heat chap13 054
TRANSCRIPT
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Chap 15Heat Exchangers
13-54 Glycerin is heated by ethylene glycol in a thin-walled double-pipe parallel-flow heat exchanger. Therate of heat transfer, the outlet temperature of the glycerin, and the mass flow rate of the ethylene glycolare to be determined.
Assumptions1 Steady operating conditions exist. 2 The heat exchanger is well-insulated so that heat lossto the surroundings is negligible and thus heat transfer from the hot fluid is equal to the heat transfer tothe cold fluid. 3 Changes in the kinetic and potential energies of fluid streams are negligible. 4 There isno fouling. 5 Fluid properties are constant. 6 The thermal resistance of the inner tube is negligible since
the tube is thin-walled and highly conductive.Properties The specific heats of glycerin and ethyleneglycol are given to be 2.4 and 2.5 kJ/kg.C,respectively.
Analysis (a) The temperature differences at thetwo ends are
T T T
T T T T T
h in c in
h out c out h out h out
1
2
60 20
15
= =
= =
, ,
, , , ,(
C C = 40 C
C) = 15 C
and
T
T T
T Tlm =
=
= 1 2
1 2
40 15
40 15255
ln( / ) ln( / ). C
Then the rate of heat transfer becomes
kW19.58==== W584,19C)5.25)(mC)(3.2.W/m240( 22lms TUAQ
(b) The outlet temperature of the glycerin is determined from
C47.2=
+=+==C)kJ/kg.kg/s)(2.43.0(
kW584.19C20)]([ glycerin
pinoutinoutp
Cm
QTTTTCmQ
(c) Then the mass flow rate of ethylene glycol becomes
kg/s3.56=
=
=
=
C]60C15)+C)[(47.2kJ/kg.(2.5
kJ/s584.19
)(
)]([
glycolethylene
glycolethylene
outinp
outinp
TTC
Qm
TTCmQ
13-37
Glycerin20C0.3 kg/s
Hot ethylene
60C3 kg/s
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Chap 15Heat Exchangers
13-55 Air is preheated by hot exhaust gases in a cross-flow heat exchanger. The rate of heat transfer andthe outlet temperature of the air are to be determined.
Assumptions1 Steady operating conditions exist. 2 The heat exchanger is well-insulated so that heat lossto the surroundings is negligible and thus heat transfer from the hot fluid is equal to the heat transfer tothe cold fluid. 3 Changes in the kinetic and potential energies of fluid streams are negligible. 4 There isno fouling. 5 Fluid properties are constant.
Properties The specific heats of air and combustion gases are given to be 1005 and 1100 J/kg.C,respectively.
Analysis The rate of heat transfer is
kW103=
C)95CC)(180kJ/kg.kg/s)(1.11.1(
)]([ gas.
=
= outinp TTCmQ
The mass flow rate of air is
( ..m
PV
RT= =
=(95 kPa)(0.8 m / s)
kPa. m / kg. K) K kg / s
3
30 287 293
0904
Then the outlet temperature of the air becomes
C133=
+=+=
=
C)J/kg.kg/s)(1005904.0(
W10103C20
)(
3
,,
,,
pincoutc
incoutcp
Cm
QTT
TTCmQ
13-38
Air95 kPa20C
0.8 m3/s
Exhaust gases
1.1 kg/s95C
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Chap 15Heat Exchangers
13-56 Water is heated by hot oil in a 2-shell passes and 12-tube passes heat exchanger. The heat transfersurface area on the tube side is to be determined.
Assumptions1 Steady operating conditions exist. 2 The heat exchanger is well-insulated so that heat lossto the surroundings is negligible and thus heat transfer from the hot fluid is equal to the heat transfer tothe cold fluid. 3 Changes in the kinetic and potential energies of fluid streams are negligible. 4 There isno fouling. 5 Fluid properties are constant.
Properties The specific heats of water and oil are given to be 4.18 and 2.3 kJ/kg.C, respectively.
