STEADY STATE HEAT CONDUCTION
Transcript of STEADY STATE HEAT CONDUCTION
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.1
2 STEADY STATE HEAT CONDUCTION
Course Contents
2.1 Introduction
2.2 Thermal resistance
2.3 Thermal conductivity of
material
2.4 General heat conduction
equation
2.5 Measurement of thermal
conductivity (Guarded hot
plate method)
2.6 Conduction through a plane
wall
2.7 Conduction through a
composite wall
2.8 Heat flow between surface and
surroundings: cooling and
heating of fluids
2.9 Conduction through a
cylindrical wall
2.10 Conduction through a
multilayer cylindrical wall
2.11 Conduction through a sphere
2.12 Critical thickness of insulation
2.13 Solved Numerical
2.14 References
2. Steady State Heat Conduction Heat Transfer (3151909)
Prepared By: Mehul K. Pujara Department of Mechanical Engineering Page 2.2 Darshan Institute of Engineering & Technology, Rajkot
2.1 Introduction
The rate of heat conduction in a specified direction is proportional to the
temperature gradient, which is the rate of change in temperature with distance in
that direction. One dimensional steady state heat conduction through homogenous
material is given by Fourier Law of heat conduction:
π = βππ΄ππ‘
ππ₯
π =π
π΄= βπ
ππ‘
ππ₯β β β β β β β (2.1)
Where,
π = heat flux, heat conducted per unit time per unit area, π π2β
Q = rate of heat flow, W
A = area perpendicular to the direction of heat flow, π2
dt = temperature difference between the two surfaces across which heat is
passing, Kelvin K or degree centigrade β
dx = thickness of material along the path of heat flow, m
The ratio ππ‘ ππ₯β represents the change in temperature per unit thickness, i.e. the
temperature gradient.
The negative sign indicates that the heat flow is in the direction of negative
temperature gradient, so heat transfer becomes positive.
The proportionality factor k is called the heat conductivity or thermal conductivity of
material through which heat is transfer.
The Fourier law is essentially based on the following assumptions:
1. Steady state heat conduction, i.e. temperature at fixed point does not change
with respect to time.
2. One dimensional heat flow.
3. Material is homogenous and isotropic, i.e. thermal conductivity has a constant
value in all the directions.
4. Constant temperature gradient and a linear temperature profile.
5. No internal heat generation.
The Fourier law helps to define thermal conductivity of the material.
π = βππ΄ππ‘
ππ₯
Assuming ππ₯ = 1π; π΄ = π2 and ππ‘ = 1β, we obtain
π = π
Hence thermal conductivity may be defined as the amount of heat conducted per
unit time across unit area and through unit thickness, when a temperature
difference of unit degree is maintained across the bounding surface.
Unit of thermal conductivity is given by:
π = βπ
π΄
ππ₯
ππ‘
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β΄ [π] =π
π2
π
πππ=
π
π β πππ
2.2 Thermal Resistance
In systems, which involve flow of fluid, heat and electricity, the flow quantity is
directly proportional to the driving force and inversely proportional to the flow
resistance.
In a hydraulic system, the pressure along the path is the driving potential and
roughness of the pipe is the flow resistance.
The current flow in a conductor is governed by the voltage potential and electrical
resistance of the material.
Likewise, temperature difference constitutes the driving force for heat conduction
through a medium.
Fig. 2.1 Concept of thermal resistance
From Fourierβs law
βπππ‘ ππππ€ π =π‘πππππππ‘π’ππ πππ‘πππ‘πππ (ππ‘)
π‘βπππππ πππ ππ π‘ππππ (ππ₯ ππ΄β )
Thermal resistance, π π‘ = (ππ₯ ππ΄β ), is expressed in the unit πππ πβ .
The reciprocal of thermal resistance is called thermal conductance and it represents
the amount of heat conducted through a solid wall of area A and thickness dx when
a temperature difference of unit degree is maintained across the bounding surfaces.
2.3 Thermal Conductivity of Materials
Thermal conductivity is a property of the material and it depends upon the material
structure, moisture content and density of the material, and operating conditions of
pressure and temperature.
Following remarks apply to the thermal conductivity and its variation for different
materials and under different conditions:
In material thermal conductivity is due to two effects: the lattice vibrational waves
and flow of free electrons.
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In metals the molecules are closely packed; molecular activity is rather small and so
thermal conductivity is mainly due to flow of free electrons.
In fluids, the free electron movement is negligibly small so conductivity mainly
depends upon the frequency of interactions between the lattice atoms.
Thermal conductivity is highest in the purest form of a metal. Alloying of metals and
presence of other impurities reduce the conductivity of the metal.
Mechanical forming (i.e. forging, drawing and bending) or heat treatment of metal
cause considerable variation in thermal conductivity. Conductivity of hardened steel
is lower than that of annealed steel.
At elevated temperatures, thermal vibration of the lattice becomes higher and that
retards the motion of free electrons. So, thermal conductivity of metal decreases
with increases of temperature except the aluminium and uranium.
Thermal conductivity of aluminium remains almost constant within the temperature
range of 130 β to 370 β.
For uranium, heat conduction depends mainly upon the vibrational movement of
atoms. With increase of temperature vibrational movement increase so, conductivity
also increase.
According to kinetic theory of, conductivity of gases is directly proportional to the
density of the gas, mean molecular speed and mean free path. With increase of
temperature molecular speed increases, so conductivity of gas increases.
Conductivity of gas is independent of pressure except in extreme cases as, for
example, when conditions approach that of a perfect vacuum.
Molecular conditions associated with the liquid state are more difficult to describe,
and physical mechanisms for explaining the thermal conductivity are not well
understood. The thermal conductivity of nonmetallic liquids generally decreases with
increasing temperature. The water, glycerine and engine oil are notable exceptions.
The thermal conductivity of liquids is usually insensitive to pressure except near the
critical point.
Thermal conductivity is only very weakly dependent on pressure for solids and for
liquids a well, and essentially dependent of pressure for gases at pressure near
standard atmospheric.
For most materials, the dependence of thermal conductivity on temperature is
almost linear.
Non-metallic solids do not conduct heat as efficiently as metals.
Thermal conductivity of pure copper is 385 W m β degβ and that of nickel
is 93W m β degβ .
Monel metal, an alloy of 30% nickel and 70% copper, has thermal
conductivity of only 24 W m β degβ .
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The ratio of the thermal and electrical conductivities is same for all metals at the
same temperature; and that the ratio is directly proportional to the absolute
temperature of the metal.
2.4 General Heat Conduction Equation
The objective of conduction analysis is two fold:
i To determine the temperature distribution within the body
ii To make calculation of heat transfer.
Fourier law of heat conduction is essentially valid for heat flow under uni-directional
and steady state conditions, but sometimes it is necessary to consider heat flow in
other direction as well.
So for heat transfer in multi-dimensional, it is necessary to develop general heat
conduction equation in rectangular, cylindrical and spherical coordinate systems.
2.4.1 Cartesian (Rectangular) Co-ordinates:-
Consider the flow of heat through an infinitesimal volume element oriented in a
three dimensional co-ordinate system as shown in figure 2.2. The sides dx, dy and dz
have been taken parallel to the x, y, and z axis respectively.
