solution heat excercise
DESCRIPTION
The solution to one of the biggest questions of modern heating machine design, namely how to determine the dimensions of the shell and tubesTRANSCRIPT
-
Solution exercise 6
Cold side (tap water) hot side (condensate)
cm& = 30000 kg/h = 8.333 kg/s hm& = 50000 kg/h = 13.889 kg/s Tc,in = 17 C Th,in = 67 C Tc,out = 40 C cp,h = 4184 J/kgK vc 1.5 m/s ph = 1.2 bar
Geometry
DS = 0.38735 m Rfo = 0.000176 mK/W do = 0.019 m Rfi = 0.000176 mK/W di = 0.016 m = 60 W/mK Lmax = 5 m B = 0.25 m Parallel layout with PT = 0.024 m Nt = 124/2 = 62 Np = 2
Solution Average temperature cold side: Tc = 5.282
4017=
+C
Tap water (28.5C) (in the tubes)
cp,c = 4182.72 J/kg K c = 612.296.10-3 W/mK c = 995.80 kg/m c = 842.338.10-6 kg/ms Prc = 5.7738
( ) 801656,,
== incoutccpcTTcmQ &&
W
( ) 2.53,,,
== outhouthinhhph TTTcmQ && C
Average temperature hot side: Th = 1.602672.53
=
+C
Condensate (1.2 bar)
cp,h = 4184 J/kgK h = 652.977.10-3 W/mK h = 982.72 kg/m h = 478.742.10-6 kg/ms Prh = 3.078
First estimate of the average wall temperature: Tw = 3.4425.281.60
=
+C
Viscosity at the wall: w = 625.37.10-6 kg/ms
-
Calculation of the convection coeficient at the inside Hydraulic diameter: inner diameter di
6713.0
42
=
=
ic
t
c
c
d
Nm
vpi
&
m/s < 1.5 m/s OK!
12698Re ==c
cicdi
dv
> 2300
Flow in a tube: Turbulent: Gnielinski
f = ( ) 0073683.028.3)ln(Re58.1 2 = di
Nu = ( )
82.9111Pr
27.121
Pr1000Re2 3
2
32
=
+
+
Ld
f
fi
(when neglecting correction for di/L)
Large temperature difference between the fluids: correction
Nucorr = 363188.9411.0
=
==
i
c
ii
w
c hdhNu
W/mK
Calculation of the convection coefficient for the shell side (Kern)
Equivalent diameter: 019599.04
42
2
=
=
o
o
T
e d
dP
Dpi
pi
m
C = PT do = 0.005 m
Area the fluid flows through: 02017.0==T
s
s PBCD
A m
Mass flux 6.688==s
hs A
mG&
kg/ms
28190Re ==h
se
s
GD
4705PrRe36.014.0
3155.0
=
=
u
w
hhs
h
eu hDh
W/mK
-
uuu
fui
u
i
fi
ii AhAR
ldd
AR
AhUA1
2
ln11
++
++= pi
with l = Ltube . Np (for 1 conduction path)
Ai = pi.di.l
Au = pi.du.l
Hence u
fuui
u
i
u
fii
u
i hRd
dd
dd
Rdd
hU1
2
ln11
++
++= pipi
U = 1050.65 W/mK
Q = U.A.F.LMTD
Logaritmic mean temperature difference: ( ) ( ) 38.314067172.53ln
4067172.53,
=
= tsLMT C
F = 0.95 (1 shell pass and 2 tube passes, P= 0.46, R = 0.6) (fig 2.4)
m 59.25=
=
LMTFUQA
A = 46.3= tubetubetpo LLNNdpi m, rounded 3.5 m.
The amount of baffles can now be calculated: Nb = Ltube/B 1 = 13 baffles
Pressure loss
pi?
fcorr = 0068396.025.0
=
w
cf
44812
142
=
+= pcc
i
tubecorri N
v
dLfp
Pa
po? ( )( ) 253884.0Reln19.0576.0 == sef
( ) 175932
114.0
2
=
+=
w
heh
sbso
D
DNGfp
Pa