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491
Heat Engines, Entropy, andthe Second Law of
ThermodynamicsCHAPTER OUTLINE 18.1 Heat Engines and the
Second Law of Thermodynamics
18.2 Reversible and Irreversible Processes
18.3 The Carnot Engine 18.4 Heat Pumps and
Refrigerators 18.5 An Alternative Statement
of the Second Law 18.6 Entropy 18.7 Entropy and the Second
Law of Thermodynamics 18.8 Entropy Changes in
Irreversible Processes 18.9 Context ConnectionThe
Atmosphere as a Heat Engine
ANSWERS TO QUESTIONS Q18.1 First, the efficiency of the automobile engine cannot exceed the
Carnot efficiency: it is limited by the temperature of burning fuel and the temperature of the environment into which the exhaust is dumped. Second, the engine block cannot be allowed to go over a certain temperature. Third, any practical engine has friction, incomplete burning of fuel, and limits set by timing and energy transfer by heat.
Q18.2 No. Any heat engine takes in energy by heat and must also put out
energy by heat. The energy that is dumped as exhaust into the low- temperature sink will always be thermal pollution in the outside environment. So-called “steady growth” in human energy use cannot continue.
Q18.3 A higher steam temperature means that more energy can be extracted from the steam. For a
constant temperature heat sink at Tc , and steam at Th , the efficiency of the power plant is
determined by T T
TTT
h c
h
c
h
−= −1 and is maximized for a high Th .
Q18.4 No. The first law of thermodynamics is a statement about energy conservation, while the second is a
statement about stable thermal equilibrium. They are by no means mutually exclusive. For the particular case of a cycling heat engine, the first law implies Q W Qh eng c= + , and the second law
implies Qc > 0. Q18.5 Take an automobile as an example. According to the first law or the idea of energy conservation, it
must take in all the energy it puts out. Its energy source is chemical energy in gasoline. During the combustion process, some of that energy goes into moving the pistons and eventually into the mechanical motion of the car. Clearly much of the energy goes into heat, which, through the cooling system, is transferred into the atmosphere. Moreover, there are numerous places where friction, both mechanical and fluid, turns mechanical energy into heat. In even the most efficient internal combustion engine cars, less than 30% of the energy from the fuel actually goes into moving the car. The rest ends up as useless heat put into the atmosphere.
492 Heat Engines, Entropy, and the Second Law of Thermodynamics
Q18.6 Suppose the ambient temperature is 20°C. A gas can be heated to the temperature of the bottom of the pond, and allowed to cool as it blows through a turbine. The Carnot efficiency of such an engine
is about eT
Tch
= = =∆ 80373
22%.
Q18.7 No, because the work done to run the heat pump represents energy transferred into the house by
heat. Q18.8 A slice of hot pizza cools off. Road friction brings a skidding car to a stop. A cup falls to the floor and
shatters. Your cat dies. Any process is irreversible if it looks funny or frightening when shown in a videotape running backwards. The free flight of a projectile is nearly reversible.
Q18.9 (a) When the two sides of the semiconductor are at different temperatures, an electric potential
(voltage) is generated across the material, which can drive electric current through an external circuit. The two cups at 50°C contain the same amount of internal energy as the pair of hot and cold cups. But no energy flows by heat through the converter bridging between them and no voltage is generated across the semiconductors.
(b) A heat engine must put out exhaust energy by heat. The cold cup provides a sink to absorb
output or wasted energy by heat, which has nowhere to go between two cups of equally warm water.
Q18.10 The rest of the Universe must have an entropy change of +8.0 J/K, or more.
Q18.11 (a) For an expanding ideal gas at constant temperature, ∆ ∆S
QT
nRVV
= =FHGIKJln 2
1.
(b) For a reversible adiabatic expansion ∆Q = 0 , and ∆S = 0 . An ideal gas undergoing an
irreversible adiabatic expansion can have any positive value for ∆S up to the value given in part (a).
Q18.12 To increase its entropy, raise its temperature. To decrease its entropy, lower its temperature.
“Remove energy from it by heat” is not such a good answer, for if you hammer on it or rub it with a blunt file and at the same time remove energy from it by heat into a constant temperature bath, its entropy can stay constant.
Q18.13 An analogy used by Carnot is instructive: A waterfall continuously converts mechanical energy into
internal energy. It continuously creates entropy as the organized motion of the falling water turns into disorganized molecular motion. We humans put turbines into the waterfall, diverting some of the energy stream to our use. Water flows spontaneously from high to low elevation and energy spontaneously flows by heat from high to low temperature. Into the great flow of solar radiation from Sun to Earth, living things put themselves. They live on energy flow, more than just on energy. A basking snake diverts energy from a high-temperature source (the Sun) through itself temporarily, before the energy inevitably is radiated from the body of the snake to a low-temperature sink (outer space). A tree builds organized cellulose molecules and we build libraries and babies who look like their grandmothers, all out of a thin diverted stream in the universal flow of energy crashing down to disorder. We do not violate the second law, for we build local reductions in the entropy of one thing within the inexorable increase in the total entropy of the Universe. Your roommate’s exercise puts energy into the room by heat.
Chapter 18 493
Q18.14 Either statement can be considered an instructive analogy. We choose to take the first view. All processes require energy, either as energy content or as energy input. The kinetic energy that it possessed at its formation continues to make the Earth go around. Energy released by nuclear reactions in the core of the Sun drives weather on the Earth and essentially all processes in the biosphere. The energy intensity of sunlight controls how lush a forest or jungle can be and how warm a planet is. Continuous energy input is not required for the motion of the planet. Continuous energy input is required for life because energy tends to be continuously degraded, as heat flows into lower-temperature sinks. The continuously increasing entropy of the Universe is the index to energy-transfers completed.
Q18.15 Shaking opens up spaces between jellybeans. The smaller ones more often can fall down into spaces
below them. The accumulation of larger candies on top and smaller ones on the bottom implies a small increase in order, a small decrease in one contribution to the total entropy, but the second law is not violated. The total entropy increases as the system warms up, its increase in internal energy coming from the work put into shaking the box and also from a bit of gravitational energy loss as the beans settle compactly together.
SOLUTIONS TO PROBLEMS
Section 18.1 Heat Engines and the Second Law of Thermodynamics
P18.1 (a) eW
Qh= = =eng J
360 J25 0
0 069 4.
. or 6 94%.
(b) Q Q Wc h= − = − =eng J J J360 25 0 335.
*P18.2 (a) The input energy each hour is
7 89 10 2 50060
1 18 103 9. .× = × J revolution rev minmin
1 h J he jb g
implying fuel input 1 18 101
29 49. .××
FHG
IKJ = J h
L4.03 10 J
L h7e j
(b) Q W Qh c= +eng . For a continuous-transfer process we may divide by time to have
Qt
W
tQ
tW
tQ
tQ
t
h c
h c
∆ ∆ ∆
∆ ∆ ∆
= +
= = −
= × − ×FHG
IKJ = ×
= × FHG
IKJ =
eng
eng
eng
Useful power output
Jrevolution
Jrevolution 1 min
min60 s
W
W1 hp
746 W hp
7 89 10 4 58 10 2 500 rev 11 38 10
1 38 10 185
3 35
5
. ..