Fig. 2.2 Conduction analysis in cartesian co ordinates
The general heat conduction equation can be set up by applying Fourier equation in
each Cartesian direction, and then applying the energy conservation requirement.
If kx represents the thermal conductivity at the left face, then quantity of heat
flowing into the control volume through the face during time interval dΟ is given by:
Heat influx
ππ₯ = βππ₯(ππ¦ ππ§)ππ‘
ππ₯ ππ β β β β β β β (2.2)
During same time interval the heat flow out of the element will be,
Heat efflux
ππ₯+ππ₯ = ππ₯ +πππ₯
ππ₯ ππ₯ β β β β β β β (2.3)
2. Steady State Heat Conduction Heat Transfer (3151909)
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Heat accumulated within the control volume due to heat flow in the x-direction is
given by the difference between heat influx and heat efflux.
Thus the heat accumulation due to heat flow in x-direction is
πππ₯ = ππ₯ β ππ₯+ππ₯
= ππ₯ β [ππ₯ +πππ₯
ππ₯ ππ₯]
= βπππ₯
ππ₯ ππ₯
= βπ
ππ₯[βππ₯(ππ¦ ππ§)
ππ‘
ππ₯ ππ] ππ₯
=π
ππ₯[ππ₯
ππ‘
ππ₯ ] ππ₯ ππ¦ ππ§ ππ β β β β β β β (2.4)
Likewise the heat accumulation in the control volume due to heat flow along the y-
and z-directions will be:
πππ¦ =π
ππ¦[ππ¦
ππ‘
ππ¦ ] ππ₯ ππ¦ ππ§ ππ β β β β β β β (2.5)
πππ§ =π
ππ§[ππ§
ππ‘
ππ§ ] ππ₯ ππ¦ ππ§ ππ β β β β β β β (2.6)
Total heat accumulated due to heat transfer is given by
[π
ππ₯(ππ₯
ππ‘
ππ₯) +
π
ππ¦(ππ¦
ππ‘
ππ¦) +
π
ππ§(ππ§
ππ‘
ππ§)] ππ₯ ππ¦ ππ§ ππ β β β β β β β (2.7)
There may be heat source inside the control volume. If qg is the heat generated per
unit volume and per unit time, then the total heat generated in the control volume
equals to
ππ ππ₯ ππ¦ ππ§ ππ β β β β β β β (2.8)
The total heat accumulated in the control volume due to heat flow along all the co-
ordinate axes and the heat generated within the control volume together increases
the internal energy of the control volume.
Change in internal energy of the control volume is given by
π (ππ₯ ππ¦ ππ§) π ππ‘
ππ ππ β β β β β β β (2.9)
According to first law of thermodynamics heat accumulated within the control
volume due to heat flow along the co-ordinate axes
(heat accumulated within the control volume due to heat flow along the co
β ordinate axes) + (βπππ‘ πππππππ‘ππ π€ππ‘βππ π‘βπ ππππ‘πππ π£πππ’ππ)
= (πβππππ ππ πππ‘πππππ ππππππ¦ ππ π‘βπ ππππ‘πππ π£πππ’ππ)
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.7
[π
ππ₯(ππ₯
ππ‘
ππ₯) +
π
ππ¦(ππ¦
ππ‘
ππ¦) +
π
ππ§(ππ§
ππ‘
ππ§)] ππ₯ ππ¦ ππ§ ππ + ππ ππ₯ ππ¦ ππ§ ππ
= π (ππ₯ ππ¦ ππ§) π ππ‘
ππ ππ β β β β β β β (2.10)
Dividing both sides by dx dy dz dΟ
π
ππ₯(ππ₯
ππ‘
ππ₯) +
π
ππ¦(ππ¦
ππ‘
ππ¦) +
π
ππ§(ππ§
ππ‘
ππ§) + ππ = π π
ππ‘
ππβ β β β β β β (2.11)
This expression is known as general heat conduction equation for Cartesian co-
ordinate system.
Note:- Homogeneous and isotropic material: A homogeneous material implies that
the properties, i.e., density, specific heat and thermal conductivity of the material
are same everywhere in the material system. Isotropic means that these properties
are not directional characteristics of the material, i.e., they are independent of the
orientation of the surface.
Therefore for an isotropic and homogeneous material, thermal conductivity is same
at every point and in all directions. In that case kx = ky = kz = k and equation
becomes:
π2π‘
ππ₯2+
π2π‘
ππ¦2+
π2π‘
ππ§2+
ππ
π=
π π
π ππ‘
ππ=
1
πΌ
ππ‘
ππβ β β β β β β (2.12)
The quantity Ξ± = k Οcβ is called the thermal diffusivity, and it represents a physical
property of the material of which the solid element is composed. By using the
Laplacian operator β2, the equation may be written as:
β2π‘ +ππ
π=
1
πΌ
ππ‘
ππβ β β β β β β (2.13)
Equation governs the temperature distribution under unsteady heat flow through a
homogeneous and isotropic material.
Different cases of particular interest are:
For steady state heat conduction, heat flow equation reduces to:
π2π‘
ππ₯2+
π2π‘
ππ¦2+
π2π‘
ππ§2+
ππ
π= 0 β β β β β β β (2.14)
or
β2π‘ +ππ
π= 0
This equation is called Poissonβs equation.
In the absence of internal heat generation, equation further reduces to:
π2π‘
ππ₯2+
π2π‘
ππ¦2+
π2π‘
ππ§2= 0 β β β β β β β (2.15)
or
β2π‘ = 0
2. Steady State Heat Conduction Heat Transfer (3151909)
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This equation is called Laplace equation.
Unsteady state heat flow with no internal heat generation gives:
π2π‘
ππ₯2+
π2π‘
ππ¦2+
π2π‘
ππ§2=
1
πΌ
ππ‘
ππβ β β β β β β (2.16)
or
β2π‘ =1
πΌ
ππ‘
ππ
This equation is called Fourier equation.
For one-dimensional and steady state heat flow with no heat generation, the general
heat conduction equation is reduced to:
π
ππ₯(π
ππ‘
ππ₯) = 0;
π2π‘
ππ₯2= 0 β β β β β β β (2.17)
Thermal diffusivity:
Thermal diffusivity πΌ of a material is the ratio of its thermal conductivity π to the
thermal storage capacity ππ. The storage capacity essentially represents thermal
capacitance or thermal inertia of the material.
It signifies the rate at which heat diffuses in to the medium during change in
temperature with time. Thus, the higher value of the thermal diffusivity gives the
idea of how fast the heat is conducting into the medium, whereas the low value of
the thermal diffusivity shown that the heat is mostly absorbed by the material and
comparatively less amount is transferred for the conduction.
2.4.2 Cylindrical Co-ordinates:-
When heat is transferred through system having cylindrical geometries like tube of
heat exchanger, then cylindrical co-ordinate system is used.
Consider infinitesimal small element of volume
ππ = (ππ ππβ ππ§)
(a) (b)
Fig. 2.3 (a) Cylindrical co-ordinate system (b) An element of cylinder
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.9
Fig. 2.3 (c) Heat conduction through cylindrical element
Assumptions:
1) Thermal conductivityπ, density π and specific heat π for the material do not vary
with position.
