04.conduction part2
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1D, Steady State Heat Transfer with HeatGeneration
Fins and Extended Surfaces
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Chapter 3c : One-dimensional, Steady state conduction (with
thermal energy generation) (Section 3.5Textbook)
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3.1 Implications of energy generation Involve a local source of thermal energy due to conversion from another
form of energy in a conducting medium.
The source may be uniformlydistributed, as in the conversion fromelectrical to thermal energy
or it may be non-uniformlydistributed, as in the absorption of radiationpassing through a semi-transparent medium
Generation affects the temperature distribution in the medium and causesthe heat rate to varywith location, thereby precluding inclusion of themedium in a thermal circuit. (Cannot use electrical analogy!)
Eq. (1.11c)
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Chapter 3 : One-dimensional, Steady state conduction
(without thermal generation)
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*Recall previous case: a steady state plane wall with constant k &
no heat generation Assuming steady-state conditions and nointernal heat generation (i.e. q = 0), thenthe 1-D heat conduction equation reducesto:
For constant kandA
.
This means:Heat flux (qx) is independent of xHeat rate (qx) is independent of x
Boundary conditions: T(0)= Ts,1T(L)= Ts,2
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Chapter 3 : One-dimensional, Steady state conduction (with
thermal generation)
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3.2 A plane wall with internal heat generation
Assuming steady-state conditions and internal heatgeneration (i.e. q = 0), from the 1-D heat conductionequation:
.
*Consider a plane wall between two fluids of different temperatures
- general heat equation reduces to:
Boundary conditions: T(-L)= Ts,1T(L)= Ts,2
This means:
Heat flux (qx) is not independent of x
Heat rate (qx) is not independent of x
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Chapter 3 : One-dimensional, Steady state conduction (with
thermal generation)
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, for constant kandA
2ndorder DE: Integrate twice to getT(x)
at x = -L, T(-L) = Ts,1 , at x = L, T(L) = Ts,2
for boundary conditions:
Thisgives,
and
Substituting the values
for C1and C2into eq. T(x)Tem erature distribution e uation
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Chapter 3 : One-dimensional, Steady state conduction (with
thermal generation)
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Then, apply Fouriers Law to get heat transfer(BUT qxis now dependent on x)
Heat flux (W/m2):
Heat rate (W):
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Chapter 3 : One-dimensional, Steady state conduction (with
thermal generation)
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What happens if both surfaces are maintained at the same temperature,
Ts,1 = Ts,2 = Ts
This case is called A case of symmetricsurface conditions or one surface wasinsulated.
Therefore, the temperature distribution eq. reducesto :
The max temperature exists at the mid plane:
Rearranging the temp distribution
*this means, at the planeof symmetry the temp
gradient is ZERO.
Eq. (3.42)
Eq. (3.43)
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Chapter 3 : One-dimensional, Steady state conduction (with
thermal generation)
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Symmetric surface conditions or one surface was
insulated. Because the temp gradient at the centerline is zero,there is ZEROheat flow at that point and it behaveslike an insulated wall.
The insulated wall has the same parabolictemperature profile as half the un-insulated full wall
*recall the previous chapter: Boundaryconditions (Table 2.2)
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Chapter 3 : One-dimensional, Steady state conduction (with
thermal generation)
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Symmetric surface conditions or one surface was
insulated. Because the temp gradient at the centerline is zero,there is ZEROheat flow at that point and it behaveslike an insulated wall.
The insulated wall has the same parabolic temperatureprofile as half the un-insulated full wall
Why does the magnitude of the temperaturegradient increase with increasingx ?
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Chapter 3 : One-dimensional, Steady state conduction (with
thermal generation)
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Symmetric surface conditions or one surface was
insulated. Because the temp gradient at the centerline is zero,there is ZEROheat flow at that point and it behaveslike an insulated wall.
The insulated wall has the same parabolic temperatureprofile as half the un-insulated full wall
Why does the magnitude of the temperaturegradient increase with increasingx ?
- due to increase in temperature difference
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Chapter 3 : One-dimensional, Steady state conduction (with
thermal generation)
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Symmetric surface conditions or one surface was
insulated. Because the temp gradient at the centerline is zero,there is ZEROheat flow at that point and it behaveslike an insulated wall.
The insulated wall has the same parabolic temperatureprofile as half the un-insulated full wall
Why does the magnitude of the temperaturegradient increase with increasingx ?