.P
(c) PP
engeng J s
rev 60 s rev
2 rad N m= ⇒ = =
× FHG
IKJ = ⋅τω τ
ω π1 38 102 500
1527
5.b g
(d) Q
tc
∆= × F
HGIKJ = ×4 58 10 2 500
1 91 103
5..
Jrevolution
rev60 s
W
494 Heat Engines, Entropy, and the Second Law of Thermodynamics
P18.3 (a) We have eW
QQ Q
QQQh
h c
h
c
h= =
−= − =eng 1 0 250.
with Qc = 8 000 J, we have Qh = 10 7. kJ
(b) W Q Qh ceng J= − = 2 667
and from P =W
teng
∆, we have ∆t
W= = =eng J
5 000 J s s
P2 667
0 533. .
*P18.4 The engine’s output work we identify with the kinetic energy of the bullet:
W K mv
eW
Q
QW
eQ W Q
h
h
h c
eng
eng
eng
eng
kg 320 m s J
J J
= = = =
=
= = = ×
= +
12
12
0 002 4 123
1230 011
1 12 10
2 2
4
.
..
b g
The energy exhaust is
Q Q W
Q mc T
TQmc
c h= − = × − = ×
=
= =× °
= °
eng4
4
J J 1.10 10 J
1.10 10 J kg C1.80 kg 448 J
C
1 12 10 123
13 7
4.
.
∆
∆
Section 18.2 Reversible and Irreversible Processes Section 18.3 The Carnot Engine P18.5 Tc = 703 K Th = 2 143 K
(a) eT
Tch
= ∆ = =1 4402 143
67 2%.
(b) Qh = ×1 40 105. J , W Qheng = 0 420.
P = = × =W
teng J
s kW
∆5 88 10
158 8
4..
Chapter 18 495
P18.6 When e ec= , 1 − =TT
W
Qc
h h
eng and W
tQ
t
c
hh
TT
eng
∆
∆
= −1
(a) Qt
h
Wt
TT
c
h
=FH IK
−=
×
−
eng W s∆ ∆
1
1 50 10 3 600
1
5
293773
.e jb g
Qh = × =8 70 10 8708. J MJ
(b) Q QW
ttc h= −
FHGIKJ = × − × = × =eng J MJ
∆∆ 8 70 10 1 50 10 3 600 3 30 10 3308 5 8. . .e jb g
P18.7 Isothermal expansion at Th = 523 K
Isothermal compression at Tc = 323 K
Gas absorbs 1 200 J during expansion.
(a) Q QTTc h
c
h=FHGIKJ =
FHGIKJ =1 200 741 J
323523
J
(b) W Q Qh ceng J J= − = − =1 200 741 459b g
P18.8 We use eTTc
c
h= −1
as 0 300 1573
.K= −
Th
From which, Th = = °819 546 K C
P18.9 The Carnot summer efficiency is eTTc s
c
h, .= − = −
++
=1 1273 20273 350
0 530a fa f
K K
And in winter, ec w, .= − =1283623
0 546
Then the actual winter efficiency is 0 3200 5460 530
0 330...
.FHGIKJ = or 33 0%.
496 Heat Engines, Entropy, and the Second Law of Thermodynamics
P18.10 (a) eTT
c
hmax . .= − = − = × =−1 1
278293
5 12 10 5 12%2
(b) P = = ×W
teng J s
∆75 0 106.
Therefore, Weng J s s h J h= × = ×75 0 10 3 600 2 70 106 11. .e jb g
From eW
Qh= eng we find Q
W
eh = =×
×= × =−
eng J h J h TJ h
2 70 105 12 10
5 27 10 5 2711
212.
.. .
(c) As fossil-fuel prices rise, this way to use solar energy will become a good buy.
*P18.11 (a) eW W
Qe Q e Q
Qh
h h
h=
+=
+eng1 eng2
1
1 1 2 2
1
Now Q Q Q W Q e Qh c h h h2 1 1 1 1 1 1= = − = −eng .
So ee Q e Q e Q
Qe e e eh h h
h=
+ −= + −1 1 2 1 1 1
11 2 1 2
b g.
(b) e e e e eTT
TT
TT
TT
TT
TT
TT
TT
TT
TT
i
h
c
i
i
h
c
i
i
h
c
i
i
h
c
i
c
h
c
h
= + − = − + − − −FHGIKJ −FHGIKJ = − − − + + − = −1 2 1 2 1 1 1 1 2 1 1
The combination of reversible engines is itself a reversible engine so it has the Carnot efficiency.
(c) With W Weng2 eng1= , eW W
Q
W
Qe
h h=
+= =eng1 eng2 eng1
1 11
22
1 2 1
0 12
2
12
− = −FHGIKJ
− = −
= +
= +
TT
TT
TT
TT
T T T
T T T
c
h
i
h
c
h
i
h
i h c
i h cb g
(d) e e
TT
TT
T T T
T T T
i
h
c
i
i c h
i h c
1 2
2
1 2
1 1= = − = −
=
= b g
Chapter 18 497
P18.12 (a) First, consider the adiabatic process D A→ :
P V P VD D A Aγ γ= so P P
VVD A
A
D=FHGIKJ = F
HGIKJ =
γ
1 400 7125 3
kPa10.0 L15.0 L
kPa .
Also nRT
VV
nRTV
VD
DD
A
AA
FHGIKJ =FHGIKJ
γ γ
or T TVVD A
A
D=FHGIKJ = F
HGIKJ =
−γ 1 2 3
720 549 K10.015.0
K .
Now, consider the isothermal process C D→ : T TC D= = 549 K .
P PVV
PVV
VV
P V
V VC DD
CA
A
D
D
C
A A
C D
=FHGIKJ =FHGIKJ
LNMM
OQPPFHGIKJ = −
γ γ
γ 1
PC = =1 400 10 0
24 0 15 0445
5 3
2 3
kPa L
L L kPa
.
. .
a fa f
Next, consider the adiabatic process B C→ : P V P VB B C Cγ γ= .
But, PP V
V VCA A
C D
= −
γ
γ 1 from above. Also considering the isothermal process, P PVVB A
A
B=FHGIKJ .
Hence, PVV
VP V
V VVA
A
BB
A A
C DC
FHGIKJ =FHG
IKJ−
γγ
γγ
1 which reduces to VV V
VBA C
D= = =
10 015 0
16 0.
..
L 24.0 L L
La f
.
Finally, P PVVB A
A
B=FHGIKJ =
FHG
IKJ =1 400 875 kPa
10.0 L16.0 L
kPa .
State P(kPa) V(L) T(K) A
B C D
1 400 875 445 712
10.0 16.0 24.0 15.0
720 720 549 549
(b) For the isothermal process A B→ : ∆ ∆E nC TVint = = 0
so Q W nRTVV
B
A= − =
FHGIKJ = ⋅ F
HGIKJ = +ln . ln
.
..2 34 720
16 010 0
6 58 mol 8.314 J mol K K kJb ga f .