2) Uniform heat generation at the rate of ππ per unit volume per unit time,
a) Heat transfer in radial direction, (π§ β β πππππ)
Heat influx
ππ = βπ (ππβ ππ§) ππ‘
ππ ππ β β β β β β β (2.18)
Heat efflux
ππ+ππ = ππ +π
ππ(ππ) ππ β β β β β β β (2.19)
Heat stored in the element due to flow of heat in the radial direction
πππ = ππ β ππ+ππ
= βπ
ππ(ππ) ππ
= βπ
ππ[βπ (ππβ ππ§)
ππ‘
ππ ππ] ππ
= π (ππ πβ ππ§) π
ππ(π
ππ‘
ππ) ππ
= π (ππ πβ ππ§) (ππ2π‘
ππ2+
ππ‘
ππ) ππ
= π (ππ ππβ ππ§) (π2π‘
ππ2+
1
π
ππ‘
ππ) ππ
2. Steady State Heat Conduction Heat Transfer (3151909)
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= π ππ (π2π‘
ππ2+
1
π
ππ‘
ππ) ππ β β β β β β β (2.20)
b) Heat transfer in tangential direction (π β π§ πππππ)
Heat influx
πβ = βπ (ππ ππ§) ππ‘
ππβ ππ β β β β β β β (2.21)
Heat efflux
πβ +πβ = πβ +π
ππβ (πβ ) ππβ β β β β β β β (2.22)
Heat stored in the element due to heat flow in the tangential direction,
ππβ = πβ β πβ +πβ
= βπ
ππβ (πβ ) ππβ
= βπ
ππβ [βπ (ππ ππ§)
ππ‘
ππβ ππ] ππβ
= π (ππ ππβ ππ§) π
ππβ (
ππ‘
ππβ ) ππ
= π (ππ ππβ ππ§) 1
π2
π2π‘
πβ 2 ππ
= π ππ 1
π2
π2π‘
πβ 2 ππ β β β β β β β (2.23)
c) Heat transferred in axial direction (π β β πππππ)
Heat influx
ππ§ = βπ (ππβ ππ) ππ‘
ππ§ ππ β β β β β β β (2.24)
Heat efflux
ππ§+ππ§ = ππ§ +π
ππ§(ππ§) ππ§ β β β β β β β (2.25)
Heat stored in the element due to heat flow in axial direction,
πππ§ = ππ§ β ππ§+ππ§
= βπ
ππ§(ππ§) ππ§
= βπ
ππ§[βπ (ππβ ππ)
ππ‘
ππ§ ππ] ππ§
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.11
= π (ππ ππβ ππ§) π2π‘
ππ§2 ππ
= π ππ π2π‘
ππ§2 ππ β β β β β β β (2.26)
d) Heat generated within the control volume
= ππ ππ ππ β β β β β β β (2.27)
e) Rate of change of energy within the control volume
= π ππ π ππ‘
ππ ππ β β β β β β β (2.28)
According to first law of thermodynamics, the rate of change of energy within the
control volume equals the total heat stored plus the heat generated. So,
π ππ [π2π‘
ππ2+
1
π
ππ‘
ππ+
1
π2
π2π‘
πβ 2+
π2π‘
ππ§2] ππ + ππ ππ ππ
= π ππ π ππ‘
ππ ππ β β β β β β β (2.29)
Dividing both sides by dV dΟ
π [π2π‘
ππ2+
1
π
ππ‘
ππ+
1
π2
π2π‘
πβ 2+
π2π‘
ππ§2] + ππ = π π
ππ‘
ππ
or
[π2π‘
ππ2+
1
π
ππ‘
ππ+
1
π2
π2π‘
πβ 2+
π2π‘
ππ§2] +
ππ
π =
π π
π ππ‘
ππ=
1
πΌ
ππ‘
ππβ β β β β β β (2.30)
which is the general heat conduction equation in cylindrical co-ordinates.
For steady state unidirectional heat flow in the radial direction, and with no internal
heat generation, equation reduces to
(π2π‘
ππ2+
1
π
ππ‘
ππ) = 0
or
1
π
π
ππ(π
ππ‘
ππ) = 0
Since1
rβ 0
π
ππ(π
ππ‘
ππ) = 0 ππ π
ππ‘
ππ= ππππ π‘πππ‘ β β β β β β β (2.31)
2. Steady State Heat Conduction Heat Transfer (3151909)
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2.4.3 Spherical Co-ordinates:-
When heat is transferred through system having spherical geometries like spherical
storage tank, ball of ball bearing, junction of thermocouple, then cylindrical co-
ordinate system is used.
Consider infinitesimal small element of volume
ππ = (ππ β πππ β ππ πππ πβ )
Assumptions:
1) Thermal conductivityπ, density π and specific heat π for the material do not vary
with position.
2) Uniform heat generation at the rate of ππ per unit volume per unit time,
(a) (b)
(c)
Fig. 2.4 (a) Spherical co-ordinate system (b) An element of sphere
(c) Heat conducted through spherical element
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.13
a) Heat transferred through π β π πππππ, β β ππππππ‘πππ
Heat influx
πβ = βπ (ππ β πππ) ππ‘
π π πππ πβ ππ β β β β β β β (2.32)
Heat efflux
πβ +πβ = πβ +π
π π πππ πβ (πβ ) π π πππ πβ β β β β β β β (2.33)
Heat stored in the element due to heat flow in the tangential direction,
ππβ = πβ β πβ +πβ
= βπ
π π πππ πβ (πβ ) π π πππ πβ
= β1
π π πππ
π
πβ [βπ (ππ β πππ)
1
π π πππ
ππ‘
πβ ππ] π π πππ πβ
= π (ππ β πππ β π π πππ πβ ) 1
π2 π ππ2π
π2π‘
πβ 2 ππ
= π ππ 1
π2 π ππ2π
π2π‘
πβ 2 ππ β β β β β β β (2.34)
b) Heat flow through π β β πππππ, π β ππππππ‘πππ
Heat influx
ππ = βπ (ππ β ππ πππ πβ ) ππ‘
πππ ππ β β β β β β β (2.35)
Heat efflux
ππ+ππ = ππ +π
πππ(ππ) πππ β β β β β β β (2.36)
Heat stored in the element due to heat flow in the tangential direction,
πππ = ππ β ππ+ππ
= βπ
πππ(ππ) πππ
= βπ
πππ[βπ (ππ β ππ πππ πβ )
ππ‘
πππ ππ] πππ
= π (ππ β π πβ β πππ)π
πππ(π πππ
ππ‘
πππ) ππ
= π (ππ β π π πππ πβ β πππ)1
π2π πππ
π
ππ(π πππ
ππ‘
ππ) ππ
= π ππ1
π2π πππ
π
ππ(π πππ
ππ‘
ππ) ππ β β β β β β β (2.37)
2. Steady State Heat Conduction Heat Transfer (3151909)
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c) Heat flow through π β β πππππ, π β ππππππ‘πππ
Heat influx
ππ = βπ (πππ β ππ πππ πβ ) ππ‘
ππ ππ β β β β β β β (2.38)
Heat efflux
ππ+ππ = ππ +π
ππ(ππ) ππ β β β β β β β (2.39)
Heat stored in the element volume due to heat flow in the r β direction
πππ = ππ β ππ+ππ
= βπ
ππ(ππ) ππ
= βπ
ππ[βπ (πππ β ππ πππ πβ )
ππ‘
ππ ππ] ππ
= π (ππ β π πππ πβ β ππ)π
ππ[π2
ππ‘
ππ ] ππ
= π (πππ β ππ πππ πβ β ππ)1
π2
π
ππ[π2
ππ‘
ππ ] ππ
= π ππ 1
π2
π
ππ(π2
ππ‘
ππ) ππ β β β β β β β (2.40)
d) Heat generated within the control volume
= ππ ππ ππ β β β β β β β (2.41)
e) Rare of change of energy within the control volume
= π ππ π ππ‘
ππ ππ β β β β β β β (2.42)
According to first law of thermodynamics, the rate of change of energy within the
control volume equals the total heat stored plus the heat generated. So,
π ππ [1
π2 π ππ2π
π2π‘
πβ 2+
1
π2π πππ
π
ππ(π πππ
ππ‘
ππ) +
1
π2
π
ππ(π2
ππ‘
ππ)] ππ + ππ ππ ππ
= π ππ π ππ‘
ππ ππ
Dividing sides by k dV dΟ
[1
π2 π ππ2π
π2π‘
πβ 2+
1
π2π πππ
π
ππ(π πππ
ππ‘
ππ) +
1
π2
π
ππ(π2
ππ‘
ππ)] +
ππ
π=
ππ
π ππ‘
ππ
=1
πΌ ππ‘
ππβ β β β β β β (2.43)
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.15
Which is the general heat conduction equation in spherical co-ordinates
The heat conduction equation in spherical co-ordinates could also be obtained by
utilizing the following inter relation between the rectangular and spherical co-
ordinates.