Analysis The rate of heat transfer in this heat exchanger is
[ ( )] ( .Q mC T T p out in= = water kg / s)(4.18 kJ / kg. C)(70 C C) = 940.5 kW4 5 20
The outlet temperature of the hot water is determined from
C129C)kJ/kg.kg/s)(2.310(
kW5.940C170)]([ oil =
===
pinoutoutinp
Cm
QTTTTCmQ
The logarithmic mean temperature difference for counter-flow arrangement and the correction factor F are
C109=C20C129
C100=C70C170
,,2
,,1
==
==
incouth
outcinh
TTT
TTT
C105)109/100ln(
109100
)/ln( 21
21, =
=
=
TT
TTT CFlm
0.1
2.1170129
7020
27.017020
170129
12
21
11
12
=
=
=
=
=
=
=
F
tt
TTR
tT
ttP
Then the heat transfer surface area on the tube side becomes
2
m15=
=
==
C)105(C)(1.0).kW/m6.0(
kW5.940
2,
,CFlm
sCFlms TUF
Q
ATFUAQ
13-39
Oil170C10 kg/s
Water20C
4.5 kg/s
70C
(12 tube passes)
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Chap 15Heat Exchangers
13-57 Water is heated by hot oil in a 2-shell passes and 12-tube passes heat exchanger. The heat transfersurface area on the tube side is to be determined.
Assumptions1 Steady operating conditions exist. 2 The heat exchanger is well-insulated so that heat lossto the surroundings is negligible and thus heat transfer from the hot fluid is equal to the heat transfer tothe cold fluid. 3 Changes in the kinetic and potential energies of fluid streams are negligible. 4 There isno fouling. 5 Fluid properties are constant.
Properties The specific heats of water and oil are given to be 4.18 and 2.3 kJ/kg.C, respectively.
Analysis The rate of heat transfer in this heat exchanger is
[ ( )] (Q mC T T p out in= = water kg / s)(4.18 kJ / kg. C)(70 C C) = 418 kW2 20
The outlet temperature of the oil is determined from
C8.151C)kJ/kg.kg/s)(2.310(
kW418C170)]([ oil =
===
pinoutoutinp
Cm
QTTTTCmQ
The logarithmic mean temperature difference for counter-flow arrangement and the correction factor F are
T T T
T T T
h in c out
h out c in
1
2
170 70
1518 20
= =
= =
, ,
, , .
C C = 100 C
C C = 131.8 C
T
T T
T Tlm CF,
ln( / )
.
ln( / . ).=
=
= 1 2
1 2
100 1318
100 1318115 2 C
}
0.1
7.21708.151
7020
12.017020
1708.151
12
21
11
12
=
=
=
=
=
=
=
F
tt
TTR
tT
ttP
Then the heat transfer surface area on the tube side becomes
2m6.05=
=
==C)2.115(C)(1.0).kW/m6.0(
kW418
2,, CFlmiiCFlmii TFU
QATFAUQ
13-40
Oil
170C10 kg/s
Water20C2 kg/s
70C
(12 tube passes)
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Chap 15Heat Exchangers
13-58 Ethyl alcohol is heated by water in a 2-shell passes and 8-tube passes heat exchanger. The heattransfer surface area of the heat exchanger is to be determined.
Assumptions1 Steady operating conditions exist. 2 The heat exchanger is well-insulated so that heat lossto the surroundings is negligible and thus heat transfer from the hot fluid is equal to the heat transfer tothe cold fluid. 3 Changes in the kinetic and potential energies of fluid streams are negligible. 4 There isno fouling. 5 Fluid properties are constant.
Properties The specific heats of water and ethyl alcohol are given to be 4.19 and 2.67 kJ/kg.C,respectively.
