
135 18869 3890 
140 20004 4124 
145 21166 4364 
150 22355 4609 
155 23570 4859 
160 24814 5116 
165 26085 5378 
170 27385 5646 
175 28713 5920 
180 30071 6200 
185 31459 6486 
190 32877 6778 
195 34327 7077 
200 35807 7382 
 
 
 
 
100 120 140 160 180 200
10000
15000
20000
25000
30000
35000
40000
2000
3000
4000
5000
6000
7000
8000
Ts [C]
Q
 [
W
]
C
os
t 
[$
]
Q
Cost
 
 
 9-32
Chapter 9 Natural Convection 
9-38 A steam pipe extended from one end of a plant to the other. It is proposed to insulate the steam pipe 
for $750. The simple payback period of the insulation to pay for itself from the energy it saves are to be 
determined. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 
Properties The properties of air at 1 atm and the anticipated film 
temperature of (Ts+T∞)/2 = (35+20)/2 = 27.5°C are (Table A-15) 
Steam 
L = 60 m 
 
 D =16.03 cm
170°C, ε = 0.1 
Air 
T∞ = 20°C 
Insulation 
ε = 0.1 
 
1-
25
K 003328.0
K)2735.27(
11
7289.0Pr
/sm 10584.1
CW/m. 0257.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Analysis Insulation will drop the outer surface temperature to a value close to the ambient temperature. The 
solution of this problem requires a trial-and-error approach since the determination of the Rayleigh number 
and thus the Nusselt number depends on the surface temperature which is unknown. We start the solution 
process by “guessing” the outer surface temperature to be 35°C for the evaluation of the properties and h. 
We will check the accuracy of this guess later and repeat the calculations if necessary. The characteristic 
length in this case is the outer diameter of the insulated pipe, m. 1603.0== DLc Then, 
6
225
3-12
2
3
10856.5)7289.0(
)/sm 10584.1(
)m 1603.0)(K 2035)(K 003328.0)(m/s 81.9(Pr
)( ×=×
−=−= −∞υ
β DTTg
Ra s 
 ( )[ ] ( )[ ] 23.247289.0/559.01 )10856.5(387.06.0Pr/559.01 387.06.0
2
27/816/9
6/16
2
27/816/9
6/1
=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
×+=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
+= RaNu 
 
2
2
m 22.30m) m)(60 1603.0(
C.W/m 884.3)23.24(
m 1603.0
CW/m. 0257.0
===
°=°==
ππDLA
Nu
D
kh
s
 
Then the total rate of heat loss from the outer surface of the insulated pipe by convection and radiation 
becomes 
 
W2039
])K 27320()K 27335)[(.KW/m 1067.5)(m 22.30)(1.0(+
C)2035)(m 22.30)(C.W/m 884.3(
)()(
444282
22
44
 =
+−+×
°−°=
−+−=+=
−
∞ surrssssradconv TTATThAQQQ σε&&&
In steady operation, the heat lost from the exposed surface of the insulation by convection and radiation must be equal 
to the heat conducted through the insulation. This requirement gives the surface temperature to be 
)m 60)(CW/m. 038.0(2
)03.6/03.16ln(
C)170(
W 2039 
2
)/ln( 12
..
insulation
°
°−=→−=−==
ππ
ssis
ins
sis T
kL
DD
TT
R
TT
QQ && 
It gives 30.8°C for the surface temperature, which is somewhat different than the assumed value of 35°C. 
Repeating the calculations with other surface temperatures gives 
 W 1988and C3.34 =°= QTs &
Heat loss and its cost without insulation was determined in the Prob. 9-36 to be 27.388 kW and $5647. 
Then the reduction in the heat losses becomes 
 or 25.388/27.40 = 0.927 (92.7%) kW 40.25988.1388.27saved ≅−=Q&
Therefore, the money saved by insulation will be 0.921×($5647/yr) = $5237/yr which will pay for the cost 
of $750 in $750/($5237/yr)=0.1432 year = 52.3 days. 
 9-33
Chapter 9 Natural Convection 
9-39 A circuit board containing square chips is mounted on a vertical wall in a room. The surface 
temperature of the chips is to be determined. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with 
constant properties. 3 The local atmospheric pressure is 1 atm. 4 The heat 
transfer from the back side of the circuit board is negligible. 
Air 
T∞ = 25°C 
Tsurr = 25°C 
PCB, Ts 
ε = 0.7 
121×0.05 W
 L = 30 cm
Properties The properties of air at 1 atm and the anticipated film 
temperature of (Ts+T∞)/2 = (35+25)/2 = 30°C are (Table A-15) 
 