π₯ = π sin π sin β
π¦ = π sin π πππ β
π§ = ππππ π
For steady state, uni-direction heat flow in the radial direction for a sphere with no
internal heat generation, equation can be written as
1
π2
π
ππ(π2
ππ‘
ππ) = 0 β β β β β β β (2.44)
General one-dimensional conduction equation: The one-dimensional time
dependent heat conduction equation can be written as
1
ππ
π
ππ(ππ π
ππ‘
ππ) + ππ = π π
ππ‘
ππβ β β β β β β (2.45)
Where n = 0, 1 and 2 for rectangular, cylindrical and spherical co-ordinates
respectively. Further, while using rectangular co-ordinates it is customary to replace
the r-variable by the x-variable.
2.5 Measurement of Thermal Conductivity (Guarded Hot Plate
Method) Construction
The essential elements of the experimental set-up as shown in figure 2.5 are:
Main heater π»π placed at the centre of the unit. It is maintained at a fixed
temperature by electrical energy which can be metered.
Guarded heater π»π which surrounds the main heater on its ends. The guarded
heater is supplied electrical energy enough to keep its temperature same as that of
main heater.
Fig. 2.5 Elements of guarded hot plate method
2. Steady State Heat Conduction Heat Transfer (3151909)
Prepared By: Mehul K. Pujara Department of Mechanical Engineering Page 2.16 Darshan Institute of Engineering & Technology, Rajkot
Function of the guarded heater is to ensure unidirectional heat flow and eliminates
the distortion caused by edge losses.
Test specimens π1 and π2 which are placed on both sides of the heater.
Cooling unit plates πΆ1 and πΆ2 are provided for circulation of cooling medium. Flow of
cooling medium is maintained to keep the constant surface temperature of
specimen.
Thermocouples attached to the specimens at the hot and cold faces.
Desired measurement
From the Fourierβs law of heat conduction
π = βππ΄ππ‘
ππ₯=
ππ΄
π(π‘β β π‘π)
β΄ π =π
π΄
π
(π‘β β π‘π)β β β β β β β (2.46)
So to measure thermal conductivity k following measurements are required
Heat flow Q from the main heart through a test specimen; it will be half of the total
electrical input to the main heater
Thickness of the specimen X
Temperature drop across the specimen (π‘β β π‘π); subscripts h and c refer to the hot
and cold faces respectively
Area A of heat flow; the area for heat flow is taken to be the area of main heater
plus the area of one-half of air gap between it and the guarded heater
For the specimen of different thickness, the respective temperature at the hot and
cold faces would be different and then the thermal conductivity is worked out from
the following relation:
π =π
π΄(
π1
(π‘β1 β π‘π1)+
π2
(π‘β2 β π‘π2)) β β β β β β β (2.47)
Where suffix 1 is for the upper specimen and 2 is for the lower specimen.
Here Q is the total electrical input to the main heater.
2.6 Conduction Through a Plane Wall:-
Consider one-dimensional heat conduction through a homogeneous, isotropic wall
of thickness Ξ΄ with constant thermal conductivity k and constant cross-sectional area
A.
The wall is insulated on its lateral faces, and constant but different temperatures t1
and t2 are maintained at its boundary surfaces.
Starting with general heat conduction equation in Cartesian co-ordinates
π2π‘
ππ₯2+
π2π‘
ππ¦2+
π2π‘
ππ§2+
ππ
π=
1
πΌ
ππ‘
ππβ β β β β β β (2.48)
For steady state, one dimensional with no heat generation equation is reduced to
π2π‘
ππ₯2= 0
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.17
or
π2π‘
ππ₯2= 0 β β β β β β β (2.49)
Integrate the equation with respect to x is given by
ππ‘
ππ₯= πΆ1
π‘ = πΆ1π₯ + πΆ2 β β β β β β β (2.50)
The constants of integration are evaluated by using boundary conditions and here
boundary conditions are:
π‘ = π‘1 at π₯ = 0 and π‘ = π‘2 at π₯ = πΏ
When boundary conditions are applied
π‘1 = 0 + πΆ2 and π‘2 = πΆ1πΏ + πΆ2
So, integration constants are
πΆ2 = π‘1, πΆ1 =π‘2 β π‘1
πΏ
Accordingly the expression for temperature profile becomes
π‘ = π‘1 + (π‘2 β π‘1
πΏ) π₯ β β β β β β β (2.51)
The temperature distribution is thus linear across the wall. Since equation does not
involve thermal conductivity so temperature distribution is independent of the
material; whether it is steel, wood or asbestos.
Heat flow can be made by substitution the value of temperature gradient into
Fourier equation
π = βπ π΄ ππ‘
ππ₯
ππ‘
ππ₯=
π
ππ₯[π‘1 + (
π‘2 β π‘1
πΏ) π₯] =
π‘2 β π‘1
πΏ
β΄ π = βπ π΄ π‘2 β π‘1
πΏ=
π π΄ (π‘1 β π‘2)
πΏβ β β β β β β (2.52)
Alternatively, The Fourier rate equation may be used directly to determine the heat
flow rate.
Consider an elementary strip of thickness dx located at a distance x from the
reference plane. Temperature difference across the strip is dt, and temperature
gradient is dt dxβ .