Analysis The rate of heat transfer in this heat exchanger is
kW252.3=C)25CC)(70kJ/kg.kg/s)(2.671.2()]([ alcoholethyl == inoutp TTCmQ
The logarithmic mean temperature difference for counter-flow arrangement and the correction factor F are
T T T
T T T
h in c out
h out c in
1
2
95 70
45 25
= =
= =
, ,
, ,
C C = 25 C
C C = 20 C
T
T T
T Tlm CF,
ln( / ) ln( / ).=
=
= 1 2
1 2
25 20
25 2022 4 C
77.0
9.09545
7025
7.09525
9545
12
21
11
12
=
=
=
=
=
=
=
F
tt
TTR
tT
ttP
Then the heat transfer surface area on the tube side becomes
2m15.4=
=
==C)4.22(C)(0.77).kW/m950.0(
kW3.2522
,
,
CFlmi
iCFlmiiTFU
QATFAUQ
13-41
Water90C
EthylAlcohol
25C2.1 kg/s
70C
(8 tube passes)
45C
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Chap 15Heat Exchangers
13-59 Water is heated by ethylene glycol in a 2-shell passes and 12-tube passes heat exchanger. The rateof heat transfer and the heat transfer surface area on the tube side are to be determined.
Assumptions1 Steady operating conditions exist. 2 The heat exchanger is well-insulated so that heat lossto the surroundings is negligible and thus heat transfer from the hot fluid is equal to the heat transfer tothe cold fluid. 3 Changes in the kinetic and potential energies of fluid streams are negligible. 4 There isno fouling. 5 Fluid properties are constant.
Properties The specific heats of water and ethylene glycol are given to be 4.18 and 2.68 kJ/kg.C,respectively.
Analysis The rate of heat transfer in this heat exchanger is :
kW160.5=C)22CC)(70kJ/kg.kg/s)(4.188.0()]([ water == inoutp TTCmQ
The logarithmic mean temperature difference for counter-flow arrangement and the correction factor F are
T T T
T T T
h in c out
h out c in
1
2
110 70
60 22
= =
= =
, ,
, ,
C C = 40 C
C C = 38 C
T
T T
T Tlm CF,
ln( / ) ln( / )=
=
= 1 2
1 2
40 38
40 3839 C
94.0
96.011060
7022
57.011022
11060
12
21
11
12
=
=
=
=
=
=
=
F
tt
TTR
tT
ttP
Then the heat transfer surface area on the tube side becomes
2m15.6=
=
==C)39(C)(0.94).kW/m28.0(
kW5.1602
,
,
CFlmi
iCFlmiiTFU
QATFAUQ
13-42
Ethylene110C
Water22C
0.8 kg/s
70C
(12 tube passes)
60C
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Chap 15Heat Exchangers
0.25 0.65 1.05 1.45 1.85 2.25
50
10 0
15 0
20 0
25 0
30 0
35 0
40 0
45 0
5
10
15
20
25
30
35
40
45
mw[kg/s]
Q
[kW]
A
m2
heat
area
13-44
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Chap 15Heat Exchangers
13-61E Steam is condensed by cooling water in a condenser. The rate of heat transfer, the rate ofcondensation of steam, and the mass flow rate of cold water are to be determined.
Assumptions1 Steady operating conditions exist. 2 The heat exchanger is well-insulated so that heat lossto the surroundings is negligible and thus heat transfer from the hot fluid is equal to the heat transfer tothe cold fluid. 3 Changes in the kinetic and potential energies of fluid streams are negligible. 4 There isno fouling. 5 Fluid properties are constant. 6 The thermal resistance of the inner tube is negligible sincethe tube is thin-walled and highly conductive.
Properties We take specific heat of water are given to be1.0 Btu/lbm.F. The heat of condensation of steam at 90Fis 1043 Btu/lbm.