1-
25
K 0033.0
K)27330(
11
7282.0Pr
/sm 10608.1
CW/m. 02588.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Analysis The solution of this problem requires a trial-and-error approach since the determination of the 
Rayleigh number and thus the Nusselt number depends on the surface temperature which is unknown. We 
start the solution process by “guessing” the surface temperature to be 35°C for the evaluation of the 
properties and h. We will check the accuracy of this guess later and repeat the calculations if necessary. 
The characteristic length in this case is the height of the board, m. 3.0== LLc Then, 
 7225
3-12
2
3
10463.2)7282.0(
)/sm 10608.1(
)m 3.0)(K 2535)(K 0033.0)(m/s 81.9(Pr
)( ×=×
−=−= −∞υ
β LTTg
Ra s 
 57.40
7282.0
492.01
)10463.2(387.0825.0
Pr
492.01
Ra387.0825.0
2
27/816/9
6/17
2
27/816/9
6/1
=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
×+=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
+=Nu 
 
22
2
m 09.0m) 3.0(
C.W/m 50.3)57.40(
m 3.0
CW/m. 02588.0
==
°=°==
sA
Nu
L
kh
 
Considering both natural convection and radiation, the total rate of heat loss can be expressed as 
 
])K 27325()K 273)[(.KW/m 1067.5)(m 09.0)(7.0( 
C)25)(m 09.0)(C.W/m 50.3(W )05.0121(
)()(
444282
22
44
+−+×+
°−°=×
−+−=
−
∞
s
s
surrssss
T
T
TTATThAQ σε&
Its solution is 
 Ts = 33.5°C 
which is sufficiently close to the assumed value in the evaluation of properties and h. Therefore, there is no 
need to repeat calculations by reevaluating the properties and h at the new film temperature. 
 9-34
Chapter 9 Natural Convection 
9-40 A circuit board containing square chips is positioned horizontally in a room. The surface temperature 
of the chips is to be determined for two orientations. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 4 The heat transfer from the back side of the circuit board is negligible. 
Properties The properties of air at 1 atm and the anticipated film 
temperature of (Ts+T∞)/2 = (35+25)/2 = 30°C are (Table A-15) Air 
T∞ = 25°C 
Tsurr = 25°C PCB, Ts 
ε = 0.7 
121×0.05 W 
L = 30 cm
 
1-
25
K 0033.0
K)27330(
11
7282.0Pr
/sm 10608.1
CW/m. 02588.0
=+==
=
×=
°=
−
fT
k
β
υ
 
 
Analysis The solution of this problem requires a trial-and-error approach since the determination of the 
Rayleigh number and thus the Nusselt number depends on the surface temperature which is unknown. We 
start the solution process by “guessing” the surface temperature to be 35°C for the evaluation of the 
properties and h. The characteristic length for both cases is determined from 
 m. 075.0
m)] 3.0(+m) 3.02[(
m) 3.0( 2 ===
p
A
L sc 
Then, 
5
225
3-12
2
3
10848.3)7282.0(
)/sm 10608.1(
)m 075.0)(K 2535)(K 00333.0)(m/s 81.9(Pr
)( ×=×
−=−= −∞υ
β cs LTTgRa 
(a) Chips (hot surface) facing up: 
 45.13)10848.3(54.054.0 4/154/1 =×== RaNu
 
22
2
m 09.0m) 3.0(
C.W/m 641.4)45.13(
m 075.0
CW/m. 02588.0
==
°=°==
s
c
A
Nu
L
kh
 
Considering both natural convection and radiation, the total rate of heat loss can be expressed as 
 
])K 27325()K273)[(.KW/m 1067.5)(m 09.0)(7.0( 
C)25)(m 09.0)(C.W/m 641.4(W )05.0121(
)()(
444282
22
44
+−+×+
°−°=×
−+−=
−
∞
s
s
surrssss
T
T
TTATThAQ σε&
Its solution is Ts = 32.5°C 
which is sufficiently close to the assumed value. Therefore, there is no need to repeat calculations. 
(b) Chips (hot surface) facing up: 
 725.6)10848.3(27.027.0 4/154/1 =×== RaNu
 C.W/m 321.2)725.6(
m 075.0
CW/m. 02588.0 2 °=°== Nu
L
kh
c
 
