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Chapter 6Empirical and Practical Relations for
Forced-Convection Heat Transfer
6-1 Introduction
6-2 Empirical relations for pipe and tube flow
1. Mean flow velocity
A
VudA
Au
A
1
2. Laminar and turbulent flow
Re<2300 laminar flow
2300<Re<104 transient region
Re>104 turbulent flow
3. Bulk temperature Energy-averaged fluid temperature or mixing cup
For constant physical properties
A p
A p
bdAuc
tdAuct
A
A
Af utdA
VudA
tdAut
1
)( 21 bbp ttcm )(2 bw ttrdxhd av)( bw tthA
The calculation of Tb needs the distribution of u.
The practical method is to measure Tb after mixing.
4. Dittus-Boelter expression for fully developed turbulent flow in smooth tubes
nPrReNu 8.0023.0
3.0
4.0n
For heating of the fluid
For cooling of the fluid wb
wb
tt
tt
Characteristic length, inside diameter
Reference temperature, )(2
1 "'bbb ttt
Applicability 54 102.1Re10 1006.0 Pr
60/ dLFully developed
CttCttCtt owb
owb
owb 10 oil ,30~20 water ,50 gas
Moderate temperature difference
Example : Water is heated from 25.3℃ to 34.6 ℃ in a tube with a diameter of d=20mm and a length of 5m, the velocity is u=2m/s. Calculate the convection heat transfer coefficient.
( 1 )审题内容,确定类型。( 2 )定性温度,查取物性。( 3 )计算准则,选用公式。( 4 )代入计算,考虑修正。
Solution ( 1 ) Forced convection in tube
( 2 ) Reference temperature C30
2
6.343.25
2
1 o"'
bbb ttT
Physical properties: k=0.618W/(m.K), v=0.80510-6m2/s,
Pr=5.42, ρ=995.7kg/m3, cp=4.17 kJ/kg( 3 ) Calculate dimensionless group and choose equation
446
101097.410805.0
02.02Re
v
ud
nNu PrRe023.0 8.0 For heating of the fluid n=0.4
(4) Calculation and correction
5.25842.51097.4023.0 4.08.04 Nu
W/(m.K)798702.0
618.05.258
d
Nukh
Check whether the parameters are in the range of application
6025002.0
5
d
L
W
ttcd
uq bbp
242853.256.3410174.44
02.027.995
4
32
'"2
bw tthAq
C68.39502.07895
2428530 o
DLh
qt
hA
qtt bbb
C2068.93068.39 o bw tt
5. Qualitative analysis and correction(1)length
Laminar flow x , , h Turbulent flow x , , h as turbulent growth h goes up and then down
Entrance length of laminar L/d=0.05RePrFor turbulent flow, the influence of entrance is negligible when L/d>60
If L/d<60 the effect of entrance must be considered. The method is
0hh L 7.0/1 LdL
liquidsgases
,
,
t
t
Take liquid as an example wb tt No heat transfer, velocity profile of fully developed flow is shown in curve1.
If
If bwbw
bwbw
tt
tt
,
, curve2
curve3
( 2 ) Temperature
nNu PrRe023.0 8.0
The value of n is different because physical properties
b>a Φ 1≠Φ 2
btb atb
atw btw 1 2
Φ 1
Φ 2
Flow rate is constant. T , , , du/dr , dT/dr Temperature has effect on heat transfer through laminar sublayer,
heating q 1> q 2, or h1>h2.
There is a difference between heating and cooling.
If T is small, the difference is not large, it is exact enough to taken into
account by n , that is Prn=(v/a)n 。 If T is large, the following method is used.
For liquids, T only has influence on , the correction is
nwbT /
For gases, T has effects on , , k, cP , the correction is
nwbT tt /
0hh TL
25.0
11.0n
For heating of the fluid
For cooling of the fluid
3
03 . 1 1
77 . 1 1
Rd
Rd
R gases
liquids
Solution: Except for L=0.5m, other conditions are the same with the last example. We have got h=7987 W/(m2K). L/d=0.5/0.02=25<60
11.15.0
02.011
7.07.0
l
dl
W24285'" bbbp ttcq
( 3 ) bend The secondary flow enhances the heat transfer.
0hh RtL
)KW/(m8866798711.1 20 hh L
R curvature radius
Example : Water is heated from 25.3℃ to 34.6 ℃ in a tube with a diameter of d=20mm and a length of 0.5m, the velocity is u=2m/s. Calculate the convection heat transfer coefficient.
C30C2.875.002.08866
24285 oo
hA
tt bw
Temperature difference correction
6
o
105.801
C30
b
bt
6
o
104.243
C2.117
w
wt
C5.1065.002.010107
2428530 o1
wt
Repeat this process until tw does not change
)KW/(m10107798711.114.1 20 hh TL
wTw th
)KW/(m10004 2h
14.14.243
5.881/
11.011.0
wbT
6. Convection in ducts characteristic dimension: hydraulic (equivalent) diameter DH.
P
ADH
4 A—the cross-sectional area of the flow
P — the wetted perimeter
Annular tube 12
12
21
22 dd
dd
ddDH
Rectangular tube ba
ab
ba
abDH
2
2
4
1
4
221
221
d
ss
ddD
dPdssA
H
This method suitable for many cases There are some notable exceptions where the method does not work
Tube bank
7. Heat transfer in laminar tube flowInformation of fully developed laminar in ducts by Shah and Londu
n
The characteristic of heat transfer in laminar duct flow
Nuq=const>NuTw=const
Nu is independent of Re
Generally the h of ducts with different cross sections, the same DH
are different
Generally In practice, the flow in entrance is often laminar
The length of entrance is Gz=RePrd/L=0.05 Graetz number
The results is in fig. 6-5
7. Entrance effects in Turbulent flow
We have considered it by L
6-3 Flow across cylinders and spheres
Separation point at 00
yy
u
Drag force2
2
uACF DD
A -- frontal area of the body is the product of diameter and length
1. Correlation for heat transfer
At Re of the order of 10, no flow separation
At Re=70800 ~ 101300, laminar,φ↑,δ↑, h↓.
At φ=82o, boundary layer separation causes
turbulent eddy motion in the separated flow,
φ↑ , h ↑ 。 At Re>1.5×105 the flow is turbulent. Two
minimum points of h are observed. The 1st
occurs at the point of transition from laminar to
turbulent, the 2nd occurs when the turbulent
boundary layer separates atφ=130-140o because
eddy motion.
Other correlations equation (6-19) ~ (6-24)
2. Choice of equations for cross flow over cylinders3. Noncircular cylinders
17)-(6 PrRe 3/1f
n
f
Ck
hdNu
The constant are given in Table 6-3
4. Spheres
Correlations equation (6-25) ~ (6-30)
Reference temperature (Tw+T∞)/2
Characteristic length d
The constant C and n are given in Table 6-2
17)-(6 PrRe 3/1f
n
f
Ck
hdNu
6-4 Flow across tube banksline-instaggered hh
10 or more rows of tubes in the direction of flow
Reference temperature
2/)( ttt wf
Characteristic length dRe is based on the umax
17)-(6 PrRe 3/1f
n
f
Ck
hdNu
t)arrangemen line-(in )]/([max dSSuu nn
For staggered area flow minimum is for )]/([max pnn SdSSuu
If not ])2/[(
)2/(2/122max dSS
Suu
pn
n
The constant C and n are given in Table 6-4
For fewer rows the ratio of h for N rows deep to
that for 10 rows is given in table 6-5
rows 10hh N
6-5 Liquid-metal heat transfer
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