chapter 6 empirical and practical relations for forced
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Chapter 6 Empirical and Practical Relations in forced convection in heat transfer.TRANSCRIPT
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Chapter 6 Empirical and Practical Relations for Forced-Convection Heat Transfer
Empirical relations for pipe and tube flow Turbulent flow in smooth tube: Dittus and Boelter
0.8
5
0.023Re Pr0.40.3
0.6 Pr 1002500 Re 1.25 10
nd dNu
for heating of the fluidn
for cooling of the fluid
=
⎧= ⎨⎩< <
< < ×
Gnielinske
0.8 0.4
4 6
0.0214(Re 100) Pr0.5 Pr 1.510 Re 5 10
dNu = −< <
< < ×
, or
0.87 0.4
6
0.012(Re 280) Pr1.5 Pr 5003000 Re 10
dNu = −< <
< <
To take into account the property variations Sieder and Tate
0.14
0.8 1/30.027 Re Prd dw
Nu μμ
⎛ ⎞= ⎜ ⎟
⎝ ⎠ for turbulent fully developed flow
More accurate relations, Petukhov
1/ 2 2/3
210
4 6
( / 8) Re Pr1.07 12.7( / 8) (Pr 1)
0.110.250 .
(1.82log Re 1.64)0.5 Pr 200 6%0.5 Pr 2000 10%10 Re 5 100.8 / 40
n
d bd
w
w b
w b
d
d
b w
fNuf
for T Tn for T T
const heat flux
faccuracy withinaccuracy within
μμ
μ μ
−
⎛ ⎞= ⎜ ⎟+ − ⎝ ⎠
>⎧⎪= >⎨⎪⎩
= −
< << <
< < ×< <
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For fully developed, laminar tube flow at const. wall temp. Hausen
2/3
0.0668( / ) Re Pr3.661 0.04[( / ) Re Pr]
dd
d
d LNud L
= ++
Laminar tube flow Sieder and Tate :
0.141/31/31.86(Re Pr)
Re Pr 10
d dw
d
dNuL
dL
μμ
⎛ ⎞⎛ ⎞= ⎜ ⎟⎜ ⎟⎝ ⎠ ⎝ ⎠
>
For rough tube,
2/3
2
Pr8
2
b f
m
fSt
Pf friction coefficientu L
dρ
=
Δ= =
In the entrance region, Nusselt
0.055
0.8 1/30.036Re Pr 10 400d dd LNu forL d
⎛ ⎞= < <⎜ ⎟⎝ ⎠
Turbulent flow
Or
Fig 6-5 & 6-6. Re Pr dGz Graetz numberx
= =
Noncircular pipe, Hydraulic diameter
4
::
HAD
PA cross section area of the flowP wetted perimeter
=
Flow across cylinder Hilpert for gases & Knudsen and Katz for liquids
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1/3Re Prnf dfNu C=
Redf C N 0.4-4 0.989 0.330 4-40 0.911 0.385
40-4000 0.683 0.466 4000-40,000 0.193 0.618
40,000-400,000 0.0266 0.805