mel242-27 (1)
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xcscscsTRANSCRIPT
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Thermal Development of Internal Flows
P M V SubbaraoAssociate Professor
Mechanical Engineering DepartmentIIT Delhi
Concept for Precise Design ……
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Development of Flow
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q’’
Ti
Ts(x)
Ti Ts(x)q’’
Hot Wall & Cold Fluid
Cold Wall & Hot Fluid
Temperature Profile in Internal Flow
T(x)
T(x)
• The local heat transfer rate is: xTTAhq mwallxx
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We also often define a Nusselt number as:
fluid
mwall
x
fluid
xD k
DxTTA
q
kDhxNu )(
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Mean Velocity and Bulk Temperature
Two important parameters in internal forced convection are the mean flow velocity u and the bulk or mixed mean fluid temperature Tm(z).
The mass flow rate is defined as:
while the bulk or mixed mean temperature is defined as:
p
Acp
m Cm
TdAuC
xT c
)( cA
cc
m uTdAAu
xT 1)(
For Incompressible Flows:
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Mean Temperature (Tm)
• We characterise the fluid temperature by using the mean temperature of the fluid at a given cross-section.
• Heat addition to the fluid leads to increase in mean temperature and vice versa.
• For the existence of convection heat transfer, the mean temperature of the fluid should monotonically vary.
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First Law for A CV : SSSF
Tm,in Tm,exit
dx
qz
inmexitmmeanpz TTCmq ,,,
No work transfer, change in kinetic and potential energies are negligible
CVexitexitininCV WgzVhmgzVhmq
22
exitexitininCV hmhmq ~~
inexitz hhmq ~~
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THERMALLY FULLY DEVELOPED FLOW
• There should be heat transfer from wall to fluid or vice versa.
• Then What does fully developed flow signify in Thermal view?
0,,, inmexitmmeanpz TTCmq
0 xTTAhq mwallxz
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FULLY DEVELOPED CONDITIONS (THERMALLY)
(what does this signify?)
Use a dimensionless temperature difference to characterise the profile, i.e. use
)()(),()(
xTxTxrTxT
ms
s
This ratio is independent of x in the fully developed region, i.e.
0)()(),()(
,
tfdms
s
xTxTxrTxT
x
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0)()(),()(),()()()(
x
xTxTxrTxTx
xrTxTxTxT mss
sms
0)()(),()(),()()()(
x
xTxTxrTxTx
xrTxTxTxT mss
sms
0)()(),()(),()()()(
x
xTxxTxrTxT
xxrT
xxTxTxT ms
ss
ms
0),()()()()(),()(,)(
xrTxT
xxTxTxT
xxrTxTxrT
xxT
sm
msms
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Uniform Wall Heat flux : Fully Developed Region
tfd
mtfd dx
dTx
xrT,, ,
Temp. profile shape is unchanging.
)()(constant'' xTxThq msx
xxT
xxT ms
)()(
0),()()()()(),()(,)(
xrTxT
xxTxTxT
xxrTxTxrT
xxT
sm
msms
0),()()()()(),(
xrTxT
xxTxTxT
xxrT
msm
ms
0)()()(),(
xTxT
xxT
xxrT
msm
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dx
cmPh
TTTTd
pms
ms
Integrating from x=0 (Tm = T m,i) to x = L (Tm = Tm,o):
dx
cmPh
TTTTd L
pms
msT
T
om
im
0
,
,
Constant Surface Heat Flux : Heating of Fluid
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Temperature Profile in Fully Developed Region
Uniform Wall Temperature (UWT)
)(0 xdxdTs
tfdm
ms
stfd dx
dTTTTT
xT
,, )()(
axial temp. gradient is not independent of r and shape of temperature profile is changing.
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The shape of the temperature profile is changing, but the relative shape is unchanged (for UWT conditions).
Both the shape and the relative shape are independent of x for UWF conditions.
At the tube surface:
)( ][
but
)(
"
00"
00
xfTTk
q
rT
kyT
kq
xfTT
rT
TTTT
r
ms
s
rrys
ms
rrrr
ms
s
)(xfkh
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i.e. the Nusselt number is independent of x in the thermally fully developed region.
Assuming const. fluid properties:-
tfdxxxfh ,)(
This is the real significance of thermally fully developed
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Evolution of Macro Flow Parameters
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Thermal Considerations – Internal FlowT fluid Tsurface
a thermal boundary layer develops
The growth of th depends on whether the flow is laminar or turbulent
Extent of Thermal Entrance Region:
Laminar Flow: PrRe05.0 ,
D
x tfd
Turbulent Flow:
10 ,
D
x tfd
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Energy Balance : Heating or Cooling of fluid
• Rate of energy inflow
Tm Tm + dTm
dx
QmpTcm
• Rate of energy outflow mmp dTTcm
Rate of heatflow through wall:
ms TTdAhQ Conservation of energy:
mpmmpms TcmdTTcmTTdAhQ
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mpms dTcmTTdxPh
msp
m TTcmPh
dxdT
This expression is an extremely useful result, from which axialVariation of Tm may be determined.The solution to above equation depends on the surface thermal
condition.
Two special cases of interest are:
1. Constant surface heat flux.2. Constant surface temperature
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Constant Surface Heat flux heating or cooling
• For constant surface heat flux:
imomps TTcmLPqQ ,,''
For entire pipe:
For small control volume:
mps dTcmqdxPh ''
)(''
xfcm
Pqdx
dT
p
sm
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Integrating form x = 0
xcm
PqTxTp
simm
''
,)(
The mean temperature varies linearly with x along the tube.
mpms dTcmTTdxPh
For a small control volume:
dxdT
Phcm
TT mpms
The mean temperature variation depends on variation of h.