Analysis (a) The log mean temperature difference isdetermined from
T T T
T T T
h in c out
h out c in
1
2
90 73
90 60
= =
= =
, ,
, ,
F F = 17 F
F F = 30 F
T
T T
T Tlm CF,
ln( / ) ln( / ).=
=
= 1 2
1 2
17 30
17 3022 9 F
The heat transfer surface area is
2ft7.392ft)ft)(548/3(5088 === DLnAs
and
Btu/h105.396 6=== F)9.22)(ftF)(392.7.Btu/h.ft600( 22lms TUAQ
(b) The rate of condensation of the steam is
lbm/s1.44=lbm/h5173=
===Btu/lbm1043
Btu/h10396.5)(
6
fgsteamsteamfg
h
QmhmQ
(c) Then the mass flow rate of cold water becomes
lbm/s115lbm/h104.15 5 ==
=
=
=
F]60FF)(73Btu/lbm.(1.0
Btu/h10396.5
)(
)]([
6
watercold
watercold
inoutp
inoutp
TTC
Qm
TTCmQ
13-45
Steam90F20 lbm/s
60F
Water
73F
90F
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Chap 15Heat Exchangers
13-62"!PROBLEM 13-62E"
"GIVEN"N_pass=8N_tube=50"T_steam=90 [F], parameter to be varied"h_fg_steam=1043 "[Btu/lbm]"
T_w_in=60 "[F]"T_w_out=73 "[F]"C_p_w=1.0 "[Btu/lbm-F]"D=3/4*1/12 "[ft]"L=5 "[ft]"U=600 "[Btu/h-ft^2-F]"
"ANALYSIS""(a)"DELTAT_1=T_steam-T_w_outDELTAT_2=T_steam-T_w_inDELTAT_lm=(DELTAT_1-DELTAT_2)/ln(DELTAT_1/DELTAT_2)A=N_pass*N_tube*pi*D*L
Q_dot=U*A*DELTAT_lm*Convert(Btu/h, Btu/s)"(b)"Q_dot=m_dot_steam*h_fg_steam"(c)"Q_dot=m_dot_w*C_p_w*(T_w_out-T_w_in)
Tsteam [F] Q [Btu/s] msteam[lbm/s] mw [lbm/s]
80 810.5 0.7771 62.34
82 951.9 0.9127 73.23
84 1091 1.046 83.89
86 1228 1.177 94.42
88 1363 1.307 104.990 1498 1.436 115.2
92 1632 1.565 125.694 1766 1.693 135.8
96 1899 1.821 146.1
98 2032 1.948 156.3
100 2165 2.076 166.5
102 2297 2.203 176.7
104 2430 2.329 186.9
106 2562 2.456 197.1
108 2694 2.583 207.2110 2826 2.709 217.4
112 2958 2.836 227.5
114 3089 2.962 237.6
116 3221 3.088 247.8
118 3353 3.214 257.9
120 3484 3.341 268
13-46
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Chap 15Heat Exchangers
80 85 90 95 100 105 110 115 120
50 0
1000
1500
2000
2500
3000
3500
0. 5
1
1. 5
2
2. 5
3
3. 5
Tsteam
[F]
Q
[Btu/s]
msteam
[lbm/s]
heat
msteam
80 85 90 95 100 105 110 115 12050
95
14 0
18 5
23 0
27 5
Tsteam[F ]
mw
[lbm/s]
13-47
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Chap 15Heat Exchangers
13-63 Glycerin is heated by hot water in a 1-shell pass and 13-tube passes heat exchanger. The mass flowrate of glycerin and the overall heat transfer coefficient of the heat exchanger are to be determined.
Assumptions1 Steady operating conditions exist. 2 The heat exchanger is well-insulated so that heat lossto the surroundings is negligible and thus heat transfer from the hot fluid is equal to the heat transfer tothe cold fluid. 3 Changes in the kinetic and potential energies of fluid streams are negligible. 4 There isno fouling. 5 Fluid properties are constant.
Properties The specific heats of water and glycerin are given to be 4.18 and 2.48 kJ/kg.C, respectively.