For the adiabatic process B C→ : Q = 0
∆E nC T TV C Bint mol32
J mol K K kJ= − = ⋅LNM
OQP − = −b g b g a f2 34 8 314 549 720 4 98. . .
and W Q E= − + = + − = −∆ int kJ kJ0 4 98 4 98. .a f .
continued on next page
498 Heat Engines, Entropy, and the Second Law of Thermodynamics
For the isothermal process C D→ : ∆ ∆E nC TVint = = 0
and Q W nRTVV
D
C= − =
FHGIKJ = ⋅ F
HGIKJ = −ln . ln
.
..2 34 549
15 024 0
5 02 mol 8.314 J mol K K kJb ga f .
Finally, for the adiabatic process D A→ : Q = 0
∆E nC T TV A Dint mol32
J mol K K kJ= − = ⋅LNM
OQP − = +b g b g a f2 34 8 314 720 549 4 98. . .
and W Q E= − + = + = +∆ int kJ kJ0 4 98 4 98. . .
Process Q(kJ) W(kJ) ∆Eint (kJ) A B→ +6.58 –6.58 0 B C→ 0 –4.98 –4.98 C D→ –5.02 +5.02 0 D A→ 0 +4.98 +4.98 ABCDA +1.56 –1.56 0
The work done by the engine is the negative of the work input. The output work Weng is
given by the work column in the table with all signs reversed.
(c) eW
QWQh
ABCD
A B= =
−= =
→
eng kJ6.58 kJ1 56
0 237.
. or 23 7%.
eTTc
c
h= − = − =1 1
549720
0 237. or 23 7%.
Section 18.4 Heat Pumps and Refrigerators
*P18.13 COP refrigeratorb g = QW
c
(a) If Qc = 120 J and COP .= 5 00 , then W = 24 0. J
(b) Heat expelled = Heat removed + Work done.
Q Q Wh c= + = + =120 24 144 J J J
Chapter 18 499
*P18.14 COP .= =3 00QW
c . Therefore, WQc=3 00.
.
The heat removed each minute is
QtC = ° ° + ×
+ ° ° = ×
0 030 0 4 186 22 0 0 030 0 3 33 105. kg J kg C . C . kg . J kg
0.030 0 kg 2 090 J kg C 20.0 C 1.40 10 J min4
b gb ga f b ge jb gb ga f
or, Qt
c = 233 J s.
Thus, the work done per sec = = =P233
3 0077 8
J s W
.. .
P18.15 (a) 10 01055 1
3 60011
2 93. . Btu
h W J
1 Btu h
s W J s⋅
FHG
IKJFHG
IKJFHG
IKJFHGIKJ =
(b) Coefficient of performance for a refrigerator: COP refrigeratora f
(c) With EER 5, 510 000
Btu
h WBtu h
⋅=
P: P = = =
⋅
10 0002 000 2 005
Btu h W kW Btu
h W
.
Energy purchased is P ∆t = = ×2 00 1 500 3 00 103. kW h . kWha fb g
Cost kWh kWh= × =3 00 10 0 1003. . $ $300e jb g
With EER 10, 10 10 000Btu
h WBtu h
⋅=
P: P = = =
⋅
10 0001 000 1 0010 Btu
Btu h W kW
h W
.
Energy purchased is P ∆t = = ×1 00 1 50 103. . kW 1 500 h kWha fb g
Cost . kWh kWh= × =1 50 10 0 1003e jb g. $ $150
Thus, the cost for air conditioning is half as much with EER 10
P18.16 COP refriga f = = =TTc
∆27030 0
9 00.
.
P18.17 (a) For a complete cycle, ∆Eint = 0 and W Q Q QQ
Qh c ch
c= − = −
LNMM
OQPP
b g1 .
We have already shown that for a Carnot cycle (and only for a Carnot cycle) QQ
TT
h
c
h
c= .
Therefore, W QT T
Tch c
c=
−LNM
OQP
.
continued on next page
500 Heat Engines, Entropy, and the Second Law of Thermodynamics
(b) We have the definition of the coefficient of performance for a refrigerator, COP =QW
c .
Using the result from part (a), this becomes COP =−
TT T
c
h c.
P18.18 COP heat pumpa f =+
= = =Q W
WT
Tc h
∆29525
11 8.
P18.19 COP COPCarnot cycle= 0 100.
or QW
QW
h h=FHGIKJ =
FHG
IKJ0 100 0 100
1. .
Carnot cycleCarnot efficiency
QW
TT T
h h
h c=
−FHG
IKJ = −
FHG
IKJ =0 100 0 100
293268
1 17. . . K
293 K K
FIG. P18.19
Thus, 1 17. joules of energy enter the room by heat for each joule of work done.
*P18.20 eWQh
= = 0 350. W Qh= 0 350.
Q W Qh c= + Q Qc h= 0 650.
COP refrigeratorb g = = =QW
c h
h
0 6500 350
1 86..
.
P18.21 COP Carnot refriga f = = = =TT
QW
c c
∆4 00289
0 013 8.
.
∴ =W 72 2. J per 1 J energy removed by heat.
*P18.22 (a) The TV set uses energy at the rate 40015
3 6 1060
100 106
3 J skWh
1 kWh. J
s
$0.min
$1. minFHGIKJ ×FHG
IKJFHG
IKJ = × − .
(b) An air conditioner is a refrigerator:
COP
QW
Wt COP
cQ
tW
t
Qt
c
c
= =
= = =
∆
∆
∆
∆400
4 5088 9
J s J s
..
continued on next page
Chapter 18 501
This is the rate at which extra electric energy is required by the air conditioner to keep the room cool, with cost
88 915
1 0001
6022 10 4.
$0.min
$2. minWkwh
k
h
FHGIKJFHGIKJFHG
IKJ = × − .
(c) Your father blames his extra output of 170 120 50W W W− = on the TV set. It must be
pumped out of the room by the air conditioner, with power expenditure
W
tQ tCOP
c
∆∆
= = FHGIKJFHGIKJFHG
IKJ = × −50
4 5015
1 0001
6078 10 5 W
kWhk
h
.$0.
min$2. min .
Section 18.5 An Alternative Statement of the Second Law No problems in this section
Section 18.6 Entropy Section 18.7 Entropy and the Second Law of Thermodynamics
P18.23 ∆SdQT
mcdTT
mcT
Ti
f
T
Tf
ii
f
= = =FHGIKJz z ln
∆S = ⋅° FHGIKJ = =250
353293
46 6 195 g 1.00 cal g C cal K J Kb g ln .
P18.24 For a freezing process,
∆ ∆S
QT
= =− ×
= −0 500 3 33 10
273610
5. . kg J kg
K J K
b ge j.
*P18.25 (a) The process is isobaric because it takes place under constant atmospheric pressure. As
described by Newton’s third law, the stewing syrup must exert the same force on the air as the air exerts on it. The heating process is not adiabatic (energy goes in by heat), isothermal (T goes up), isovolumetic (it likely expands a bit), cyclic (it is different at the end), or isentropic (entropy increases). It could be made as nearly reversible as you wish, by not using a kitchen stove but a heater kept always just incrementally higher in temperature than the syrup. The process would then also be eternal, and impractical for food production.
