3. convective heat transfer 3.1 fundamentals€¦ · pr (7) ⎟ ⎠ ⎞ ⎜ ⎝ ⎛ ... local heat...
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3. Convective Heat Transfer 3.1 Fundamentals
( ∞−⋅α= TTq w& ) (1)
T
fluid~δλ
α
∫ ⋅α⋅=αL
0x dx
L1 (2)
λ⋅α
=xNu x
x (3)
λ⋅α
=LNu (4)
ν⋅
= ∞ xuRex (5)
ν⋅
= ∞ LuRe (6)
λ⋅ρ⋅ν
=ν
= pca
Pr (7)
⎟⎠⎞
⎜⎝⎛⋅⋅⋅=
LLifPrRecNu ba (8)
3.2 Forced Flow over Products
5crit 103Re ⋅≈ (9)
Form NUSSELTfunction validity range
plate laminar
33,0PrRe664,0Nu ⋅⋅= 33,0
xx PrRe332,0Nu ⋅⋅=
510Re <
5,0Pr >
(10)
(11)
plate turbulent
43,08,0 PrRe037,0Nu ⋅⋅= 43,08,0
xx PrRe030,0Nu ⋅⋅= 75 103Re10 ⋅<<
5,0Pr >
(12)
(13)
cylinder lam.-turb.
67,0d
33,0dd PrRe0012,0PrRe48,035,0Nu ⋅⋅+⋅⋅+=
und 5
d2 104Re10 ⋅<<−
5,0Pr >
(14)
sphere lam.-turb.
33,0dd PrRe6,02Nu ⋅⋅+= und 6
d 10Re <
5,0Pr >
(15)
Tab. 3.1: NUSSELTfunctions of forced convection over products
λα dNud⋅
= , ν
duRed⋅
= ∞ (16)
UA4Leg ⋅= (17)
Re → 0 stationary heat conduction
( ) ( )∞
∞
−−
λ⋅π⋅=→ TT
d1
d120ReQ wmin
&
( )∞−⋅⋅π⋅α= TTdQ w
2min&
2dNumin =λ⋅α
=
material properties for mean boundary temperature
( )∞+⋅= TT21T wm
Gases
n
000 TT⎟⎟⎠
⎞⎜⎜⎝
⎛≈
λλ
≈μμ ,
1
00 TT
−
⎟⎟⎠
⎞⎜⎜⎝
⎛=
ρρ ,
1n
000 TT
aa
+
⎟⎟⎠
⎞⎜⎜⎝
⎛≈
νν
≈
1n7.0 ≤≤
Pr independent on temperature
laminar flow 5.0RekNu ⋅=
( ) 5.01nn
00
05.0
5.0
5.0
TT
Lwk
Lwk
⋅+−
⎟⎟⎠
⎞⎜⎜⎝
⎛⋅
νλ⋅⎟
⎠⎞
⎜⎝⎛⋅=
νλ
⋅⎟⎠⎞
⎜⎝⎛⋅=α
( )00T/T~α for n = 1
( ) 15.0
0T/T~ −α for n = 0.7 turbulent flow 8.0RekNu ⋅=
8.0)1n(n
08.0 T
T~⋅+−
⎟⎟⎠
⎞⎜⎜⎝
⎛=
νλ
α
( ) 6.00T/T~ −α for n = 1
( ) 66.0
0T/T~ −α for n = 0.7 Liquids
λρ ,c , nearly independ on temperature, ν strongly decreases with temperature,
25.0
w
42.08.0
PrPrPrRekNu ⎟⎟
⎠
⎞⎜⎜⎝
⎛⋅⋅⋅=
3.3 Forced Flow in Tubes and Ducts Local heat transfer
( )[ ]xTTq wxx −⋅α=& T T
w
T(x=0)
0 L x
T(x)
Fig. 3.6: Axial temperature profile in a duct Mean heat transfer
( ) ( )( )( ) w
wln
TLTT0xTln
0xTLTTq
−−==−
⋅α=Δ⋅α=&
α mean heat transfer coefficient
λα dNud⋅
= (18)
νduRe ⋅
= (19)
Form NUSSELTfunction validity range laminar
3d
33d L
dPrRe61,166,3Nu ⋅⋅⋅+=
33,0dd Pr
LdRe664,0Nu ⋅⋅⋅=
2300Red <
Ld1,0 <
(20)
(21)
turbulent 48,08,0dd PrRe0235,0Nu ⋅⋅≈
( )⎥⎥⎦
⎤
⎢⎢⎣
⎡⎟⎠⎞
⎜⎝⎛+⋅⋅−⋅=
67,04,08,0
d Ld1Pr100Re0214,0Nu
( )⎥⎥⎦
⎤
⎢⎢⎣
⎡⎟⎠⎞
⎜⎝⎛+⋅⋅−⋅=
67,04,087,0
d Ld1Pr280Re012,0Nu
6d
4 10Re10 << Pr6,0 <
5,1Pr5,0 <<
500Pr5,1 <<
(22)
(23)
(24)
Tab. 3-2: NUSSELTfunctions of forced convection in ducts
materials properties for ( ))0x(T)L(T21Tm =+⋅=
for liquids ( ) ( )( )
11.0
w
mm TPr
TPrTNuNu ⎟⎟⎠
⎞⎜⎜⎝
⎛⋅=
(25)
UA4dh ⋅= (26)
a b
b
do
di
Tube
ddh =
rectangular duct
baba2dh +⋅⋅
=
Flat duct
b2dh ⋅= Annular duct
ioh ddd −=
d
Tab. 3.3: Hydraulic diameter of ducts
3.4 Impinging flows
λ⋅α
=dNu ,
ν⋅
=duRe
d diameter of nozzle u nozzle outlet velocity νλ, for gas temperature in nozzle
stagnation point
5.0st Re07.0Nu ⋅= 0 < r/d < 1
average for 5.3d/r1 <≤
65.0Re07.0Nu ⋅= 3.5 Packed Beds
void fraction V
VV S−=ψ
