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ch01


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PROBLEM 1.1 
 
KNOWN: Heat rate, q, through one-dimensional wall of area A, thickness L, thermal 
conductivity k and inner temperature, T1. 
 
FIND: The outer temperature of the wall, T2. 
 
SCHEMATIC: 
 
 
ASSUMPTIONS: (1) One-dimensional conduction in the x-direction, (2) Steady-state conditions, 
(3) Constant properties. 
 
ANALYSIS: The rate equation for conduction through the wall is given by Fourier\u2019s law, 
 
q q q A = -k dT
dx
A = kA T T
Lcond x x
1 2
= = \u2032\u2032 \u22c5 \u22c5
\u2212
. 
 
Solving for T2 gives 
 
 T T
q L
kA2 1
cond
= \u2212 . 
 
Substituting numerical values, find 
 
 T C - 3000W 0.025m
0.2W / m K 10m2 2
=
×
\u22c5 ×
415$ 
 
 T C - 37.5 C2 = 415
$ $
 
 
 T C.2 = 378
$
 < 
 
COMMENTS: Note direction of heat flow and fact that T2 must be less than T1. 
PROBLEM 1.2 
 
KNOWN: Inner surface temperature and thermal conductivity of a concrete wall. 
 
FIND: Heat loss by conduction through the wall as a function of ambient air temperatures ranging from 
-15 to 38°C. 
 
SCHEMATIC: 
 
 
ASSUMPTIONS: (1) One-dimensional conduction in the x-direction, (2) Steady-state conditions, (3) 
Constant properties, (4) Outside wall temperature is that of the ambient air. 
 
ANALYSIS: From Fourier\u2019s law, it is evident that the gradient, xdT dx q k\u2032\u2032= \u2212 , is a constant, and 
hence the temperature distribution is linear, if xq\u2032\u2032 and k are each constant. The heat flux must be 
constant under one-dimensional, steady-state conditions; and k is approximately constant if it depends 
only weakly on temperature. The heat flux and heat rate when the outside wall temperature is T2 = -15°C 
are 
 
( ) 21 2
x
25 C 15 CdT T Tq k k 1W m K 133.3W m
dx L 0.30m
\u2212 \u2212
\u2212
\u2032\u2032 = \u2212 = = \u22c5 =
$ $
. (1) 
 
2 2
x xq q A 133.3W m 20m 2667 W\u2032\u2032= × = × = . (2) < 
 
Combining Eqs. (1) and (2), the heat rate qx can be determined for the range of ambient temperature, -15 
\u2264 T2 \u2264 38°C, with different wall thermal conductivities, k. 
-20 -10 0 10 20 30 40
Ambient air temperature, T2 (C)
-1500
-500
500
1500
2500
3500
H
ea
t l
os
s,
 q
x 
(W
)
Wall thermal conductivity, k = 1.25 W/m.K
k = 1 W/m.K, concrete wall
k = 0.75 W/m.K
 
 
For the concrete wall, k = 1 W/m\u22c5K, the heat loss varies linearily from +2667 W to -867 W and is zero 
when the inside and ambient temperatures are the same. The magnitude of the heat rate increases with 
increasing thermal conductivity. 
 
COMMENTS: Without steady-state conditions and constant k, the temperature distribution in a plane 
wall would not be linear. 
PROBLEM 1.3 
 
KNOWN: Dimensions, thermal conductivity and surface temperatures of a concrete slab. Efficiency 
of gas furnace and cost of natural gas. 
 
FIND: Daily cost of heat loss. 
 
SCHEMATIC: 
 
 
 
ASSUMPTIONS: (1) Steady state, (2) One-dimensional conduction, (3) Constant properties. 
 
ANALYSIS: The rate of heat loss by conduction through the slab is 
 
 ( ) ( )1 2T T 7 Cq k LW 1.4 W / m K 11m 8m 4312 W
t 0.20 m
\u2212 °
= = \u22c5 × = < 
 
The daily cost of natural gas that must be combusted to compensate for the heat loss is 
 
 ( ) ( )gd 6f
q C 4312 W $0.01/ MJC t 24h / d 3600s / h $4.14 / d
0.9 10 J / MJ\u3b7
×
= \u2206 = × =
×
 
<
 
 
COMMENTS: The loss could be reduced by installing a floor covering with a layer of insulation 
between it and the concrete. 
 