Considering both natural convection and radiation, the total rate of heat loss can be expressed as 
 
])K 27325()K 273)[(.KW/m 1067.5)(m 09.0)(7.0( 
C)25)(m 09.0)(C.W/m 321.2(W )05.0121(
)()(
444282
22
44
+−+×+
°−°=×
−+−=
−
∞
s
s
surrssss
T
T
TTATThAQ σε&
Its solution is Ts = 35.0°C 
which is identical to the assumed value in the evaluation of properties and h. Therefore, there is no need to 
repeat calculations. 
 9-35
Chapter 9 Natural Convection 
9-41 It is proposed that the side surfaces of a cubic industrial furnace be insulated for $550 in order to 
reduce the heat loss by 90 percent. The thickness of the insulation and the payback period of the insulation 
to pay for itself from the energy it saves are to be determined. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with 
constant properties. 3 The local atmospheric pressure is 1 atm. 
Properties The properties of air at 1 atm and the film temperature of 
(Ts+T∞)/2 = (110+30)/2 = 70°C are (Table A-15) 
Hot gases 
 
T∞ = 30°C
 
Furnace 
Ts = 110°C 
ε = 0.7 
2 m
2 m
 
1-
25
K 002915.0
K)27370(
11
7177.0Pr
/sm 10995.1
CW/m. 02881.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Analysis The characteristic length in this case is the height of the furnace, m. 2== LLc Then, 
10
225
3-12
2
3
10301.3)7177.0(
)/sm 10995.1(
)m 2)(K 30110)(K 002915.0)(m/s 81.9(Pr
)( ×=×
−=−= −∞υ
β LTTg
Ra s 
 2.369
7177.0
492.01
)10301.3(387.0825.0
Pr
492.01
Ra387.0825.0
2
27/816/9
6/110
2
27/816/9
6/1
=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
×+=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
+=Nu 
 
22
2
m 16)m 2(4
C.W/m318.5)2.369(
m 2
CW/m. 02881.0
==
°=°==
s
c
A
Nu
L
kh 
 
Then the heat loss by combined natural convection and radiation becomes 
 
W 119,15
])K 27330()K 273110)[(.KW/m 1067.5)(m 16)(7.0( 
C)30110)(m 16)(C.W/m 318.5(
)()(
444282
22
44
=
+−+×+
°−°=
−+−=
−
∞ surrssss TTATThAQ σε&
Noting that insulation will reduce the heat losses by 90%, the rate of heat loss after insulation will be 
 
 W1512 W119,151.0)9.01(
 W607,13 W119,159.09.0
insulation noloss
insulation nosaved
=×=−=
=×==
QQ
QQ
&&
&&
The furnace operates continuously and thus 8760 h. Then the amount of energy and money the insulation 
will save becomes 
 therms/yr5215s/yr) 3600(8760
kJ 105,500
 therm1
78.0
kJ/s 607.13savedEnergy =×⎟⎟⎠
⎞⎜⎜⎝
⎛=Δ= tQsaved& 
 $2868)therm/55.0)($ therms5215(=energy) ofcost t saved)(UniEnergy (savedMoney ==
Therefore, the money saved by insulation will pay for the cost of $550 in 
550/($2868/yr)=0.1918 yr = 70 days. 
 9-36
Chapter 9 Natural Convection 
 Insulation will lower the outer surface temperature, the Rayleigh and Nusselt numbers, and thus 
the convection heat transfer coefficient. For the evaluation of the heat transfer coefficient, we assume the 
surface temperature in this case to be 50°C. The properties of air at the film temperature of (Ts+T∞)/2 = 
(50+30)/2 = 40°C are (Table A-15) 
 
1-
25
K 003195.0
K)27340(
11
7255.0Pr
/sm 10702.1
CW/m. 02662.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Then, 
10
225
3-12
2
3
10256.1)7255.0(
)/sm 10702.1(
)m 2)(K 3050)(K 003195.0)(m/s 81.9(Pr
)( ×=×
−=−= −∞υ
β LTTg
Ra s 
 0.272
7255.0
492.01
)10256.1(387.0
825.0
Pr
492.01
Ra387.0825.0
2
27/816/9
6/110
2
27/816/9
6/1
=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
×+=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
+=Nu 
 C.W/m 620.3)0.272(
m 2
CW/m. 02662.0 2 °=°== Nu
L
kh 
 m )2m)(2 2(4 insuls tA +×=
The total rate of heat loss from the outer surface of the insulated furnace by convection and radiation 
becomes 
])K 27330()K 273)[(.KW/m 1067.5()7.0(+C)30(C).W/m 620.3(W 1512
)()(
444282
44
+−+×°−°=
−+−=+=
−
∞
ss
surrssssradconv
TATA
TTATThAQQQ σε&&&
I
n steady operation, the heat lost by the side surfaces of the pipe must be equal to the heat lost from the 
exposed surface of the insulation by convection and radiation, which must be equal to the heat conducted 
through the insulation. Therefore, 
 