(b) The final temperature is
220 212 8 100 8032
104° = ° + ° = ° + ° − °− °
FHG
IKJ = °F F F C F
100 C212 F
C.
continued on next page
502 Heat Engines, Entropy, and the Second Law of Thermodynamics
For the mixture,
Q m c T m c T= + = ⋅° + ⋅° ° − °
= × = ×
1 1 2 2
4 5
900 930 104 4 23
9 59 10 4 02 10
∆ ∆ g 1 cal g C g 0.299 cal g C C C
cal J
b ga f.
. .
(c) Consider the reversible heating process described in part (a):
∆SdQT
m c m c dTT
m c m cT
Ti
f
i
ff
i= =
+= +
= + ° FHGIKJ
°FHGIKJ
++
FHG
IKJ
= = ×
z z 1 1 2 21 1 2 2
3
900 1 930 0 2994 186 1 273 104
273 23
4 930 1 20 10
b g b g
a f a f b gb g
ln
..
ln
.
cal C J
1 calC
1 K
J K 0.243 J K
P18.26 We take data from Tables 17.1 and 17.2, and we assume a constant specific heat for each phase. As
the ice is warmed from –12°C to 0°C, its entropy increases by
∆
∆
∆
SdQT
mc dTT
mc T dT mc T
S
S
i
f
= = = =
= ⋅° − = ⋅° FHGIKJ
FHG
IKJ
=
z z z −ice
K
273 K
ice K
273 K
ice K273 K
kg 2 090 J kg C K K kg 2 090 J kg C
J K
261
1
261261
0 027 9 273 261 0 027 9273261
2 62
ln
. ln ln . ln
.
b ga f b g
As the ice melts its entropy change is
∆SQT
mL
Tf= = =
×=
0 027 9
27334 0
..
kg 3.33 10 J kg
K J K
5e j
As liquid water warms from 273 K to 373 K,
∆Smc dT
Tmc
T
Ti
ff
i= =
FHGIKJ = ⋅° F
HGIKJ =z liquid
liquid kg 4 186 J kg C J Kln . ln .0 027 9373273
36 5b g
As the water boils and the steam warms,
∆
∆
SmL
Tmc
T
T
S
v f
i= +
FHGIKJ
=×
+ ⋅° FHGIKJ = +
steam
6 kg 2.26 10 J kg
K kg 2 010 J kg C J K J K
ln
.. ln .
0 027 9
3730 027 9
388373
169 2 21e j b g
The total entropy change is
2 62 34 0 36 5 169 2 21 244. . . .+ + + + =a f J K J K .
For steam at constant pressure, the molar specific heat in Table 17.3 implies a specific heat of
35 41
1 970. J mol K mol
0.018 kg J kg K⋅
FHG
IKJ = ⋅b g , nearly agreeing with 2 010 J kg K⋅ .
Chapter 18 503
P18.27 (a) A 12 can only be obtained one way: 6 6+
(b) A 7 can be obtained six ways: 6 1+ , 5 2+ , 4 3+ , 3 4+ , 2 5+ , 1 6+
P18.28 (a) The table is shown below. On the basis of the table, the most probable result of a toss is
2 heads and 2 tails .
(b) The most ordered state is the least likely state. Thus, on the basis of the table this is
either all heads or all tails .
(c) The most disordered is the most likely state. Thus, this is 2 heads and 2 tails .
Result Possible Combinations Total All heads HHHH 1 3H, 1T THHH, HTHH, HHTH, HHHT 4 2H, 2T TTHH, THTH, THHT, HTTH, HTHT, HHTT 6 1H, 3T HTTT, THTT, TTHT, TTTH 4 All tails TTTT 1 P18.29 (a) Result Possible Combinations Total All red RRR 1 2R, 1G RRG, RGR, GRR 3 1R, 2G RGG, GRG, GGR 3 All green GGG 1 (b) Result Possible Combinations Total All red RRRRR 1 4R, 1G RRRRG, RRRGR, RRGRR, RGRRR, GRRRR 5 3R, 2G RRRGG, RRGRG, RGRRG, GRRRG, RRGGR, RGRGR, GRRGR, RGGRR, GRGRR, GGRRR 10 2R, 3G GGGRR, GGRGR, GRGGR, RGGGR, GGRRG, GRGRG, RGGRG, GRRGG, RGRGG, RRGGG 10 1R, 4G RGGGG, GRGGG, GGRGG, GGGRG, GGGGR 5 All green GGGGG 1
Section 18.8 Entropy Changes in Irreversible Processes
P18.30 ∆SQT
QT
= − = −FHG
IKJ =2
2
1
1
1 000290
1 0005 700
3 27 J K J K.
P18.31 The car ends up in the same thermodynamic state as it started, so it undergoes zero changes in
entropy. The original kinetic energy of the car is transferred by heat to the surrounding air, adding to the internal energy of the air. Its change in entropy is
∆SmvT
= = =12
2 2750 20 0293
1 02.
.a f
J K kJ K .
504 Heat Engines, Entropy, and the Second Law of Thermodynamics
P18.32 c iron J kg C= ⋅°448 ; cwater J kg C= ⋅°4 186
Q Qcold hot= − : 4 00 10 0 1 00 448 900. . . kg 4 186 J kg C C kg J kg C C⋅° − ° = − ⋅° − °b gd i b gb gd iT Tf f
which yields Tf = ° =33 2 306 2. .C K
∆
∆
∆
∆
Sc m dT
Tc m dT
T
S c m c m
S
S
= +
= FHGIKJ +
FHGIKJ
= ⋅ + ⋅ −
=
z zwater water
K
306.2 Kiron iron
K
306.2 K
water water iron iron
J kg K kg J kg K kg
J K
283 1 173
306 2283
306 21 173
4 186 4 00 0 078 8 448 1 00 1 34
718
ln.
ln.
. . . .b gb gb g b gb ga f
P18.33 Sitting here writing, I convert chemical energy, in ordered molecules in food, into internal energy
that leaves my body by heat into the room-temperature surroundings. My rate of energy output is equal to my metabolic rate,
2 5002 500 10 4 186
1203
kcal d cal
86 400 s J
1 cal W=
× FHG
IKJ =
..
My body is in steady state, changing little in entropy, as the environment increases in entropy at the
rate
∆∆ ∆
∆St
Q Tt
Q tT
= = = =1200 4 1
W293 K
W K W K. ~ .
When using powerful appliances or an automobile, my personal contribution to entropy production
is much greater than the above estimate, based only on metabolism.
P18.34 ∆S nRV
VRf
i=FHGIKJ = =ln ln .2 5 76 J K
There is no change in temperature .
FIG. P18.34
P18.35 ∆S nRV
VRf
i=FHGIKJ =ln . ln0 044 0 2 2b ga f
∆S = =0 088 0 8 314 2 0 507. . ln .a f J K
FIG. P18.35
Chapter 18 505
Section 18.9 Context ConnectionThe Atmosphere as a Heat Engine
P18.36 The Earth presents a circular projected area of π 6 37 106 2. × me j perpendicular to the direction of
energy flow in sunlight. The power incident on the Earth is then
P = = ×LNM
OQP = ×IA 1 370 6 37 10 1 75 106 2 17 W m m W2e j e jπ . . .
