me421lec10p1
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ME421
Heat Exchanger andSteam Generator Design
Lecture Notes 10 Part 1
Condensation and Evaporation (Boiling)(Condensers and Evaporators)
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Introduction• Condensation: when saturated vapor contacts a lower-
temperature medium
• Evaporation: when saturated liquid contacts a higher
temperature medium; if this medium is a surface - boiling
• Condenser: a two-phase flow HEX where the heat is
generated from the conversion of vapor into liquid, and the
heat generated is removed from the system by a coolant
• Evaporator: a two-phase flow HEX where the heat is
removed by the conversion of liquid into vapor
• Especially in the refrigeration and air-conditioning industry,evaporators and condensers are widely used
• Other examples are power condensers, boilers, steam
generators, etc
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Condensation• Film condensation: if the liquid (condensate) wets the
surface
• Droplet condensation: if the liquid does not wet the surface
• Dropwise condensation results in higher HT coefficientsthan filmwise condensation, but is very difficult to sustain
in practice; thus condensers are designed to operate in
filmwise mode.
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Dropwise
condensation
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Film Condensation on a Single Horizontal Tube
Laminar Film Condensation
• Local HT coefficient around the tube (Fig. 7.1) as a function of
circumferential angle is
δ is the film thickness and kl is the liquid phase thermal
conductivity
• Average HT coefficient given by Nusselt theory (Eq. 7.2)
subscript l (or f) is for liquid, g (or v) is for gas, ilg is enthalpy of
vaporization (hfg), Tsat is the saturation temperature, Tw is the
wall temperature
• Simple example (7.1) in book
)(
k)(h lφδ=φ
25.0
lwsatl
3lggll
l
m
k)TT(
dgi)(728.0
k
dh
⎥⎥⎦
⎤
⎢⎢⎣
⎡
−µ
ρ−ρρ=
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Film Condensation on a Single Horizontal Tube
Forced Convection Film Condensation
• When vapor moves at a high velocity
– surface shear stress between the vapor and the condensate
– vapor separationbecome important considerations.
• Several correlations are available, see Section 7.3.2, and
the example within• The most conservative approach that satisfies the extremes
of gravity-controlled and shear-controlled condensation is
proposed by Butterworth (Eq. 7.7)
( )( ) 2/12/1
2/1m F47.911416.0
eR~Nu
++=
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Film Condensation on a Single Horizontal Tube
• In the previous correlation
two-phase Reynolds number:l
dueR~g
ν=
wsat
l2g
lglTTT,
Tku
idgF −=∆
∆
µ=
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Film Condensation in Tube Bundles
continuouslaminar sheet
staggeredconfiguration discretedroplets large vapor velocities
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Film Condensation in Tube Bundles
Effect of Condensate Inundation
• In the absence of vapor velocity:
– condensate falls by gravity onto lower tubes in the bundle
– condensate thickens around the lower tubes – condensation heat transfer decreases, because the thick condensate
layer acts as an insulator
• Film condensation on a vertical in-line column of N horizontal
tubes using Nusselt idealized theory (Fig. 7.3(a)) gives the
following average coefficient compared to the coefficient for
the first (top) tube
h1 given by Eq. 7.2
4/1
1
N,mN
h
h −=
Fil C d ti i T b B dl
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Film Condensation in Tube BundlesEffect of Condensate Inundation (continued)
• The local coefficient for the Nth
tube by the Nusselt theory
• Kern's relationship is less conservative
• Eissenberg relation for a staggered bundle (side-drainage
model, Fig. 7.3(b))
• For design purposes, Kern relation is recommended
4/34/3
1
N )1N(Nh
h−−=
6/56/5
1
N6/1
1
N,m)1N(N
h
handN
h
h−−== −
4/1
1
N N42.060.0hh −+=
Fil C d i i T b B dl
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Film Condensation in Tube Bundles
Effect of Condensate Inundation (continued)
• Example 7.3 compares previous relations, but usesEissenberg for in-line and others for staggered, too
• Staggered arrangement yields a higher HT coefficient
• To prevent inundation, tubes are slightly inclined, which
results in an increase of up to 25% in the HT coefficient
Film Condensation in Tube Bundles
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Film Condensation in Tube BundlesEffect of Vapor Shear
• For downward and horizontal flow, Fujii et al proposed:
• Mean local steam velocity is ug= g/ρg Am, where Am = wNtL isthe mean flow area in terms of the number of unit cells Nt and
the mean flow width per cell w
600F03.0for F96.0eR
~Nu 5/1
2/1m <<=
m&
L
2
TL
p4/dppw π−=
Film Condensation in Tube Bundles
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Film Condensation in Tube BundlesCombined Effects of Inundation and Vapor Shear
• Butterworth correlation for the local HT coefficient in the Nth
tube row
where hsh is given by Eq. 7.6 as
• McNaught correlation treats shell-side condensation as two-
phase forced convection:
where hG is
and hsh is given as
( ) [ ]6/56/52/1
2/14L
4sh
2shN )1N(Nhh25.0h5.0h −−×⎥
⎦
⎤⎢⎣
⎡ ++=
2/1lsh eR
~
d
k59.0h =
( )2/12
G
2
shN hhh +=6/56/5
LG )1N(Nhh −−=
Ltt
sh hX
26.1h ⎟⎟ ⎠
⎜⎜⎝
=78.01 ⎞⎛
Film Condensation in Tube Bundles
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Film Condensation in Tube BundlesCombined Effects of Inundation and Vapor Shear (continued)
• Xtt is the Lockhart-Martinelli parameter
and hL is the liquid phase forced convection heat transfer
coefficient across a bank of tubes, select from Chapter 3 or
elsewhere.