Analysis The rate of heat transfer in this heat exchanger is
[ ( )] (5Q mC T T p in out= = water kg / s)(4.18 kJ / kg. C)(100 C C) = 940.5 kW55
The mass flow rate of the glycerin is determined from
kg/s9.5=
=
=
=
C]15CC)[(55kJ/kg.(2.48
kJ/s5.940
)(
)]([
glycerin
glycerin
inoutp
inoutp
TTC
Qm
TTCmQ
The logarithmic mean temperature difference for counter-flow arrangement and the correction factor F are
T T T
T T T
h in c out
h out c in
1
2
100 55
55 15= = = =
, ,
, ,
C C = 45 C
C C = 40 C
T
T T
T Tlm CF,
ln( / ) ln( / ).=
=
= 1 2
1 2
45 40
45 4042 5 C
77.0
89.010055
5515
53.010015
10055
12
21
11
12
=
=
=
=
=
=
=
F
tt
TTR
tT
ttP
The heat transfer surface area is
2m0.94=m)m)(2015.0(10 == DLnAs
Then the overall heat transfer coefficient of the heat exchanger is determined to be
C.kW/m30.6 2 =
=
==C)5.42)(77.0)(m94.0(
kW5.9402
,,
CFlmsCFlms
TFA
QUTFUAQ
13-48
Glycerin15C
100C
Hot Water5 kg/s
55C
55C
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Chap 15Heat Exchangers
13-64 Isobutane is condensed by cooling air in the condenser of a power plant. The mass flow rate of airand the overall heat transfer coefficient are to be determined.
Assumptions1 Steady operating conditions exist. 2 The heat exchanger is well-insulated so that heat lossto the surroundings is negligible and thus heat transfer from the hot fluid is equal to the heat transfer tothe cold fluid. 3 Changes in the kinetic and potential energies of fluid streams are negligible. 4 There isno fouling. 5 Fluid properties are constant.
Properties The heat of vaporization of isobutane at 75C is given to be hfg = 255.7 kJ/kg and specific heatof air is given to be Cp = 1005 J/kg.C.
Analysis First, the rate of heat transfer is determined from
kW39.690)kJ/kg7.255)(kg/s7.2()( isobutane === fghmQ
The mass flow rate of air is determined from
kg/s98.14=
C)21CC)(28kJ/kg.(1.005
kJ/s39.690
)(
)]([
inoutair
airinout
=
=
=
TTC
Qm
TTCmQ
p
p
The temperature differences between the isobutane andthe air at the two ends of the condenser are
C47=C28C75
C54=C21C75
inc,outh,2
outc,inh,1
==
==
TTT
TTT
and
C4.50)47/54ln(
4754
)/ln( 21
21lm =
=
=
TT
TTT
Then the overall heat transfer coefficient is determined from
C.W/m571 2 == =C)4.50)(m(24W390,690 2lm UUTUAQ s
13-49
Isobutane
75C2.7 kg/s
Air21C
Air28C
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Chap 15Heat Exchangers
13-65 Water is evaporated by hot exhaust gases in an evaporator. The rate of heat transfer, the exittemperature of the exhaust gases, and the rate of evaporation of water are to be determined.
Assumptions1 Steady operating conditions exist. 2 The heat exchanger is well-insulated so that heat lossto the surroundings is negligible and thus heat transfer from the hot fluid is equal to the heat transfer tothe cold fluid. 3 Changes in the kinetic and potential energies of fluid streams are negligible. 4 There isno fouling. 5 Fluid properties are constant.
Properties The heat of vaporization of water at 200C is given to be hfg = 1941 kJ/kg and specific heat ofexhaust gases is given to be Cp = 1051 J/kg.C.