The power absorbed in the atmosphere is 0 64 1 75 10 1 1 1017 17. . .× = × W We j . The mechanical wind
power is 0 008 1 1 10 9 1017 14. . × = × W We j .
P18.37 (a) The volume of the air is π r h2 and its mass is m V r h= =ρ ρπ 2 . Then its kinetic energy is
K mv r hv
K
K
= =
= FHG
IKJ
= ×
12
12
12
1 20 300 000 11 00060 0003 600
5 2 10
2 2 2
22
17
ρ π
π.
.
kg m m m m s
J
3e j a f a f
(b) We can suppose the light shines perpendicularly down onto the hurricane. Its intensity is
IA
EA t
tEAI
= = = = × ⋅ ⋅
×= ×P
∆∆:
..
5 2 10
3 10 101 8 10
17
5 2 3
3 J m s
m J s
2
π e j e j.
Additional Problems
P18.38 For the Carnot engine, eTTc
c
h= − = − =1 1
3000 600
K750 K
. .
Also, eW
Qch
= eng .
so QW
ehc
= = =eng J J
1500 600
250.
.
and Q Q Wc h= − = − =eng J J J250 150 100 .
FIG. P18.38
(a) QW
ehS
= = =eng J0.700
J150
214
Q Q Wc h= − = − =eng J J J214 150 64 3.
(b) Qh, .net J J J= − = −214 250 35 7
Qc , . .net J J J= − = −64 3 100 35 7
The net flow of energy by heat from the cold to the hot reservoir without work input, is impossible.
FIG. P18.38(b)
continued on next page
506 Heat Engines, Entropy, and the Second Law of Thermodynamics
(c) For engine S: Q Q WW
eWc h
S= − = −eng
engeng .
so WQc
eS
eng J
J=−
=−
=1 10 7001100
1233
.
.
and Q Q Wh c= + = + =eng J J J233 100 333 .
(d) Qh, .net J J J= − =333 250 83 3
Wnet J J J= − =233 150 83 3.
Qc ,net = 0
The output of 83.3 J of energy from the heat engine by work in a cyclic process without any exhaust by heat is impossible.
FIG. P18.38(d)
(e) Both engines operate in cycles, so ∆ = ∆ =S SS Carnot 0 .
For the reservoirs, ∆ = −SQTh
h
h and ∆ = +S
QTc
c
c.
Thus, ∆ = ∆ + ∆ + ∆ + ∆ = + − + = −S S S S SS h ctotal CarnotJ
750 K K J K0 0
83 3 0300
0 111.
. .
A decrease in total entropy is impossible. P18.39 As in Section 6.6, let TET represent the energy transferred by electrical transmission. Then
(a) Pelectric =T
tET
∆ so if all the electric energy is converted into internal energy, the steady-state
condition of the house is described by T QET = .
Therefore, Pelectric W= =Qt∆
5 000
(b) For a heat pump, COPK
27 KCarnota f = = =T
Th
∆295
10 92.
Actual COP = = = =0 6 10 92 6 55. . .a f QW
Q tW t
h h ∆∆
Therefore, to bring 5 000 W of energy into the house only requires input power
Pheat pump COP W
6.56 W= = = =W
tQ th
∆∆ 5 000
763
Chapter 18 507
P18.40 The conversion of gravitational potential energy into kinetic energy as the water falls is reversible. But the subsequent conversion into internal energy is not. We imagine arriving at the same final state by adding energy by heat, in amount mgy, to the water from a stove at a temperature infinitesimally above 20.0°C. Then,
∆SdQT
QT
mgyT
= = = = = ×z 5 000 1 000 9 80 50 0
2938 36 106
m kg m m s m
K J K
3 3 2e je ja f. .. .
P18.41 Q mc T mL mc Tc = + + =∆ ∆
Q
Q
QW
TT T
WQ T T
T
c
c
cc
c
h c
c h c
c
= ⋅° ° + × + ⋅° °
= ×
= =−
=−
=× ° − − °
−=
0 500 10 0 500 0 500 20
2 08 10
2 08 10 20 0 20 0
273 20 032 9
5
5
. . .
.
. . .
..
kg 4 186 J kg C C kg 3.33 10 J kg kg 2 090 J kg C C
J
COP refrigerator
J C C
K kJ
5b ga f e j b ga f
b g
b g e j a fa f
*P18.42 (a) Let state i represent the gas before its compression and state f afterwards, VV
fi=
8. For a
diatomic ideal gas, C Rv = 52
, C Rp = 72
, and γ = =C
Cp
V1 40. . Next,
PV P V
P PVV
P P
PV nRT
P VPV
PV nRT nRT
i i f f
f ii
fi i
i i i
f fi i
i i i f
γ γ
γ
=
=FHGIKJ = =
=
= = = =
8 18 4
18 48
2 30 2 30
1.40 .
.. .
so T Tf i= 2 30.
∆ ∆E nC T n R T T nR T PVV f i i i iint . .
. . . .
= = − = =
= × × =−
52
52
1 3052
1 30
52
1 30 1 013 10 0 12 10 39 45 3 3
d i
e j N m m J2
Since the process is adiabatic, Q = 0 and ∆E Q Wint = + gives W = 39 4. J .
(b) The moment of inertia of the wheel is I MR= = = ⋅12
12
5 1 0 085 0 018 42 2. . . kg m kg m2a f . We
want the flywheel to do work 39.4 J, so the work on the flywheel should be –39.4 J:
continued on next page
508 Heat Engines, Entropy, and the Second Law of Thermodynamics
K W K
I
i f
i
i
rot rot
2
J
J kg m
rad s
+ =
− =
=⋅
FHG
IKJ =
12
39 4 0
2 39 40 018 4
65 4
2
1 2
ω
ω
.
..
.a f
(c) Now we want W K i= 0 05. rot
39 4 0 0512
0 018 4
2 789
0 018 4293
2
1 2
. . .
.
J i= ⋅
=⋅
FHG
IKJ =
kg m
J
kg mrad s
2
2
ω
ω a f
P18.43 (a) For an isothermal process, Q nRTVV
=FHGIKJln 2
1
Therefore, Q nR Ti1 3 2= b g ln
and Q nR Ti312
= FHGIKJb g ln
For the constant volume processes, Q E nR T Ti i232
3= = −∆ int, 2 b g
and Q E nR T Ti i432
3= = −∆ int, 4 b g
The net energy by heat transferred is then
Q Q Q Q Q= + + +1 2 3 4
FIG. P18.43
or Q nRTi= 2 2ln .
(b) A positive value for heat represents energy transferred into the system.