• McNaught correlation is valid for
p/d = 1.25
10≤
G≤
70 kg/m2
s0.025 ≤ x ≤ 0.8 (x: vapor quality)
0.008 ≤ Xtt ≤ 0.8
• See example 7.4
1.0
g
l
5.0
l
g
9.0
ttx
x1X ⎟
⎟ ⎠
⎞⎜⎜⎝
⎛
µµ
⎟⎟ ⎠
⎞⎜⎜⎝
⎛
ρ
ρ⎟ ⎠
⎞⎜⎝
⎛ −=
Condensation inside Tubes (Horizontal)
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Condensation inside Tubes (Horizontal)• Different flow patterns exist during condensation inside tubes
due to the balance between vapor shear and gravitational
forces
• These flow patterns change the HT coefficients, so local
values must be determined
• To predict flow patterns, define dimensionless mass velocity
– jg* > 1.5, Xtt < 1.0 : mist and annular
– jg* < 0.5, Xtt < 1.0 : wavy and stratified
– jg* < 0.5, Xtt > 1.5 : slug
– jg* > 1.5, Xtt < 1.5 : bubble
• When jg* is low, gravitational forces dominate and stratification
of the condensate will occur
• When jg* is high, interfacial shear forces are large andcondensate flow is annular
( )[ ] 2/1
glg
*
gdg
Gx j
ρ−ρρ=
Condensation inside Tubes (Horizontal)
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Condensation inside Tubes (Horizontal)
• For laminar flow, stratification occurs and heat transfer
coefficients are too low because heat transfer is negligible inthe stratified region. See p.245 in book for a Nusselt-based
correlation.
Condensation inside Tubes (Horizontal)
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Condensation inside Tubes (Horizontal)
• In general, turbulent flow models are used.
• In the single-phase region, for example when there issuperheating or subcooling, use proper correlations from
literature (Chapter 3).
• There are numerous correlations for use in the two-phaseregion with different kinds of fluids (refrigerants especially).
• Traviss correlation (Eq. 7.25) is for R-12 and R-22, and
makes use of the liquid Reynolds number (Eq. 7.26) and twoparameters F1 and F2 (Eqs. 7.27-7.30).
• A more recent correlation developed by Cavallini and Zecchin
(Eq. 7.31) is valid for R-11, R-12-, R-21, R-22, R-113, and R-114.
Condensation inside Tubes (Horizontal)
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Condensation inside Tubes (Horizontal)• The Shah correlation for two-phase (TP) HT coefficient is
valid for a larger group of fluids including water
where
where pr = psat/pcr is the reduced pressure and the liquid-only
HT coefficient hL can be found by Dittus-Boelter equation:
• Shah correlation can be integrated to evaluate the mean HT
coefficient in the whole condensing region, but for a linear variation of quality over a 100% to 0% range,
• See Section 7.5.1 for vertical tube condensation
⎟ ⎠
⎞⎜⎝
⎛ +=
95.0LTPZ
8.31hh
4.0r
8.0
px
x1
Z ⎟ ⎠
⎞⎜⎝
⎛ −=
d
kPr d)x1(G023.0h l
4.0l
8.0
lL ⎟⎟
⎠
⎞⎜⎜⎝
⎛
µ−
=
⎟
⎟
⎠
⎞
⎜
⎜
⎝
⎛ +=
38.0r
Lm,TP
p
09.255.0hh