How do we determine Ts?- due to increase in temperature difference
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Chapter 3 : One-dimensional, Steady state conduction (with
thermal generation)
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Symmetric surface conditions or one surface was
insulated. Because the temp gradient at the centerline is zero,there is ZEROheat flow at that point and it behaveslike an insulated wall.
The insulated wall has the same parabolic temperatureprofile as half the un-insulated full wall
Why does the magnitude of the temperaturegradient increase with increasingx ?
How do we determine Ts?
How do we determine the heat rate at x = L ?
(no energy in, neglecting radiation,energy balance becomes)
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Chapter 3 : One-dimensional, Steady state conduction (with
thermal generation)
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Symmetric surface conditions or one surface was
insulated. Because the temp gradient at the centerline is zero,there is ZEROheat flow at that point and it behaveslike an insulated wall.
The insulated wall has the same parabolic temperatureprofile as half the un-insulated full wall
Why does the magnitude of the temperaturegradient increase with increasingx ?
How do we determine Ts?
How do we determine the heat rate at x = L ?Using the surface energy balance, energy
generated must equal to energy outflow
(Neglecting radiation, energy balancebecomes)
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Chapter 3c : One-dimensional, Steady state conduction (with
thermal energy generation)
Referring to the Example 3.7 in textbook
a) Parabolic in material Ab) Zero slope at insulated
boundaryc) Linear slope in material
Bd) Slope change kB/kA=2 at
interfacee) Large gradients near the
surface
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Chapter 3c : One-dimensional, Steady state conduction (with
thermal energy generation)
Example (3.74):
Consider a plane composite wall that is composed of three materials(materials A,B and C are arranged left to right) of thermal conductivitieskA=0.24 W/mK, kB=0.13 W/mK and kC=0.50 W/mK. The thickness of thethree sections of the wall are LA= 20mm, LB= 13mm and LC= 20mm. Acontact resistance of Rt,c=10
-2m2K/W exists at the interface between
materials A and B, as well as interface between B and C. The left face of thecomposite wall is insulated, while the right face is exposed to convectiveconditions characterised by h=10 W/m2K, T=20C. For case 1, thermalenergy is generated within material A at rate 5000 W/m3. For case 2,thermal energy is generated within material C at rate 5000 W/m3.
a) Determine the maximum temperature within the composite wall under
steady state conditions for Case 1b) Sketch the steady state temperature distribution on T-x coordinates for
Case 1
c) Find the maximum temperature within the composite wall and sketchthe steady state temperature distribution for Case 2
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Chapter 3c : One-dimensional, Steady state conduction (with
thermal energy generation)
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3.3 Radial systems (cylinder and sphere)
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Chapter 3c : One-dimensional, Steady state conduction (with
thermal energy generation)
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Temp distribution for solid cylinder:
Eq. (3.53)or
(C.23)
Temp distribution for hollow cylinder:
Eq. (C.2)
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Chapter 3c : One-dimensional, Steady state conduction (with
thermal energy generation)
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Temp distribution for solid sphere:
Temp distribution for spherical wall:
Eq. (C.24)
Eq. (C.3)
*A summary of temp distributions, heat fluxes & heat rates for all cases is provided inA endix C.
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Chapter 3c : One-dimensional, Steady state conduction (with
thermal energy generation)
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Problem 3.92:
A long cylindrical rod of diameter 200 mm with thermal conductivity of0.5 W/mK experiences uniform volumetric heat generation of 24,000W/m3. The rod is encapsulated by a circular sleeve having an outerdiameter of 400 mm and a thermal conductivity of 4 W/mK. The outersurface of the sleeve is exposed to cross flow of air at 27C with a
convection coefficient of 25 W/m2
K.a) Find the temperature at the interface between the rod and sleeve and
on the outer surface.
b) What is the temperature at the center of the rod ?
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Chapter 3c : One-dimensional, Steady state conduction (with
thermal energy generation)
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Problem 3.95:
Radioactive wastes (krw=20 W/mK) are stored in a spherical stainless steel(kss=15 W/mK) container of inner and outer radii equal to ri=0.5 m andro=0.6 m. Heat is generated volumetrically within the wastes at a uniformrate of 105 W/m3, and the outer surfaces of the container is exposed to awater flow for which h=1000 W/m2K and T=20C
a) Evaluate the steady-state outer surface temperature, Ts,o
b) Evaluate the steady-state inner surface temperature, Ts,i
c) Obtain an expression for the temperature distribution, T(r), in theradioactive wastes. Express your result in term of ri, Ts,i, krw and q.Evaluate the temperature at r = 0
.