Therefore, Q Q Q nRTh i= + = +1 4 3 1 2lna f
Since the change in temperature for the complete cycle is zero,
∆Eint = 0 and W Qeng =
Therefore, the efficiency is eW
QQQc
h h= = =
+=eng 2 2
3 1 20 273
lnln
.a f
P18.44 ∆Shot J
600 K=
−1 000
∆Scold J
350 K= +750
(a) ∆ ∆ ∆S S SU = + =hot cold J K0 476.
continued on next page
Chapter 18 509
(b) eTTc = − =1 0 4171
2.
W e Qc heng J J= = =0 417 1 000 417. b g
(c) Wnet J J J= − =417 250 167
T SU1 350 167∆ = = K 0.476 J K Jb g
P18.45 eTT
W
Qcc
h h
Wt
Qth
= − = =1 engeng
∆
∆
: Q
tT
T Th
TT
h
h cc
h∆
=−
=−
P P
1e j
Q W Qh c= +eng : Q
tQ
t
W
tc h
∆ ∆ ∆= − eng
Q
tT
T TT
T Tc h
h c
c
h c∆=
−− =
−P
PP
Q mc Tc = ∆ : Q
tmt
c TT
T Tc c
h c∆∆∆
∆= FHGIKJ =
−P
∆∆ ∆mt
TT T c T
c
h c=
−P
b g
∆∆mt
=×
⋅° °= ×
1 00 10 300
200 6 005 97 10
94
.
..
W K
K 4 186 J kg C C kg s
e ja fb ga f
P18.46 eTT
W
Qcc
h h
Wt
Qth
= − = =1 engeng
∆
∆
Q
tT
T Th
TT
h
h cc
h∆
=−
=−
P P
1e j
Q
tQ
tT
T Tc h c
h c∆ ∆=FHGIKJ − =
−P
P
Q mc Tc = ∆ , where c is the specific heat of water.
Therefore, Q
tmt
c TT
T Tc c
h c∆∆∆
∆= FHGIKJ =
−P
and ∆∆ ∆mt
TT T c T
c
h c=
−P
b g .
We test for dimensional correctness by identifying the units of the right-hand side: W C
C J kg C C
J s kg
Jkg s
⋅°° ⋅° °
= =b gb g
, as on the left hand side. Think of yourself as a power-company
engineer arranging to have enough cooling water to carry off your thermal pollution. If the plant power P increases, the required flow rate increases in direct proportion. If environmental regulations require a smaller temperature change, then the required flow rate increases again, now in inverse proportion. If you can run the reactor core or firebox hotter, since Th is in the bottom of the fraction, the required flow rate decreases! If the turbines take in steam at higher temperature, they can be made more efficient to reduce waste heat output.
510 Heat Engines, Entropy, and the Second Law of Thermodynamics
P18.47 We want to evaluate dPdV
for the function implied by PV nRT= = constant , and also for the different
function implied by PV γ = constant . We can use implicit differentiation:
From PV = constant PdVdV
VdPdV
+ = 0 dPdV
PV
FHGIKJ = −
isotherm
From PV γ = constant P V VdPdV
γ γ γ− + =1 0 dPdV
PV
FHGIKJ = −
adiabat
γ
Therefore, dPdV
dPdV
FHGIKJ = FHG
IKJadiabat isotherm
γ . The theorem is proved.
*P18.48 (a) 35 059
35 0 32 0 1 67 273 15 274 82. . . . . .° = − ° = + =F C K Ka f a f
98 659
98 6 32 0 37 0 273 15 310 15
453 6 1 00 453 6310 15274 82
54 86
453 6 1 00310 15 274 82
310 1551 67
54 86 51 67 3 19
274.82
310 15
. . . . . .
. . . ln..
.
. .. .
..
. . .
.
° = − ° = + =
= = ⋅ × = FHG
IKJ =
= − = −−
= −
= − =
z zF C K K
g cal g K cal K
cal K
cal K
ice water
bodybody
system
a f a f
b gb g
a fa f a f∆
∆
∆
SdQT
dTT
SQ
T
S
(b) 453 6 1 274 82 70 0 10 1 310 153. . . .a fa fb g e ja fb gT TF F− = × −
Thus,
70 0 0 453 6 10 70 0 310 15 0 453 6 274 82 103 3. . . . . .+ × = + ×b g a fa f b ga fTF
and TF = = ° = °309 92 36 77 98 19. . . K C F
∆
∆
′ = FHG
IKJ =
′ = − × FHG
IKJ = −
S
S
ice water
body
cal K
cal K
453 6309 92274 82
54 52
70 0 10310 15309 92
51 933
. ln..
.
. ln..
.e j
∆ ′ = − =Ssys cal K54 52 51 93 2 59. . . which is less than the estimate in part (a).
Chapter 18 511
P18.49 (a) For the isothermal process AB, the work on the gas is
W P VVV
W
W
AB A AB
A
AB
AB
= −FHGIKJ
= − × × FHGIKJ
= − ×
−
ln
. . ln..
.
5 1 013 10 10 0 1050 010 0
8 15 10
5 3
3
Pa m
J
3e je j
where we have used 1 00 1 013 105. .atm Pa= ×
and 1 00 1 00 10 3. .L m3= × −
FIG. P18.49
W P VBC B= − = − × − × = + ×−∆ 1 013 10 10 0 50 0 10 4 05 105 3 3. . . . Pa m J3e j a f
WCA = 0 and W W WAB BCeng J kJ= − − = × =4 11 10 4 113. .
(b) Since AB is an isothermal process, ∆E ABint, = 0
and Q WAB AB= − = ×8 15 103. J
For an ideal monatomic gas, CR
V = 32
and CR
P = 52
T TP VnR R RB AB B= = =
× ×= ×
−1 013 10 50 0 10 5 05 105 3 3. . .e je j
Also, TP VnR R RCC C= =
× ×= ×
−1 013 10 10 0 10 1 01 105 3 3. . .e je j
Q nC T RRCA V= = F
HGIKJ
× − ×FHG
IKJ =∆ 1 00
32
5 05 10 1 01 106 08
3 3
.. .
. kJ
so the total energy absorbed by heat is Q QAB CA+ = + =8 15 6 08 14 2. . . kJ kJ kJ .
(c) Q nC T nR T P VBC P B BC= = =∆ ∆ ∆52
52
a f
QBC = × − × = − × = −−52
1 013 10 10 0 50 0 10 1 01 10 10 15 3 4. . . . .e j a f J kJ
(d) eW
Q
W
Q Qh AB CA= =
+= ×
×=eng eng
4 J
1.42 10 J4 11 10
0 2893.
. or 28 9%.
512 Heat Engines, Entropy, and the Second Law of Thermodynamics
P18.50 Like a refrigerator, an air conditioner has as its purpose the removal of energy by heat from the cold reservoir.
Its ideal COP is COPK
20 KCarnot =−
= =T
T Tc
h c
28014 0.
(a) Its actual COP is 0 400 14 0 5 60. . .a f = =−
=−
QQ Q
Q t
Q t Q tc
h c
c
h c
∆∆ ∆
5 60 5 60. .Q
tQ
tQ
th c c
∆ ∆ ∆− =
5 60 10 0 6 60. . . kWa f = Qtc
∆ and
Qtc
∆= 8 48. kW
(b) Q W Qh c= +eng : W
tQ
tQ
th ceng kW kW kW
∆ ∆ ∆= − = − =10 0 8 48 1 52. . .