Heat transfer through the strip is given by
π = βπ π΄ ππ‘
ππ₯
2. Steady State Heat Conduction Heat Transfer (3151909)
Prepared By: Mehul K. Pujara Department of Mechanical Engineering Page 2.18 Darshan Institute of Engineering & Technology, Rajkot
Fig. 2.6 Heat conduction through plane wall
For steady state condition, heat transfer through the strip is equal to the heat
transfer through the wall. So integrate the equation between the limits, t = t1 at x =
0 and t = t2 at x = Ξ΄, thus
π β« ππ₯
πΏ
0
= βπ π΄ β« ππ‘
π‘2
π‘1
π πΏ = π π΄(π‘1 β π‘2); π =π π΄ (π‘1 β π‘2)
πΏβ β β β β β β (2.53)
To determine the temperature at any distance x from the wall surface, the Fourier
rate equation is integrated between the limit:
a) π₯ = 0 where the temperature is stated to be π‘1
b) π₯ = π₯ where the temperature is to be worked out
Thus,
π β« ππ₯
π₯
0
= βπ π΄ β« ππ‘
π‘
π‘1
π π₯ = π π΄(π‘1 β π‘); π =π π΄ (π‘1 β π‘)
π₯
Substituting the value of Q in above equation
π π΄ (π‘1 β π‘2)
πΏ=
π π΄ (π‘1 β π‘)
π₯
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.19
β΄ π‘ = π‘1 + (π‘2 β π‘1
πΏ) π₯ β β β β β β β (2.54)
The expression for the heat flow rate can be written as
π =π‘1 β π‘2
πΏ π π΄β=
π‘1 β π‘2
π π‘β β β β β β β (2.55)
Where Rt = Ξ΄ k Aβ is the thermal resistance to heat flow. Equivalent thermal circuit
for flow through a plane wall has been included in figure 2.6.
Let us develop the condition when weight, not space, required for insulation of a
plane wall is the significant criterion.
For one dimensional steady state heat condition
π =π π΄ (π‘1 β π‘2)
πΏ=
π‘1 β π‘2
πΏ π π΄β
Thermal resistance of the wall, Rt = Ξ΄ k Aβ
Weight of the wall, W = Ο A Ξ΄
Eliminating the wall thickness Ξ΄ from expression
π π‘ =π
πππ΄2
π = (ππ)π π‘π΄2 β β β β β β β (2.56)
From the equation when the product (Οk) for a given resistance is smallest, the
weight of the wall would also be so. It means for the lightest insulation for a
specified thermal resistance, product of density times thermal conductivity should
be smallest.
2.7 Conduction Through a Composite Wall
A composite wall refers to a wall of a several homogenous layers.
Wall of furnace, boilers and other heat exchange devices consist of several layers; a
layer for mechanical strength or for high temperature characteristics (fire brick), a
layer of low thermal conductivity material to restrict the flow of heat (insulating
brick) and another layer for structural requirements for good appearance (ordinary
brick).
Figure 2.7 shows one such composite wall having three layers of different materials
tightly fitted to one another.
The layers have thickness Ξ΄1, Ξ΄2, Ξ΄3 and their thermal conductivities correspond to
the average temperature conditions.
The surface temperatures of the wall are t1 and t4 and the temperatures at the
interfaces are t2 and t3.
2. Steady State Heat Conduction Heat Transfer (3151909)
Prepared By: Mehul K. Pujara Department of Mechanical Engineering Page 2.20 Darshan Institute of Engineering & Technology, Rajkot
Fig. 2.7 Heat conduction through composite wall
Under steady state conditions, heat flow does not vary across the wall. It is same for
every layer. Thus
π =π1π΄
πΏ1
(π‘1 β π‘2) =π2π΄
πΏ2
(π‘2 β π‘3) =π3π΄
πΏ3
(π‘3 β π‘4) β β β β β β β (2.57)
Rewriting the above expression in terms of temperature drop across each layer,
π‘1 β π‘2 =π πΏ1
π1π΄; π‘2 β π‘3 =
π πΏ2
π2π΄; π‘3 β π‘4 =
π πΏ3
π3π΄
Summation gives the overall temperature difference across the wall
π‘1 β π‘4 = π ( πΏ1
π1π΄+
πΏ2
π2π΄+
πΏ3
π3π΄)
Then
π =(π‘1 β π‘4)
πΏ1
π1π΄+
πΏ2
π2π΄+
πΏ3
π3π΄
π =(π‘1 β π‘4)
π π‘1 + π π‘2 + π π‘3=
(π‘1 β π‘4)
π π‘β β β β β β β (2.58)
Where Rt = Rt1 + Rt2 + Rt3, is the total resistance.
Analysis of the composite wall assumes that there is a perfect contact between
layers and no temperature drop occurs across the interface between materials.
2.8 Heat Flow Between Surface and Surroundings: Cooling and
Heating of Fluids
When a moving fluid comes into contact with a stationary surface, a thin boundary
layer develops adjacent to the wall and in this layer there is no relative velocity with
respect to surface.
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.21
Fig. 2.8 Heat conduction through a wall separating two fluids
In a heat exchange process, this layer is called stagnant film and heat flow in the
layer is covered both by conduction and convection processes. Since thermal
conductivity of fluids is low, the heat flow from the moving fluid of the wall is mainly
due to convection.
The rate of convective heat transfer between a solid boundary and adjacent fluid is
given by the Newton-Rikhman law:
π = β π΄(π‘π β π‘π) β β β β β β β (2.59)
Where, tf is the temperature of moving fluid, ts is the temperature of the wall
surface, A is the area exposed to heat transfer and h is the convective co-efficient.
The dimension of h is W m2 β degβ .
Heat transfer by convection may be written as
π =π‘π β π‘π
1
β π΄
=π‘π β π‘π
π π‘β β β β β β β (2.60)
Where Rt = 1h Aβ is the convection resistance.
The heat transfer through a wall separating two moving fluids involves: (i) flow of
heat from the fluid of high temperature to the wall, (ii) heat conduction through the
wall and (iii) transport of heat from the wall to the cold fluid.
Under steady state conditions, the heat flow can be expressed by the equations:
π = βπ π΄(π‘π β π‘1) =ππ΄
πΏ(π‘1 β π‘2) = βπ π΄(π‘2 β π‘π)
Where ha and hb represent the convective film coefficients, k is thermal conductivity
of the solid wall having thickness Ξ΄. These expressions can be presented in the form:
2. Steady State Heat Conduction Heat Transfer (3151909)
Prepared By: Mehul K. Pujara Department of Mechanical Engineering Page 2.22 Darshan Institute of Engineering & Technology, Rajkot
π‘π β π‘1 =π
βπ π΄; π‘1 β π‘2 =
π πΏ
ππ΄; π‘2 β π‘π =
π
βπ π΄
Summation of these gives
π‘π β π‘π = π (1
βπ π΄+
πΏ
ππ΄+
1
βπ π΄)
β΄ π =(π‘π β π‘π)
1
βππ΄+
πΏ
ππ΄+
1
βππ΄
β β β β β β β (2.61)
The denominator (1 haAβ + Ξ΄ kAβ + 1 hbAβ ) is the sum of thermal resistance of
difference sections through which heat has to flow.
Heat flow through a composite section is written in the form
π = ππ΄(π‘π β π‘π) =(π‘π β π‘π)
1ππ΄β
β β β β β β β (2.62)
Where, U is the overall heat transfer coefficient.
It represents the intensity of heat transfer from one fluid to another through a wall
separating them.
Numerically it equals the quantity of heat passing through unit area of wall surface in
unit time at a temperature difference of unit degree. The coefficient U has
dimensions of W m2 β degβ .
By comparing the equation
1
ππ΄=
1
βππ΄+
πΏ
ππ΄+
1
βππ΄= π π‘ β β β β β β β (2.63)
So heat transfer coefficient is reciprocal of unit thermal resistance to heat flow.