V volume of apparatus VS volume of solids d mean particle diameter
...d1
VV
d1
VV
1d
2S
2
1S
1 +⋅+⋅=
λ⋅α
=dNu ,
ν⋅
=dwRe
Superficial velocity
AVw&
=
V& volumne flow of gas A cross section area of empty apparatus
( ) ( )[ ]ψ−⋅+⋅⋅+= 15.11 PrRe6.02Nu 4.05.0
3.6 Natural convection
( )2
w3
T TTLgGrν
β ∞−⋅⋅= (27)
PrGrRa ⋅= (28)
910PrGr <⋅ laminar 910PrGr >⋅ turbulent
Shape Form NUSSELTfunction validity range vertical plate
laminar turbulent
25,0
L2
L Pr952,0GrPr677,0Nu ⎟⎟
⎠
⎞⎜⎜⎝
⎛+
⋅⋅=
( ) 33,0LL PrGr13,0Nu ⋅⋅=
9
L 10PrGr <⋅
PrGr10 L9 ⋅<
(29)
(30)horizontal cylinder
lam.-turb. ( ) 25,0dd PrGr40,0Nu ⋅⋅= 10
d2 10PrGr10 <⋅<
100Pr7,0 << (31)
horizontal plate
laminar turbulent
( ) 25,0LL PrGr54,0Nu ⋅⋅=
( ) 33,0LL PrGr14,0Nu ⋅⋅=
7L
5 102PrGr10 ⋅<⋅< 10
L7 103PrGr102 ⋅<⋅<⋅
(32)
(33)
Tab. 3.4: NUSSELTfunctions of free convection Forced and natural convection
Gr21ReRe 2
forcedeq ⋅+= (34)
Nu = f (Reeq) for forced convection
Fig. 3.1: Velocity boundary layer developing over a flat plate
Fig. 3.2: Thermal boundary layer
Fig. 3.3: Local heat transfer coefficient along a flat plate
Fig. 3.4a: Flow over a circular cylinder
Fig. 3-4b: Local Nusselt number (Nu0) for a flow normal to a circular cylinder
Fig. 3.4c: Local heat transfer coefficient across a cylinder
Fig. 3.5: Development of the boundary layer in a tube
Fig. 3.6: Axial temperature profile in a duct
wr δ1
δ2
Prallzone
Wandstrahl
unbeeinflusster Strahl
r
w D
Düse
Übergangsbereich
z
h
d
Fig. 3.7: Boundary layer and velocity profile for impingement flow
wD= 81 m/s
200
300
400
500
600
700
0 1 2 3r / d
αr
in W
/(m² K
)
4
h/d = 1h/d = 2h/d = 4h/d = 6h/d = 10
Fig. 3.8: Distribution of local heat transfer coefficient for several nozzle distances h/d
Re=91500
100
200
300
400
0 1 2 3 4 5r/d
Nu
h/d = 1h/d = 2h/d = 4h/d = 6h/d = 10
Fig. 3.9: Distribution of average Nusselt-number for several nozzle distances h/d
h/d=2Nu=k*Rem*Pr0,42
0,0
0,2
0,4
0,6
0,8
1,0
0 1 2 3 4 5 6r/d
m
gemitteltörtlich
Fig. 3.10a: Local Re-exponent of Nu-function for local and averaged heat transfer
at a nozzle distance of h/d=2
h/d=2Nu=k*Rem*Pr0,42
0,0
0,1
1,0
0 1 2 3 4 5 6r/d
k
gemitteltörtlich
Fig. 3.10b: Local values of factor k of Nu-function for local and averaged heat
transfer at a nozzle distance of h/d=2
1
10
100
1000
10 100 1000 10000 100000 1000000Re
Nu 0
/Pr0,
42
1 Bizzak 2 Brahma3 den Ouden 4 Garimella5 Hoogendoorn 6 Huang7 Hrycak 8 Ma9 Popiel 10 Sun11 Tawfek 12 Adler13 exakte Lösung
h/d = 2
1
2
3
45
6
7
8
9
10
11 12
13
8
11
Fig. 3.11: Comparison of several results in literature for heat transfer at stagnation Point
Fig. 3.12 –3.18: Heat transfer in an array of nozzles Fig. 3.19: Pached bed
Fig. 3.20: Development of the boundary layer on a heated vertical plate, left: interferogram of istoherms
Fig. 3-30: Approximate values of dynamic viscosity for various liquids and gases