(c) The air conditioner operates in a cycle, so the entropy of the working fluid does not change.
The hot reservoir increases in entropy by
QT
h
h=
×= ×
10 0 10 3 600
3001 20 10
35
..
J s s
K J K
e jb g
The cold room decreases in entropy by
∆SQT
c
c= − = −
×= − ×
8 48 10 3 600
2801 09 10
35
..
J s s
K J K
e jb g
The net entropy change is positive, as it must be:
+ × − × = ×1 20 10 1 09 10 1 09 105 5 4. . . J K J K J K
(d) The new ideal COP is COPK
25 KCarnot =−
= =T
T Tc
h c
28011 2.
We suppose the actual COP is 0 400 11 2 4 48. . .a f =
As a fraction of the original 5.60, this is 4 485 60
0 800..
.= , so the fractional change is to
drop by 20.0% .
Chapter 18 513
P18.51 At point A, PV nRTi i i= and n = 1 00. mol
At point B, 3PV nRTi i B= so T TB i= 3
At point C, 3 2P V nRTi i Cb gb g = and T TC i= 6
At point D, P V nRTi i D2b g = so T TD i= 2
The heat for each step in the cycle is found using CR
V = 32
and
CR
P = 52
:
Q nC T T nRT
Q nC T T nRT
Q nC T T nRT
Q nC T T nRT
AB V i i i
BC P i i i
CD V i i i
DA P i i i
= − =
= − =
= − = −
= − = −
3 3
6 3 7 50
2 6 6
2 2 50
b gb gb gb g
.
.
Q3
Q4
B C
DA
FIG. P18.51
(a) Therefore, Q Q Q Q nRTh AB BC ientering = = + = 10 5.
(b) Q Q Q Q nRTc CD DA ileaving = = + = 8 50.
(c) Actual efficiency, eQ Q
Qh c
h=
−= 0 190.
(d) Carnot efficiency, eTT
TTc
c
h
i
i= − = − =1 1
60 833.
P18.52 ∆SdQT
nC dTT
nC T dT nC T nC T T nCT
Ti
fP
i
f
Pi
f
P TT
P f i Pf
ii
f= = = = = − =FHGIKJz z z −1 ln ln ln lnd i
∆S nCPV
nRnRPV
nCPf
iP=
FHG
IKJ =ln ln3
P18.53 (a) The ideal gas at constant temperature keeps constant
internal energy. As it puts out energy by work in expanding it must take in an equal amount of energy by heat. Thus its entropy increases. Let Pi , Vi , Ti represent the state of the gas before the isothermal expansion. Let PC , VC , Ti represent the state after this process, so that PV P Vi i C C= . Let Pi , 3Vi , Tf represent
the state after the adiabatic compression.
Then P V P VC C i iγ γ= 3b g
A B
C
Pi
PC
Vi 3ViV
P
FIG. P18.53
Substituting PPVVCi i
C=
continued on next page
514 Heat Engines, Entropy, and the Second Law of Thermodynamics
gives PV V P Vi i C i iγ γ γ− =1 3e j
Then V VC iγ γ γ− −=1 13 and
VV
C
i= −3 1γ γb g
The work output in the isothermal expansion is
W PdV nRT V dV nRTVV
nRT nRTi
C
ii
C
iC
ii i= = =
FHGIKJ = =
−FHGIKJz z − −1 13
13ln ln lnγ γ γ
γb ge j
This is also the input heat, so the entropy change is
∆SQT
nR= =−FHGIKJ
γγ 1
3ln
Since C C C RP V V= = +γ
we have γ − =1b gC RV , CR
V =−γ 1
and CR
P =−
γγ 1
Then the result is ∆S nCP= ln3
(b) The pair of processes considered here carry the gas from the initial state in Problem 18.52 to
the final state there. Entropy is a function of state. Entropy change does not depend on path. Therefore the entropy change in Problem 18.52 equals ∆ ∆S Sisothermal adiabatic+ in this problem. Since ∆Sadiabatic = 0, the answers to Problems 18.52 and 18.53 (a) must be the same.
*P18.54 Simply evaluate the maximum (Carnot) efficiency.
eT
TCh
= = =∆ 4 000 014 4
..
K277 K
The proposal does not merit serious consideration. P18.55 (a) Use the equation of state for an ideal gas
VnRT
P
V
V
A
C
=
=×
= ×
=×
= ×
−
−
1 00 8 314 600
25 0 1 013 101 97 10
1 00 8 314 400
1 013 1032 8 10
53
53
. .
. ..
. .
..
a fa fe ja fa f
m
m
3
3
Since AB is isothermal, P V P VA A B B=
FIG. P18.55
and since BC is adiabatic, P V P VB B C Cγ γ=
continued on next page
Chapter 18 515
Combining these expressions, VPP
VVB
C
A
C
A=FHGIKJ
LNMM
OQPP = FHG
IKJ
×
×
L
NMMM
O
QPPP
− −
−
γ γ1 1 3 1.40
3
1 0 400
1 0025 0
32 8 10
1 97 10
b g b ge j.
.
.
.
.
m
m
3
3
VB = × −11 9 10 3. m3
Similarly, VPP
VVD
A
C
A
C=FHGIKJ
LNMM
OQPP = FHG
IKJ
×
×
L
NMMM
O
QPPP
− −
−
γ γ1 1 3 1.40
3
1 0 400
25 01 00
1 97 10
32 8 10
b g b ge j.
.
.
.
.
m
m
3
3
or VD = × −5 44 10 3. m3
Since AB is isothermal, P V P VA A B B=
and P PVVB A
A
B=FHGIKJ =
××
FHG
IKJ =
−
−25 011 9 10
4 143..
. atm1.97 10 m
m atm
3 3
3
Also, CD is an isothermal and P PVVD C
C
D=FHGIKJ =
××
FHG
IKJ =
−
−1 005 44 10
6 033
3..
. atm32.8 10 m
m atm
3
3
Solving part (c) before part (b):
(c) For this Carnot cycle, eTTc
c
h= − = − =1 1
4000 333
K600 K
.
(b) Energy is added by heat to the gas during the process AB. For the isothermal process,
∆Eint = 0 .
and the first law gives Q W nRTVVAB AB h
B
A= − =
FHGIKJln
or Q Qh AB= = ⋅ FHGIKJ =1 00 600
11 91 97
8 97. ln.
.. mol 8.314 J mol K K kJb ga f
Then, from eW
Qh= eng
the net work done per cycle is W e Qc heng kJ kJ= = =0 333 8 97 2 99. . .a f .
P18.56 Q
WT
T Tc c
h c
Qt
Wt
c
= =−
=COP refrigeratorC b g ∆
∆
0 150 260
0 150 23 1
.
. .