The overall heat transfer coefficient depends upon the geometry of the separating
wall, its thermal properties and the convective coefficient at the two surfaces.
The overall heat transfer coefficient is particularly useful in the case of composite
walls, such as in the design of structural walls for boilers, refrigerators, air-
conditioned buildings, and in the design of heat exchangers.
2.9 Conduction Through a Cylindrical Wall
Consider heat conduction through a cylindrical tube of inner radius r1, outer radius
r2 and length l.
The inside and outside surfaces of the tube are at constant temperatures t1 and t2
and thermal conductivity k of the tube material is constant within the given
temperature range.
If both ends are perfectly insulated, the heat flow is limited to radial direction only.
Further if temperature t1 at the inner surface is greater than temperature t2 at the
outer surface, the heat flows radially outwords.
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.23
Fig. 2.9 Steady state heat conduction through a cylindrical wall
The general heat conduction equation for cylindrical co-ordinate is given by
[π2π‘
ππ2+
1
π
ππ‘
ππ+
1
π2
π2π‘
πβ 2+
π2π‘
ππ§2] +
ππ
π =
1
πΌ
ππ‘
ππ
For steady state (βt βΟβ = 0) unidirectional heat flow in the radial direction and with
no internal heat generation (qg = 0) the above equation reduces to
π2π‘
ππ2+
1
π
ππ‘
ππ= 0
1
π
π
ππ(π
ππ‘
ππ) = 0
Since, 1
rβ 0
π
ππ(π
ππ‘
ππ) = 0 , π
ππ‘
ππ= ππππ π‘πππ‘ πΆ1
Integration of above equation gives
π‘ = πΆ1 ππππ π + πΆ2 β β β β β β β (2.64)
Using the following boundary conditions
π‘ = π‘1 ππ‘ π = π1, and π‘ = π‘2 ππ‘ π = π2
The constants C1 and C2 are
πΆ1 = βπ‘1 β π‘2
πππππ2
π1β
; πΆ2 = π‘1 +π‘1 β π‘2
πππππ2
π1β
ππππ π1
Using the values of C1 and C2 temperature profile becomes
π‘ = π‘1 +π‘1 β π‘2
πππππ2
π1β
ππππ π1 βπ‘1 β π‘2
πππππ2
π1β
ππππ π β β β β β β β (2.65)
(π‘ β π‘1) πππππ2
π1β = (π‘1 β π‘2) ππππ π1 β (π‘1 β π‘2) ππππ π
= (π‘2 β π‘1) ππππ π β (π‘2 β π‘1) ππππ π1 = (π‘2 β π‘1) πππππ
π1β
2. Steady State Heat Conduction Heat Transfer (3151909)
Prepared By: Mehul K. Pujara Department of Mechanical Engineering Page 2.24 Darshan Institute of Engineering & Technology, Rajkot
Therefore in dimensionless form
π‘ β π‘1
π‘2 β π‘1=
πππππ
π1β
πππππ2
π1β
β β β β β β β (2.66)
From the equation it is clear that temperature distribution with radial conduction
through a cylinder is logarithmic; not linear as for a plane wall.
Further temperature at any point in the cylinder can be expressed as a function of
radius only.
Isotherms or lines of constant temperature are then concentric circles lying between
the inner and outer cylinder boundaries.
The conduction heat transfer rate is determined by utilizing the temperature
distribution in conjunction with the Fourier law:
π = βππ΄ππ‘
ππ
= βππ΄π
ππ[π‘1 +
π‘1 β π‘2
πππππ2
π1β
ππππ π1 βπ‘1 β π‘2
πππππ2
π1β
ππππ π]
= βπ(2πππ) (β(π‘1 β π‘2)
π πππππ2
π1β
)
= 2πππ(π‘1 β π‘2)
πππππ2
π1β
=(π‘1 β π‘2)
π π‘β β β β β β β (2.67)
In the alternative approach to estimate heat flow, consider an infinitesimally thin
cylindrical element at radius r.
Let thickness of this elementary ring be dr and the change of temperature across it
be dt.
Then according to Fourier law of heat conduction
π = βππ΄ππ‘
ππ= βπ(2πππ)
ππ‘
ππ
πππ
π(2πππ) = ππ‘
Integrate the equation within the boundary condition
π
2πππβ«
ππ
π=
π2
π1
β« ππ‘
π‘2
π‘1
π
2πππππππ
π2
π1= (π‘1 β π‘2)
π = 2πππ(π‘1 β π‘2)
πππππ2
π1β
=(π‘1 β π‘2)
π π‘β β β β β β β (2.68)
For conduction in hollow cylinder, the thermal resistance is given by:
π π‘ =ππππ
π2π1
β
2πππβ β β β β β β (2.69)
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.25
Special Notes
Heat conduction through cylindrical tubes is found in power plant, oil refineries and
most process industries.
The boilers have tubes in them, the condensers contain banks of tubes, the heat
exchangers are tubular and all these units are connected by tubes.
Surface area of a cylindrical surface changes with radius. Therefore the rate of heat
conduction through a cylindrical surface is usually expressed per unit length rather
than per unit area as done for plane wall.
Logarithmic Mean Area
It is advantageous to write the heat flow equation through a cylinder in the same
form as that for heat flow through a plane wall.
Fig. 2.10 Logarithmic mean area concept
Then thickness πΏ will be equal to (π2 β π1) and the area π΄ will be an equivalent area
π΄π. Thus
π =ππ΄
πΏ(π‘1 β π‘2) = ππ΄π
(π‘1 β π‘2)
(π2 β π1)β β β β β β β (2.70)
Comparing equations 3.68 and 3.70
π = 2Οkl(t1 β t2)
loger2
r1β
= ππ΄π
(π‘1 β π‘2)
(π2 β π1)
π΄π =2Ο(π2 β π1)π
loger2
r1β
=π΄2 β π΄1
logeA2
A1β
β β β β β β β (2.71)
Where π΄1 and π΄2 are the inner and outer surface areas of the cylindrical tube.
The equivalent area π΄π is called the logarithmic mean area of the tube. Further
π΄π = 2ππππ =2Ο(π2 β π1)π
loger2
r1β
2. Steady State Heat Conduction Heat Transfer (3151909)
Prepared By: Mehul K. Pujara Department of Mechanical Engineering Page 2.26 Darshan Institute of Engineering & Technology, Rajkot
Obviously, logarithmic mean radius of the cylindrical tube is:
ππ =(π2 β π1)
loger2
r1β
β β β β β β β (2.72)
2.10 Conduction Through a Multilayer Cylindrical Wall
Multi-layer cylindrical walls are frequently employed to reduce heat looses from
metallic pipes which handle hot fluids.
The pipe is generally wrapped in one or more layers of heat insulation.
For example, steam pipe used for conveying high pressure steam in a steam power
plant may have cylindrical metal wall, a layer of insulation material and then a layer
of protecting plaster.
The arrangement is called lagging of the pipe system.
Fig. 2.11 Steady state heat conduction through a composite cylindrical wall
Figure 2.11 shows conduction of heat through a composite cylindrical wall having
three layers of different materials.
There is a perfect contact between the layers and so an equal interface temperature
for any two neighbouring layers.