Analysis The temperature differences between the waterand the exhaust gases at the two ends of the evaporator are
C)200(
C350=C200C550
outh,inc,outh,2
outc,inh,1
==
==
TTTT
TTT
and
[ ])200/(350ln)200(350
)/ln( outh,
outh,
21
21lm
=
=
T
T
TT
TTT
Then the rate of heat transfer can be expressed as
[ ])200/(350ln)200(350
)m5.0)(C.kW/m780.1(outh,
outh,22lm
==
T
TTUAQ s
(Eq. 1)
The rate of heat transfer can also be expressed as in the following forms
)CC)(550kJ/kg.51kg/s)(1.025.0()]([ outh,gasesexhaustouth,inh, TTTCmQ p ==
(Eq. 2)
)kJ/kg1941()( waterwater mhmQ fg == (Eq. 3)
We have three equations with three unknowns. Using an equation solver such as EES, the unknowns aredetermined to be
Q
T
m
=
=
=
88.85 kW
211.8 C
0.0458 kg/ s
h,out
water
13-50
Water200C
550F
Exhaustgases
Th,out
200C
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Chap 15Heat Exchangers
13-66 "!PROBLEM 13-66"
"GIVEN""T_exhaust_in=550 [C], parameter to be varied"C_p_exhaust=1.051 "[kJ/kg-C]"m_dot_exhaust=0.25 "[kg/s]"
T_w=200 "[C]"
h_fg_w=1941 "[kJ/kg]"A=0.5 "[m^2]"U=1.780 "[kW/m^2-C]"
"ANALYSIS"DELTAT_1=T_exhaust_in-T_wDELTAT_2=T_exhaust_out-T_wDELTAT_lm=(DELTAT_1-DELTAT_2)/ln(DELTAT_1/DELTAT_2)Q_dot=U*A*DELTAT_lmQ_dot=m_dot_exhaust*C_p_exhaust*(T_exhaust_in-T_exhaust_out)Q_dot=m_dot_w*h_fg_w
Texhaust,in [C] Q [kW] Texhaust,out [C] mw [kg/s]
300 25.39 203.4 0.01308
320 30.46 204.1 0.0157
340 35.54 204.7 0.01831
360 40.62 205.4 0.02093
380 45.7 206.1 0.02354
400 50.77 206.8 0.02616420 55.85 207.4 0.02877
440 60.93 208.1 0.03139
460 66.01 208.8 0.03401
480 71.08 209.5 0.03662
500 76.16 210.1 0.03924
520 81.24 210.8 0.04185540 86.32 211.5 0.04447
560 91.39 212.2 0.04709580 96.47 212.8 0.0497
600 101.5 213.5 0.05232
13-51
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Chap 15Heat Exchangers
300 350 400 450 500 550 600
20
30
40
50
60
70
80
90
10 0
11 0
20 2
20 4
20 6
20 8
21 0
21 2
21 4
Texhaust,in
[C ]
Q
[kW]
T
C
heat
temperature
300 350 400 450 500 550 600
0.01
0.015
0.02
0.025
0.03
0.035
0.04
0.045
0.05
0.055
Texhaust,in
[C]
mw
[kg/s]
13-52
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Chap 15Heat Exchangers
13-67 The waste dyeing water is to be used to preheat fresh water. The outlet temperatures of each fluidand the mass flow rate are to be determined.
Assumptions1 Steady operating conditions exist. 2 The heat exchanger is well-insulated so that heat lossto the surroundings is negligible and thus heat transfer from the hot fluid is equal to the heat transfer tothe cold fluid. 3 Changes in the kinetic and potential energies of fluid streams are negligible. 4 There isno fouling. 5 Fluid properties are constant.
Properties The specific heats of waste dyeing water and the fresh water are given to be Cp = 4295 J/kg.Cand Cp = 4180 J/kg.C, respectively.
Analysis The temperature differences between the dyeing waterand the fresh water at the two ends of the heat exchanger are
15
75
outh,inc,outh,2
outc,outc,inh,1
==
==
TTTT
TTTT
and
[ ])15/()75(ln)15()75(
)/ln( outh,outc,
outh,outc,
21
21lm
=
=
TT
TT
TT
TTT
Then the rate of heat transfer can be expressed as
[ ])15/()75(ln)15()75(
)m65.1)(C.kW/m625.0(kW35outh,outc,
outh,outc,22
lm
=
=
TT
TT
TUAQ s
(Eq. 1)
The rate of heat transfer can also be expressed as
)CC)(75kJ/kg.(4.295kW35)]([ outh,waterdyeingouth,inh, TmTTCmQ p ==
(Eq. 2)
C)15C)(kJ/kg.(4.18kW35)]([ outc,waterdyeingouth,inh, == TmTTCmQ p
(Eq. 3)
We have three equations with three unknowns. Using an equation solver such as EES, the unknowns are
determined to be
T
T
m
c,out
h,out
=
=
=
41.4 C
49.3 C
0.317 kg/ s
13-53
Freshwater15C
Dyeingwater
75C
Tc,out
Th,out