W K40.0 K
W40.0 K260 K
mW
Wt
Wt
∆
∆
=
= = FHG
IKJ =P
516 Heat Engines, Entropy, and the Second Law of Thermodynamics
P18.57 Define T1 5 00= = ° =Temp Cream . C 278 K . Define T2 60 0= = ° =Temp Coffee C 333 K. . The final
temperature of the mixture is: TT T
f =+
= ° =( . ) ( )
.20 0 200
22055 0 3281 2g g
gC K . The entropy change due
to this mixing is ∆Sc dT
Tc dT
TV
T
T VT
Tf f= +z z20 0 2001 2
. g gb g b g
∆
∆
ST
T
T
T
S
f f=FHGIKJ +
FHGIKJ =
FHGIKJ +
FHGIKJ
= +
84 0 840 84 0328278
840328333
1 18
1 2. ln ln . ln ln
.
J K J K K J J K
J K
b g b g b g b g
P18.58 No energy is transferred by heat during the adiabatic processes. Energy Qh is added by heat during
process BC and energy Qh is exhausted during process DA. We have Q nC T Th V C B= −b g and
Q nC T TC V D A= −b g . So eQ
QT TT T
C
h
D A
C B= − = −
−−
1 1 . For the adiabatic processes, P V P VC D2 1γ γ= and
P V P VB A2 1γ γ= .
From the gas law PnRT
VCC=
2 P
nRTVD
D=1
PnRT
VBB=
2 P
nRTVA
A=1
Then nRT V nRT VC D21
11γ γ− −= and T V T VB A2
11
1γ γ− −= . Thus, TT
VV
rC
D=FHGIKJ =
−−1
2
11
γγ and
TT
VV
rB
A=FHGIKJ =
−−1
2
11
γγ . Then e
T TT r T r r
rD A
D A
= −−−
= − = −− − −−1 1
111 1 1
1γ γ γ
γ .
ANSWERS TO EVEN PROBLEMS P18.2 (a) 29 4. L h; (b) 185 hp; (c) 527 N m⋅ ; (d) 1 91 105. × W P18.4 13 7. °C P18.6 (a) 870 MJ; (b) 330 MJ P18.8 546°C P18.10 (a) 5 12%. ; (b) 5 27. TJ h; (c) As conventional energy sources become
more expensive, or as their true costs are recognized, alternative sources become economically viable.
P18.12 (a) State P (kPa) V (L) T (K) A 1 400 10.0 720 B 875 16.0 720 C 445 24.0 549 D 712 15.0 549
(b) Process Q (kJ) W (kJ) ∆Eint (kJ) A→B 6.58 –6.58 0 B→C 0 –4.98 –4.98 C→D −5.02 5.02 0 D→A 0 4.98 4.98 ABCDA 1.56 –1.56 0 P18.14 77 8. W P18.16 9.00 P18.18 11.8 P18.20 1.86 P18.22 (a) $1. min00 10 3× − ; (b) $2. min22 10 4× − ;
(c) $2. min78 10 5× − P18.24 −610 J K
Chapter 18 517
P18.26 244 J K P18.28 (a) 2 heads and 2 tails ; (b) either all heads or all tails ; (c) 2 heads and 2 tails P18.30 3 27. J K P18.32 718 J K P18.34 5 76. J K , no change in temperature P18.36 9 1014× W P18.38 (a) 214 J, 64.3 J; (b) –35.7 J, –35.7 J. The net effect is the
transport of energy by heat from the cold to the hot reservoir without expenditure of external work.
(c) 333 J, 233 J; (d) 83.3 J, 83.3 J, 0. The net effect is
converting energy, taken in as heat, entirely into energy output by work in a cyclic process.
(e) −0 111. J K , the entropy of the Universe has decreased.
P18.40 8 36 106. × J K P18.42 (a) 39 4. J ; (b) 65 4. rad s ; (c) 293 rad s P18.44 (a) 0 476. J K ; (b) 417 J ; (c) W T SUnet J= =1 167∆
P18.46 mt
TT T c T
c
h c=
−P
b g ∆
P18.48 (a) 3 19. cal K; (b) 98 19. °F, 2 59. cal K P18.50 (a) 8 48. kW ; (b) 1 52. kW ; (c) 1 09 104. × J K ; (d) COP drops by 20.0% P18.52 nCP ln3 P18.54 No, the device cannot meet its
specifications, according to the second law of thermodynamics.
P18.56 23 1. mW P18.58 see the solution
CONTEXT 5 CONCLUSION SOLUTIONS TO PROBLEMS CC5.1 We take 214 K as the tropopause temperature and − °6 5. C km as the lapse rate. Then
214 6 5 13 84
298 K
K C km km Csurface
surface
− = − ° = − °
=
T
T
.b g
CC5.2 The lapse rate is
∆∆
=−
−
=−
= −− °
=∆∆
Ty
T T
y
yT T
Ty
tropopause surface
tropopause
tropopausetropopause surface K K
C km km
0
200 7328 8
60.
518 Heat Engines, Entropy, and the Second Law of Thermodynamics
CC5.3 (a) The power balance equation for the planet as a whole is
P Pabsorbed emitted absorbing emitting
2 2 4
2
2 4
W m W m K
W m
W m K K
= =
= × ⋅
=× ⋅
=
−
−
:
. .
.
.
e I A e A T
R R T
T
vis s ir
E E
σ
π π
14
2 8 21
4
1 8
4
0 70 1 370 1 5 67 10 4
0 70 1370
4 5 67 10255
e j e jd ie j
e j
(b) The power balance equation for layer 1, required for the constancy of its temperature, is
e R T e R Tir E ir Eσ π σ π8 421
4 22
4d i d i= or 2 14
24T T= . Similarly, for layer 2, 2 2
41
43
4T T T= + . Again,
2 234
24
44 4
14 4T T T T T TN N S= + = +−,K . Thus, T T2
412= .
By substitution, 4 14
14
34T T T= + T T3
413=
6 214
14
44T T T= + T T T NTN4
41
414= =,K
and T N TS = + 1 1 41a f /
(c) From part (b), TS = + =2 1 255 3361 4a f a f/ K K .
(d) The troposphere and stratosphere are too thick to be accurately modeled as having uniform
temperatures. (e) Venus is at 1 08 1011. × m from the Sun, instead of 1 496 1011. × m like the Earth. The intensity
of solar radiation incident on Venus is then 1 3701 4961 08
2 63 102
3 W m W m2 2e j ..
.FHGIKJ = × . The
overall power balance equation for Venus is e I A e A Tvis s irabsorbing emitting= σ 14
1 0 77 2 63 10 1 5 67 10 4
0 23 2 63 10
4 5 67 10227
3 2 8 21
4
1
3
8
4
− × = × ⋅
=×
× ⋅=
−
−
. . .
. .
.
a fe jd i e jd ie j
e j
W m W m K
W m
W m K K
2 2 4
2
2 4
π πR R T
T
V V
(f) T N T NTTS
S= + =FHGIKJ − = FHG
IKJ − =1 1
732227
1 1071 41
1
4 4
a f / :
(g) The multi-layer model should be better for Venus than for Earth. There are many layers, so
the temperature of each can be reasonably uniform.
ANSWERS TO EVEN CONTEXT 5 CONCLUSION PROBLEMS CC5.2 60 km