insul
s
s
ins
s
sinsulation t
T
A
t
TT
kAQQ
C)(110
C)W/m. 038.0(W 1512 
)( furnace °−°=→−== && 
Solving the two equations above by trial-and error (or better yet, an equation solver) gives 
Ts = 48.4°C and tinsul = 0.0254 m = 2.54 cm 
 
 9-37
Chapter 9 Natural Convection 
9-42 A cylindrical propane tank is exposed to calm ambient air. The propane is slowly vaporized due to a 
crack developed at the top of the tank. The time it will take for the tank to empty is to be determined. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 4 Radiation heat transfer is negligible. 
D = 1.5 m 
L = 4 m 
Propane tank 
ε ≈ 0 
Ts = -42°C 
Air 
T∞ = 25°C Properties The properties of air at 1 atm and the film temperature of 
(Ts+T∞)/2 = (-42+25)/2 = -8.5°C are (Table A-15) 
 
1-
25
K 003781.0
K)2735.8(
11
7383.0Pr
/sm 10265.1
CW/m. 02299.0
=+−==
=
×=
°=
−
fT
k
β
υ
 
Analysis The tank gains heat through its cylindrical surface as well as its circular end surfaces. For 
convenience, we take the heat transfer coefficient at the end surfaces of the tank to be the same as that of its 
side surface. (The alternative is to treat the end surfaces as a vertical plate, but this will double the amount 
of calculations without providing much improvement in accuracy since the area of the end surfaces is much 
smaller and it is circular in shape rather than being rectangular). The characteristic length in this case is the 
outer diameter of the tank, Then, m. 5.1== DLc
10
225
3-12
2
3
10869.3)7383.0(
)/sm 10265.1(
)m 5.1](K )42(25)[(K 003781.0)(m/s 81.9(Pr
)( ×=×
−−=−= −∞υ
β DTTg
Ra s 
 ( )[ ] ( )[ ] 1.3747383.0/559.01 )10869.3(387.06.0Pr/559.01 387.06.0
2
27/816/9
6/110
2
27/816/9
6/1
=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
×+=
⎪⎭
⎪⎬
⎫
⎪⎩
⎪⎨
⎧
+
+= RaNu 
 
222
2
m 38.224/m) 5.1(2)m 4)(m 5.1(4/2
C.W/m 733.5)1.374(
m 5.1
CW/m. 02299.0
=+=+=
°=°==
ππππ DDLA
Nu
D
kh
s
 
and 
 W8598C)]42(25)[(m 38.22)(C.W/m 733.5()( 22 =°−−°=−= ∞ ss TThAQ&
The total mass and the rate of evaporation of propane are 
 
kg/s 02023.0
kJ/kg 425
kJ/s 598.8
kg 4107)m 4(
4
)m 5.1()kg/m 581(
4
2
3
2
===
=π=πρ=ρ=
fgh
Qm
LDVm
&
&
 
and it will take 
 hours 56.4====Δ s 996,202
 kg/s02023.0
 kg4107
m
mt & 
for the propane tank to empty. 
 9-38
Chapter 9 Natural Convection 
9-43E The average surface temperature of a human head is to be determined when it is not covered. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 4 The head canbe approximated as a 12-in.-diameter sphere. 
Properties The solution of this problem requires a trial-and-error approach since the determination of the 
Rayleigh number and thus the Nusselt number depends on the surface temperature which is unknown. We 
start the solution process by “guessing” the surface temperature to be 120°F for the evaluation of the 
properties and h. We will check the accuracy of this guess later and repeat the calculations if necessary. 
The properties of air at 1 atm and the anticipated film temperature of (Ts+T∞)/2 = (120+77)/2 = 98.5°F are 
(Table A-15E) 
 