For steady state conduction, the heat flow through each layer is same and it can be
described by the following set of equations:
π = 2ππ1π(π‘1 β π‘2)
logππ2
π1β
= 2ππ2π(π‘2 β π‘3)
logππ3
π2β
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.27
= 2ππ3π(π‘3 β π‘4)
logππ4
π3β
These equations help to determine the temperature difference for each layer of the
composite cylinder,
(π‘1 β π‘2) =π
2ππ1πππππ
π2
π1
(π‘2 β π‘3) =π
2ππ2πππππ
π3
π2
(π‘3 β π‘4) =π
2ππ3πππππ
π4
π3
From summation of these equalities;
π‘1 β π‘4 = π [1
2ππ1πππππ
π2
π1+
1
2ππ2πππππ
π3
π2+
1
2ππ3πππππ
π4
π3]
Thus the heat flow rate through a composite cylindrical wall is
π =π‘1 β π‘4
1
2ππ1πππππ
π2
π1+
1
2ππ2πππππ
π3
π2+
1
2ππ3πππππ
π4
π3
β β β β β β β (2.73)
The quantity in the denominator is the sum of the thermal resistance of the different
layers comprising the composite cylinder.
π =π‘1 β π‘4
π π‘β β β β β β β (2.74)
Where, Rt is the total resistance
Fig. 2.12 Heat conduction through cylindrical wall with convection coefficient
If the internal and external heat transfer coefficients for the composite cylinder as
shown in figure 2.12 are hi and ho respectively, then the total thermal resistance to
heat flow would be:
π π‘ =1
2ππ1πβπ+
1
2ππ1πππππ
π2
π1+
1
2ππ2πππππ
π3
π2+
1
2ππ3πβπ
2. Steady State Heat Conduction Heat Transfer (3151909)
Prepared By: Mehul K. Pujara Department of Mechanical Engineering Page 2.28 Darshan Institute of Engineering & Technology, Rajkot
and heat transfer is given as
π =(π‘π β π‘π)
1
2ππ1πβπ+
1
2ππ1πππππ
π2
π1+
1
2ππ2πππππ
π3
π2+
1
2ππ3πβπ
β β β β β β β (2.75)
Overall Heat Transfer Coefficient U
The heat flow rate can be written as:
π = ππ΄(π‘π β π‘π) β β β β β β β (2.76)
Since the flow area varies for a cylindrical tube, it becomes necessary to specify the
area on which U is based.
Thus depending upon whether the inner or outer area is specified, two different
values are defined for U.
π = πππ΄π(π‘π β π‘π) = πππ΄π(π‘π β π‘π)
Equating equations of heat transfer
ππ2ππ1π(π‘π β π‘π) =(π‘π β π‘π)
1
2ππ1πβπ+
1
2ππ1πππππ
π2
π1+
1
2ππ2πππππ
π3
π2+
1
2ππ3πβπ
β΄ ππ =(π‘π β π‘π)
1
βπ+
π1
π1ππππ
π2
π1+
π1
π2ππππ
π3
π2+
π1
π3βπ
β β β β β β β (2.77)
Similarly
ππ =(π‘π β π‘π)
π3
π1βπ+
π3
π1ππππ
π2
π1+
π3
π2ππππ
π3
π2+
1
βπ
β β β β β β β (2.78)
Overall heat transfer coefficient may be calculated by simplified equation as follow
πππ΄π = πππ΄π =1
π π‘β β β β β β β (2.79)
2.11 Conduction Through a Sphere
Consider heat conduction through a hollow sphere of inner radius r1 and outer
radius r2 and made of a material of constant thermal conductivity.
Fig. 2.13 Steady state heat conduction through sphere
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.29
The inner and outer surfaces are maintained at constant but different temperatures
t1 and t2 respectively. If the inner surface temperature t1 is greater than outer
surface temperature t2, the heat flows radially outwards.
General heat conduction equation in spherical coordinates is given as
[1
π2 π ππ2π
π2π‘
πβ 2+
1
π2π πππ
π
ππ(π πππ
ππ‘
ππ) +
1
π2
π
ππ(π2
ππ‘
ππ)] +
ππ
π=
1
πΌ ππ‘
ππ
For steady state, uni-directional heat flow in the radial direction and with no internal
heat generation, the above equation is written as
1
π2
π
ππ(π2
ππ‘
ππ) = 0
π
ππ(π2
ππ‘
ππ) = 0 ππ
1
π2β 0
π2 ππ‘
ππ= πΆ1
π‘ = βπΆ1
π+ πΆ2
The relevant boundary conditions are
π‘ = π‘1 ππ‘ π = π1, π‘ = π‘2 ππ‘ π = π2
Using the above boundary conditions values of constants are
πΆ1 =(π‘1 β π‘2)π1π2
(π1 β π2)
πΆ2 = π‘1 +(π‘1 β π‘2)π1π2
π1(π1 β π2)
Substitute the values of constants in equation; the temperature distribution is given
as follow
π‘ = β(π‘1 β π‘2)π1π2
π(π1 β π2)+ π‘1 +
(π‘1 β π‘2)π1π2
π1(π1 β π2)
= β(π‘1 β π‘2)
π (1
π2 β
1
π1)
+ π‘1 +(π‘1 β π‘2)
π1 (1
π2 β
1
π1)
= π‘1 +(π‘1 β π‘2)
(1
π2 β
1
π1)
[1
π1β
1
π] β β β β β β β (2.80)
In non dimensional form
π‘ β π‘1
π‘2 β π‘1=
1
πβ
1
π1
(1
π2 β
1
π1)
=π2
π(
π β π1
π2 β π1)
Evidently the temperature distribution associated with radial conduction through a
spherical is represented by a hyperbola.
2. Steady State Heat Conduction Heat Transfer (3151909)
Prepared By: Mehul K. Pujara Department of Mechanical Engineering Page 2.30 Darshan Institute of Engineering & Technology, Rajkot
The conduction heat transfer rate is determined by utilizing the temperature
distribution in conjunction with the Fourier law:
π =4ππ(π‘1 β π‘2)π1π2
(π2 β π1)=
(π‘1 β π‘2)
(π2 β π1)4πππ1π2
ββ β β β β β β (2.81)
The denominator of the equation is the thermal resistance for heat conduction
through a spherical wall.
π π‘ =(π2 β π1)
4πππ1π2β β β β β β β (2.82)
In the alternative approach to determine heat flow, consider an infinitesimal thin
spherical element at radius r and thickness dr.
The change of temperature across it be dt. According to Fourier law of heat
conduction
π = βππ΄ππ‘
ππ= βπ(4ππ2)
ππ‘
ππ
Separating the variables and integrating within the boundary conditions
π
4ππβ«
ππ
π2
π2
π1
= β β« ππ‘π‘2
π‘1
π
4ππ(
1
π1 β
1
π2) = (π‘1 β π‘2)
β΄ π =4ππ(π‘1 β π‘2)π1π2
(π2 β π1)=
(π‘1 β π‘2)
(π2 β π1)4πππ1π2
β
Heat conduction through composite sphere can be obtained similar to heat
conduction through composite cylinder. Heat conduction through composite sphere
will be:
π =(π‘1 β π‘2)
π π‘1 + π π‘2 + π π‘3
π =(π‘1 β π‘2)
(π2 β π1)4ππ1π1π2
β +(π3 β π2)
4ππ2π2π3β +
(π4 β π3)4ππ3π3π4
ββ β β β β (2.83)
Further, if the convective heat transfer is considered, then
π =(π‘1 β π‘2)
π π‘π + π π‘1 + π π‘2 + π π‘3 + π π‘π
π =(π‘1 β π‘2)
14ππ1
2βπβ +
(π2 β π1)4ππ1π1π2
β +(π3 β π2)
4ππ2π2π3β +
(π4 β π3)4ππ3π3π4
β + 14ππ4
2βπβ
β β β β β β β(2.84)
2.12 Critical Thickness of Insulation
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.31
There is some misunderstanding about that addition of insulating material on a
surface always brings about a decrease in the heat transfer rate.
