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HW #4 /Tutorial # 4
WRF Chapter 18; WWWR Chapter 19
ID Chapter 6
• Tutorial # 4
• WWWR #19.1,19.4, WRF#18.10.
• ID # 6.33. 6.37.
• To be discussed during the week 8-12 Feb., 2021.
• By either volunteer or class list.
• Homework # 4 (Self practice)
• WRF#18.1, 18.3 ID # 6.35, 6.36, 6.39
# Correction
• Question 19.19
1/ 2 1/ 4 1/ 4
1/ 2 1/ 4 1/ 4
3.94Pr (Pr 0.954)
0.508Pr (Pr 0.954) ;
x
x x x x
Grx
kNu Gr h Nu
x
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Convective Heat Transfer
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Fundamental Considerations In
Convective Heat Transfer
• Two main classifications of convective heat
transfer
• These have to do with the driving force causing
fluid to flow
Natural or free convection
Fluid motion results from heat transfer
Fluid heated/ cooled -> density change/ buoyancy effect
->
natural circulation in which affected fluid moves of its own
accord past the solid surface
- fluid it replaces is similarly affected by the energy transfer
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process is repeated
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Forced convection
Fluid circulation is produced by external agency (fan or
pump)
Analytical Methods
(a) Dimensional Analysis
(b) Exact Analysis of the Boundary Layer
(c) Approximate Integral Analysis
(d) Analogy between Energy and Momentum Exchange
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Significant Parameters In
Convective Heat Transfer
A. Both have same dimensions L2/t; thus their ratio must be
dimensionless
B. This ratio, that of molecular diffusivity of momentum to
the
molecular diffusivity of heat, is designed the Prandtl
number
Pr =n
a
mcpk
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Prandtl number
•observed to be a combination of fluid properties;
•thus Pr itself may be thought of as a property.
•Primarily a function of temperature
s
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A ratio of conductive thermal resistance to the convective
thermal
resistance of the fluid
Nusselt numberNu hL
k
Where the thermal conductivity of the fluid as opposed to that
of the
solid, which was the case in the evaluation of the Biot
modulus.
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Dimensional Analysis of
Convective Energy Transfer
Forced Convection
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Dimensional
Analysis for
Forced Convection
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Natural Convection
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Dimensional
Analysis for
Natural Convection
Courtesy Contribution
by ChBE Year
Representative, 2004.
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Exact Analysis of the Laminar
Boundary Layer
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A logical consequence of this situation is that the
hydrodynamic
and thermal boundary layers are of equal thickness.
It is significant that the Prandtl numbers for most gases
are
sufficiently closed to unity that the hydrodynamic and
thermal
boundaries are of similar extent.
See detailed derivation
below
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Detailed Derivation
Eq.(19-19) WWWR page 295
0
0
2
Re0.664
2
y
S
x
S
T T
y y
T T f
y
T TX
Re2
x
y
x
From Eq.(19-18)
Re
0.332x
ST TX
1
20.332
ReS xT TX
(19-19)
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Approximate Integral Analysis of
the Thermal Boundary Layer
An approximate method for analysis of the thermal boundary
layer
employs the integral analysis used by von Kármán for the
hydrodynamic boundary layer.
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Consider the control volume designated by the dashed lines,
applying to flow parallel to a flat surface with no pressure
gradient, having width Dx, a height equal to the thickness of
the
thermal boundary layer
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0.323
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Energy and Momentum Transfer
Analogies
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The Colburn analogy expression is
St Pr 2/3 = Cf2
(19-37)
8)
9)
s
oner
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Example 1
Water at 50o
F enters a heat-exchanger tube having an inside diameter of 1 in
and a length of 10
ft. The water flows at 20 gal/min. For a constant wall
temperature of 210o
F estimate the
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Film temperature = (water mean bulk temperature + pipe wall
temperature)/2
Mean bulk temperature of water = (inlet + outlet)/2
=(90+210)/2 = 150 = (50+130)/2
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Second iteration is required since if |TL – 130| >
3o
F?