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Chapter 3d : Heat transfer from extended surface
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3.1 Introduction
Extended surface (also known as fins) is commonly used todepict an important special case involving combination ofconduction-convection system.
Consider a strut that connects two walls at differenttemperatures and across which there is fluid f low
(Section 3.6 Textbook)
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Chapter 3d : Heat transfer from extended surface
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3.1 Introduction
Extended surface (also known as fins) is commonly used todepict an important special case involving combination ofconduction-convection system.
Why its important ?
Basically, there are 2 ways of increasing heat transfer
i) Increase fluid velocity to reduce temperature (manylimitation)
ii) Increase surface area
*Particularly beneficial when h
is small i.e. gas and natural
convection
The most frequent application to enhance heat transferbetween a solid joining and an adjoining fluid
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Chapter 3d : Heat transfer from extended surface
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Applications ?
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Chapter 3d : Heat transfer from extended surface
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Typical fin configurations (after simplification)
Straight fins of (a) uniform;(b) non-uniform cross sections;(c) annular fin;(d) pin fin of non-uniform cross section
Figure 3.14
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Chapter 3d : Heat transfer from extended surface
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3.2 A general conduction analysis for an extended surfaces
Applying the conservation of energy
Using,
Then, the heat equation becomes:
General form of the energy equation for an extendedsurface
Eq. (3.61)
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Chapter 3d : Heat transfer from extended surface
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3.3 The Fin Equation
Assuming 1-D case, steady state conduction in an extendedsurface, constant k, uniform cross sectional area, negligiblegeneration and radiation.
Cross section area, Acis constantand fin surface area, As= Px, this
mean dAc/dx = 0 and dAs/dx = P
General equation becomes:
Eq. (3.62)
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Chapter 3d : Heat transfer from extended surface
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To simplify the equation, we define an excess temperature ( thereduced temperature) as:
The previous equation becomes:
where,
* malso known as fin parameter
Eq. (3.63)
Eq. (3.65)
P is the fin perimeter
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Chapter 3d : Heat transfer from extended surface
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By referring to Table 3.4 : at
different case of heat transferanalysis
Temperature distribution, /b
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Chapter 3d : Heat transfer from extended surface
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Chapter 3d : Heat transfer from extended surface
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Example (3.120):
A brass rod 100 mm long and 5 mm in diameter extendshorizontally from a casting at 200C. The rod is in an airenvironment with T= 20C and h = 30 W/m
2K. What is thetemperature of the rod at 25, 50 and 100 mm from the castingbody ?
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Chapter 3d : Heat transfer from extended surface
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3.4 Fin performance parameters (single fin case)
Fin efficiency max. potential heat transfer rate
Fin effectiveness ratio of heat transfer with and without fin
Fin resistance
Eq. (3.81)
Eq. (3.83) and (3.92)
Eq. (3.86)
Expressions for f are provided in Table 3.5 for common geometries, for example atriangular fin: - Surface area of the fin
- Profile area
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(cont.)
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Chapter 3d : Heat transfer from extended surface
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Example (3.123):
A straight fin fabricated from 2024 aluminium alloy (k = 185 W/mK) has abase thickness of t = 3 mm and a length of L = 15 mm. Its basetemperature is Tb= 100 C, and it is exposed to a fluid for which T=20C and h = 50 W/m2K. For the foregoing conditions and a fin of unitwidth, compare the fin heat rate, efficiency and volume for
i) Rectangular profileii) Triangular profile
iii) Parabolic profile
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Chapter 3d : Heat transfer from extended surface
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3.5 Fin arrays
Representative arrays of
a) Rectangular fins
b) Annular fins
Eq. (3.99)
Eq. (3.100)
Eq. (3.102)
Eq. (3.103)
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Chapter 3d : Heat transfer from extended surface
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Previous equations are for fins that are produced by machining or
casting which as an integral part of the wall ( as in Fig. 3.20 & Fig3.21a)
Eq. (3.102)
Eq. (3.103)
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Chapter 3d : Heat transfer from extended surface
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However, some fins are manufactured separately and attached by
a metallurgical or adhesive joint or press fit. Such cases need toconsider contact resistance (as in Fig 3.21b)
Eq.(3.105a)Eq.(3.105b)
Eq. (3.104)
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