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dx
cmPh
TTTTd
pms
ms
Integrating from x=0 (Tm = T m,i) to x = L (Tm = Tm,o):
dx
cmPh
TTTTd L
pms
msT
T
om
im
0
,
,
Constant Surface Heat Flux : Heating of Fluid
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mpms dTcmTTdxPh
dxcmPh
TTdT
pms
m
dx
cmPh
TTTTd
pms
ms
Integrating from x=0 (Tm = T m,i) to x = L (Tm = Tm,o):
dx
cmPh
TTTTd L
pms
msT
T
om
im
0
,
,
For a small control volume:
Constant Surface Heat flux heating or cooling
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pims
oms
cmLPh
TTTT
,
,ln
p
surface
ims
oms
cmAh
TTTT
,
,ln
ims
oms
surface
p
TTTT
Acm
h,
,ln
h : Average Convective heat transfer coefficient.
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The above result illustrates the exponential behavior of the bulk fluid for constant wall temperature. It may also be written as:
to get the local variation in bulk temperature.It important to relate the wall temperature, the inlet and exit temperatures, and the heat transfer in one single expression.
p
surfaceavg
ims
oms
cmAh
TTTT
exp
,
,
p
avg
ims
ms
cmxPh
TTxTT
exp
,
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Constant Surface Heat flux heating or cooling
mT
sT
T
x
mT
sTT
x
is TT if is TT if
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To get this we write:
iopimsomspimomp TTcmTTTTcmTTcmQ
,,,,
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which is the Log Mean Temperature Difference.
The above expression requires knowledge of the exit temperature, which is only known if the heat transfer rate is known. An alternate equation can be derived which eliminates the outlet temperature.We Know
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Thermal Resistance:
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Dimensionless Parameters for Convection
Forced Convection Flow Inside a Circular Tube
All properties at fluid bulk mean temperature (arithmetic mean of inlet and outlet temperature).
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Internal Flow Heat Transfer
• Convection correlations– Laminar flow– Turbulent flow
• Other topics– Non-circular flow channels– Concentric tube annulus
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Convection correlations: laminar flow in circular tubes
• 1. The fully developed regionfrom the energy equation,we can obtain the exact solution. for constant surface heat fluid
36.4k
hDNuDCqs
66.3k
hDNuD
for constant surface temperature
Note: the thermal conductivity k should be evaluated at average Tm
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Convection correlations: laminar flow in circular tubes
• The entry region : for the constant surface temperature condition
3/2
PrReLD04.01
PrReLD0.0668
3.66
D
D
DNu
thermal entry length
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Convection correlations: laminar flow in circular tubesfor the combined entry length
14.03/1
/PrRe86.1
s
DD DL
Nu
2/)/Pr/(Re 14.03/1 sD DL
All fluid properties evaluated at the mean T
2/,, omimm TTT
CTs
700,16Pr48.0
75.9/0044.0 s
Valid for
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Thermally developing, hydrodynamically developed laminar flow (Re < 2300)
Constant wall temperature:
Constant wall heat flux:
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Simultaneously developing laminar flow (Re < 2300)
Constant wall temperature:
Constant wall heat flux:
which is valid over the range 0.7 < Pr < 7 or if Re Pr D/L < 33 also for Pr > 7.
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Convection correlations: turbulent flow in circular tubes
• A lot of empirical correlations are available.• For smooth tubes and fully developed flow.
heatingFor PrRe023.0 4.05/4DDNu
coolingfor PrRe023.0 3.05/4DDNu
)1(Pr)8/(7.121Pr)1000)(Re8/(3/22/1
ffNu D
d
•For rough tubes, coefficient increases with wall roughness. For fully developed flows
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Fully developed turbulent and transition flow (Re > 2300)
Constant wall Temperature:
Where
Constant wall temperature: For fluids with Pr > 0.7 correlation for constant wall heat flux can be used with negligible error.
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Effects of property variation with temperature
Liquids, laminar and turbulent flow:
Subscript w: at wall temperature, without subscript: at mean fluid temperature
Gases, laminar flow Nu = Nu0
Gases, turbulent flow
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Noncircular Tubes: CorrelationsFor noncircular cross-sections, define an effective diameter, known as the hydraulic diameter:
Use the correlations for circular cross-sections.
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Selecting the right correlation• Calculate Re and check the flow regime (laminar or turbulent)• Calculate hydrodynamic entrance length (xfd,h or Lhe) to see
whether the flow is hydrodynamically fully developed. (fully developed flow vs. developing)
• Calculate thermal entrance length (xfd,t or Lte) to determine whether the flow is thermally fully developed.
• We need to find average heat transfer coefficient to use in U calculation in place of hi or ho.
• Average Nusselt number can be obtained from an appropriate correlation.
• Nu = f(Re, Pr)• We need to determine some properties and plug them into the
correlation. • These properties are generally either evaluated at mean (bulk)
fluid temperature or at wall temperature. Each correlation should also specify this.
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Heat transfer enhancement
• Enhancement• Increase the convection coefficientIntroduce surface roughness to enhance turbulence. Induce swirl.• Increase the convection surface areaLongitudinal fins, spiral fins or ribs.
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Heat transfer enhancement
• Helically coiled tube• Without inducing turbulence or additional heat transfer
surface area.• Secondary flow