1-
23
R 001791.0
R)4605.98(
11
7262.0Pr
/sft 10180.0
FBtu/h.ft. 01525.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Analysis The characteristic length for a spherical object is Lc = D = 12/24 = 0.5 ft. Then, 
Air 
T∞ = 77°F 
Head 
Q = ¼ 287 Btu/h 
D = 12 in 
 
ε = 0.9 
 6223
3-12
2
3
10943.6)7262.0(
)/sft 10180.0(
)ft 5.0)(R 7795)(R 001791.0)(ft/s 2.32(
Pr
)( ×=×
−=−= −∞υ
β DTTg
Ra s 
 39.25
7262.0
469.01
)10943.6(589.02
Pr
469.01
589.02
9/416/9
4/16
9/416/9
4/1
=
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
×+=
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
+= RaNu 
 
222
2
ft 7854.0)ft 5.0(
F.Btu/h.ft 7744.0)39.25(
ft 1
FBtu/h.ft. 01525.0
===
°=°==
ππDA
Nu
D
kh
s
 
Considering both natural convection and radiation, the total rate of heat loss can be written as 
])R 46077()R 460)[(.RBtu/h.ft 101714.0)(m 7854.0)(9.0( 
F)77)(ft 7854.0(F).Btu/h.ft 7744.0(Btu/h) 4/287(
)()(
444282
22
44
+−+×+
°−°=
−+−=
−
∞
s
s
surrssss
T
T
TTATThAQ σε&
 
Its solution is 
Ts = 125.9°F 
which is sufficiently close to the assumed value in the evaluation of the properties and h. Therefore, there is 
no need to repeat calculations. 
 9-39
Chapter 9 Natural Convection 
9-44 The equilibrium temperature of a light glass bulb in a room is to be determined. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 4 The light bulb is approximated as an 8-cm-diameter sphere. 
Properties The solution of this problem requires a trial-and-error approach since the determination of the 
Rayleigh number and thus the Nusselt number depends on the surface temperature which is unknown. We 
start the solution process by “guessing” the surface temperature to be 170°C for the evaluation of the 
properties and h. We will check the accuracy of this guess later and repeat the calculations if necessary. 
The properties of air at 1 atm and the anticipated film temperature of (Ts+T∞)/2 = (170+25)/2 = 97.5°C are 
(Table A-15) 
 
1-
25
K 002699.0
K)2735.97(
11
7116.0Pr
/sm 10279.2
C W/m.03077.0
=+==β
=
×=υ
°=
−
fT
k
 
Analysis The characteristic length in this case is Lc = D = 0.08 m. Then, 
6
225
3-12
2
3
10694.2
)7116.0(
)/sm 10279.2(
)m 08.0)(K 25170)(K 002699.0)(m/s 81.9(Pr
)(
×=
×
−=−= −∞υ
β DTTg
Ra s
 
Air 
T∞ = 25°C 
Lamp 
60 W 
ε = 0.9 
D = 8 cm 
Light, 
6 W 
 ( )[ ] ( )[ ] 42.207116.0/469.01 )10694.2(589.02Pr/469.01 589.02 9/416/9
4/16
9/416/9
4/1
=
+
×+=
+
+= RaNu 
Then 
 
222
2
m 02011.0m) 08.0(
C.W/m 854.7)42.20(
m 08.0
CW/m. 03077.0
===
°=°==
ππDA
Nu
D
kh
s
 
Considering both natural convection and radiation, the total rate of heat loss can be written as 
 
])K 27325()273)[(.KW/m 1067.5)(m 02011.0)(9.0( 
C)25)(m 02011.0)(C.W/m 854.7(W )6090.0(
)()(
444282
22
44
+−+×+
°−°=×
−+−=
−
∞
s
s
surrssss
T
T
TTATThAQ σε&
Its solution is 
Ts = 169.4°C 
which is sufficiently close to the value assumed in the evaluation of properties and h. Therefore, there is no 
need to repeat calculations. 
 