PROBLEM 1.4
KNOWN: Heat flux and surface temperatures associated with a wood slab of prescribed
thickness.
FIND: Thermal conductivity, k, of the wood.
SCHEMATIC:
ASSUMPTIONS: (1) One-dimensional conduction in the x-direction, (2) Steady-state
conditions, (3) Constant properties.
ANALYSIS: Subject to the foregoing assumptions, the thermal conductivity may be
determined from Fourier\u2019s law, Eq. 1.2. Rearranging,
( )
L W 0.05mk=q 40 
T T m 40-20 C
x 21 2
\u2032\u2032 =
\u2212
\ufffd
k = 0.10 W / m K.\u22c5 <
COMMENTS: Note that the °C or K temperature units may be used interchangeably when
evaluating a temperature difference.
PROBLEM 1.5
KNOWN: Inner and outer surface temperatures of a glass window of prescribed dimensions.
FIND: Heat loss through window.
SCHEMATIC:
ASSUMPTIONS: (1) One-dimensional conduction in the x-direction, (2) Steady-state
conditions, (3) Constant properties.
ANALYSIS: Subject to the foregoing conditions the heat flux may be computed from
Fourier\u2019s law, Eq. 1.2.
( )
T Tq k 
L
15-5 CWq 1.4 
m K 0.005m
q 2800 W/m .
1 2
x
x
2
x
\u2212
\u2032\u2032 =
\u2032\u2032 =
\u22c5
\u2032\u2032 =
\ufffd
Since the heat flux is uniform over the surface, the heat loss (rate) is
q = qx A
q = 2800 W / m2 3m2
\u2032\u2032 ×
×
q = 8400 W. <
COMMENTS: A linear temperature distribution exists in the glass for the prescribed
conditions.
PROBLEM 1.6 
 
KNOWN: Width, height, thickness and thermal conductivity of a single pane window and 
the air space of a double pane window. Representative winter surface temperatures of single 
pane and air space. 
 
FIND: Heat loss through single and double pane windows. 
 
SCHEMATIC: 
 
 
 
 
ASSUMPTIONS: (1) One-dimensional conduction through glass or air, (2) Steady-state 
conditions, (3) Enclosed air of double pane window is stagnant (negligible buoyancy induced 
motion). 
 
ANALYSIS: From Fourier\u2019s law, the heat losses are 
 
Single Pane: ( )T T 35 C21 2q k A 1.4 W/m K 2m 19,600 Wg g L 0.005m\u2212= = \u22c5 =$ 
 
Double Pane: ( )T T 25 C21 2q k A 0.024 2m 120 Wa a L 0.010 m\u2212= = =$ 
 
COMMENTS: Losses associated with a single pane are unacceptable and would remain 
excessive, even if the thickness of the glass were doubled to match that of the air space. The 
principal advantage of the double pane construction resides with the low thermal conductivity 
of air (~ 60 times smaller than that of glass). For a fixed ambient outside air temperature, use 
of the double pane construction would also increase the surface temperature of the glass 
exposed to the room (inside) air. 
 
PROBLEM 1.7
KNOWN: Dimensions of freezer compartment. Inner and outer surface temperatures.
FIND: Thickness of styrofoam insulation needed to maintain heat load below prescribed
value.
SCHEMATIC:
ASSUMPTIONS: (1) Perfectly insulated bottom, (2) One-dimensional conduction through 5
walls of area A = 4m2, (3) Steady-state conditions, (4) Constant properties.
ANALYSIS: Using Fourier\u2019s law, Eq. 1.2, the heat rate is
q = q A = k T
L
 Atotal\u2032\u2032 \u22c5
\u2206
Solving for L and recognizing that Atotal = 5×W
2
, find
L = 5 k T W
q
2\u2206
( ) ( )5 0.03 W/m K 35 - -10 C 4m
L = 
500 W
2\uf8ee \uf8f9× \u22c5 \uf8f0 \uf8fb\ufffd
L = 0.054m = 54mm. <
COMMENTS: The corners will cause local departures from one-dimensional conduction
and a slightly larger heat loss.
PROBLEM 1.8 
 
KNOWN: Dimensions and thermal conductivity of food/beverage container. Inner and outer 
surface temperatures. 
 
FIND: Heat flux through container wall and total heat load. 
 
SCHEMATIC: 
 
 
 
ASSUMPTIONS: (1) Steady-state conditions, (2) Negligible heat transfer through bottom 
wall, (3) Uniform surface temperatures and one-dimensional conduction through remaining 
walls. 
 
ANALYSIS: From Fourier\u2019s law, Eq. 1.2, the heat flux is 
 
 
( )0.023 W/m K 20 2 CT T 22 1q k 16.6 W/m
L 0.025 m
\u22c5 \u2212
\u2212
\u2032\u2032 = = =
$
 < 
 
Since the flux is uniform over each of the five walls through which heat is transferred, the 
heat load is 
 
 ( )q q A q H 2W 2W W Wtotal 1 2 1 2\u2032\u2032 \u2032\u2032 \uf8ee \uf8f9= × = + + ×\uf8f0 \uf8fb 
 
 ( ) ( )2q 16.6 W/m 0.6m 1.6m 1.2m 0.8m 0.6m 35.9 W\uf8ee \uf8f9= + + × =\uf8f0 \uf8fb < 
 
COMMENTS: The corners and edges of the container create local departures from one-
dimensional conduction, which increase