 
 9-40
Chapter 9 Natural Convection 
9-45 A vertically oriented cylindrical hot water tank is located in a bathroom. The rate of heat loss from the 
tank by natural convection and radiation is to be determined. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 4 The temperature of the outer surface of the tank is constant. 
Properties The properties of air at 1 atm and the film temperature 
of (Ts+T∞)/2 = (44+20)/2 = 32°C are (Table A-15) 
 
1-
25
K 003279.0
K)27332(
11
7276.0Pr
/sm 10627.1
CW/m. 02603.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Analysis The characteristic length in this case is the height of the cylinder, 
Air 
T∞ = 20°C 
Tank 
Ts = 44°C 
ε = 0.4 L = 1.1 m 
D = 0.4 m 
m. 1.1== LLc Then, 
 9225
3-12
2
3
10883.3
)/sm 10627.1(
)m 1.1)(K 2044)(K 003279.0)(m/s 81.9()(
Gr ×=×
−=−= −∞υ
β LTTg s 
A vertical cylinder can be treated as a vertical plate when 
 m 1542.0
)10883.3(
m) 1.1(35
Gr
35m) 4.0( 4/191/4 =×=≥=
LD 
which is satisfied. That is, the Nusselt number relation for a vertical plate can be used for the side surfaces. 
For the top and bottom surfaces we use the relevant Nusselt number relations. First, for the side surfaces, 
 99 10825.2)7276.0)(10883.3(GrPrRa ×=×==
 2.170
7276.0
492.01
)10825.2(387.0825.0
Pr
492.01
Ra387.0825.0
2
27/816/9
6/19
2
27/816/9
6/1
=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
×+=
⎪⎪
⎪
⎭
⎪⎪
⎪
⎬
⎫
⎪⎪
⎪
⎩
⎪⎪
⎪
⎨
⎧
⎥⎥⎦
⎤
⎢⎢⎣
⎡ ⎟⎠
⎞⎜⎝
⎛+
+=Nu 
 
2
2
m 382.1)m 1.1)(m 4.0(
C.W/m 027.4)2.170(
m 1.1
CW/m. 02603.0
===
°=°==
ππDLA
Nu
L
kh
s
 
 W 6.133C)2044)(m 382.1)(C.W/m 027.4()( 22side =°−°=−= ∞TThAQ ss&
For the top surface, 
 m 1.0
4
m 4.0
4
4/2 ===== D
D
D
p
A
L sc π
π 
 6225
3-12
2
3
10123.2)7276.0(
)/sm 10627.1(
)m 1.0)(K 2044)(K 003279.0)(m/s 81.9(Pr
)(
Ra ×=×
−=−= −∞υ
β cs LTTg 
 61.20)10123.2(54.0Ra54.0Nu 4/164/1 =×==
 
222
2
m 1257.04/)m 4.0(4/
C.W/m 365.5)61.20(
m 1.0
CW/m. 02603.0
===
°=°==
ππDA
Nu
L
kh
s
c 
 W 2.16C)2044)(m 1257.0)(C.W/m 365.5()( 22top =°−°=−= ∞TThAQ ss&
For the bottom surface, 
 31.10)10123.2(27.0Ra27.0Nu 4/164/1 =×==
 9-41
Chapter 9 Natural Convection 
 C.W/m 683.2)31.10(
m 1.0
CW/m. 02603.0 2 °=°== Nu
L
kh
c
 
 W 1.8C)2044)(m 1257.0)(C.W/m 683.2()( 22bottom =°−°=−= ∞TThAQ ss&
The total heat loss by natural convection is 
 W157.9=++=++= 1.82.166.133bottomtopsideconv QQQQ &&&&
The radiation heat loss from the tank is 
[ ]
 W101.1=
+−+×++=
−=
− 444282
44
rad
)K 27320()K 27344().KW/m 1067.5)(m 1257.01257.0382.1)(4.0(
)( surrss TTAQ σε&
 
 
 9-42
Chapter 9 Natural Convection 
9-46 A rectangular container filled with cold water is gaining heat from its surroundings by natural 
convection and radiation. The water temperature in the container after a 3 hours and the average rate of heat 
transfer are to be determined. 
Assumptions 1 Steady operating conditions exist. 2 Air is an ideal gas with constant properties. 3 The local 
atmospheric pressure is 1 atm. 4 The heat transfer coefficient at the top and bottom surfaces is the same as 
that on the side surfaces. 
Properties The properties of air at 1 atm and the anticipated film 
temperature of (Ts+T∞)/2 = (10+24)/2 = 17°C are (Table A-15) 
 
1-
25
K 003448.0
K)27317(
11
7317.0Pr
/sm 10489.1
CW/m. 02491.0
=+==
=
×=
°=
−
fT
k
β
υ
 
Air 
T∞ = 24°C 
Container 
Ts 
ε = 0.6 
The properties of water at 2°C are (Table A-7) 
 CJ/kg. 4214and kg/m1000 3 °== pCρ
Analysis We first evaluate the heat transfer coefficient on the side surfaces. The