But addition of insulating material to the outside surfaces of cylindrical or spherical
walls (geometries which have non-constant cross-sectional areas) may increase the
heat transfer rate rather than decrease under the certain circumstances.
To establish this fact, consider a thin walled metallic cylinder of length l, radius ππ and
transporting a fluid at temperature π‘π which is higher than the ambient temperature
π‘π.
Insulation of thickness (πβππ) and conductivity k is provided on the surface of the
cylinder.
Fig. 2.14 Critical thickness of pipe insulation
With assumption
a. Steady state heat conduction
b. One-dimensional heat flow only in radial direction
c. Negligible thermal resistance due to cylinder wall
d. Negligible radiation exchange between outer surface of insulation and
surrounding
The heat transfer can be expressed as
π =(π‘π β π‘π)
π π‘1 + π π‘2 + π π‘3
π =(π‘π β π‘π)
1
2ππππβπ+
1
2πππππππ
π
ππ+
1
2πππβπ
β β β β β β β (2.85)
2. Steady State Heat Conduction Heat Transfer (3151909)
Prepared By: Mehul K. Pujara Department of Mechanical Engineering Page 2.32 Darshan Institute of Engineering & Technology, Rajkot
Where βπ and βπ are the convection coefficients at inner and outer surface
respectively.
The denominator represents the sum of thermal resistance to heat flow.
The value of π, ππ, βπ and βπ are constant; therefore the total thermal resistance will
depend upon thickness of insulation which depends upon the outer radius of the
arrangement.
It is clear from the equation 2.85 that with increase of radius r (i.e. thickness of
insulation), the conduction resistance of insulation increases but the convection
resistance of the outer surface decreases.
Therefore, addition of insulation can either increase or decrease the rate of heat
flow depending upon a change in total resistance with outer radius r.
To determine the effect of insulation on total heat flow, differentiate the total
resistance π π‘ with respect to r and equating to zero.
ππ π‘
ππ=
π
ππ[
1
2ππππβπ+
1
2πππππππ
π
ππ+
1
2πππβπ]
=1
2πππ
1
πβ
1
2ππ2πβπ
β΄1
2πππ
1
πβ
1
2ππ2πβπ= 0
1
2πππ
1
π=
1
2ππ2πβπ
β΄ π =π
βπβ β β β β β β (2.86)
To determine whether the foregoing result maximizes or minimizes the total
resistance, the second derivative need to be calculated
π2π π‘
ππ2=
π
ππ[
1
2πππ
1
πβ
1
2ππ2πβπ]
= β1
2πππ
1
π2+
1
ππ3πβπ
ππ‘ π =π
βπ
π2π π‘
ππ2= β
1
2πππ(
βπ2
π2) +
1
ππβπ(
βπ3
π3)
=βπ
2
2ππ3π
which is positive, so π = πβπ
β represent the condition for minimum resistance and
consequently maximum heat flow rate.
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.33
The insulation radius at which resistance to heat flow is minimum is called critical
radius.
The critical radius, designated by ππ is dependent only on thermal quantities π and
βπ.
β΄ π = ππ =π
βπ
From the above equation it is clear that with increase of radius of insulation heat
transfer rate increases and reaches the maximum at π = ππ and then it will decrease.
Two cases of practical interest are:
When ππ < ππ
It is clear from the equation 2.14a that with addition of insulation to bare pipe
increases the heat transfer rate until the outer radius of insulation becomes equal to
the critical radius.
Because with addition of insulation decrease the convection resistance of surface of
insulation which is greater than increase in conduction resistance of insulation.
Fig. 2.14 Dependence of heat loss on thickness of insulation
Any further increase in insulation thickness decreases the heat transfer from the
peak value but it is still greater than that of for the bare pipe until a certain amount
of insulation (πβ).
So insulation greater than (πβ β ππ) must be added to reduce the heat loss below the
bare pipe.
This may happen when insulating material of poor quality is applied to pipes and
wires of small radius.
This condition is used for electric wire to increase the heat dissipation from the wire
which helps to increase the current carrying capacity of the cable.
2. Steady State Heat Conduction Heat Transfer (3151909)
Prepared By: Mehul K. Pujara Department of Mechanical Engineering Page 2.34 Darshan Institute of Engineering & Technology, Rajkot
Fig. 2.15 Critical radius of insulation for electric wire
When ππ < ππ
It is clear from the figure 2.14b that increase in insulation thickness always decrease
the heat loss from the pipe.
This condition is used to decrease the heat loss from steam and refrigeration pipes.
Critical radius of insulation for the sphere can be obtain in the similar way:
π π‘ =1
4ππ[
1
π1β
1
π] +
1
4ππ2βπ
ππ π‘
ππ=
π
ππ[
1
4ππ[
1
π1β
1
π] +
1
4ππ2βπ]
ππ π‘
ππ=
1
4πππ2β
2
4ππ3βπ= 0
β΄ π3βπ = 2ππ2
β΄ π = ππ =2π
βπβ β β β β β β (2.87)
2.13 Solved Numerical
Ex 2.1.
A 30 cm thick wall of 5 π π 3 π size is made of red brick (π = 0.3 π π β πππβ ).
It is covered on both sides by layers of plaster, 2 cm thick (π = 0.6 π π β πππβ ).
The wall has a window size of 1 π π 2 π. The window door is made of 12 mm
thick glass (π = 1.2 π π β πππβ ). If the inner and outer surface temperatures
are 15 and 40 , make calculation for the rate of heat flow through the wall.
Solution:
Given data:
Plaster: π1 = π3 = 0.6 π π β πππβ , π1 = π3 = 2 ππ = 2 Γ 10β2 π
Red brick: π2 = 0.3 π π β πππβ , π2 = 30 ππ = 30 Γ 10β2 π
Glass: π4 = 1.2 π π β πππβ , π4 = 12 ππ = 12 Γ 10β3 π
π‘π = 15β, π‘π = 40β, Total Area A = 5 π π 3 π = 15 π2,
Area of glass Window π΄ππππ π = 1 π π 2 π = 2 π2
Total heat transfer from the given configuration is sum of the heat transfer
from composite wall and glass window. So,
ππ‘ππ‘ππ = ππ€πππ + πππππ π
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.35
Heat transfer from the composite wall ππ€πππ
Area of the wall, π΄π€πππ = π΄ β π΄ππππ π = 15 β 2 = 13 π2
Resistance of inner and outer plaster layers, π 1 = π 3
π 1 = π 3 =π1
π1π΄π€πππ=
2 Γ 10β2
0.6 Γ 13= 2.564 Γ 10β3 β πβ
Resistance of brick work,
π 2 =π2
π2π΄π€πππ=
30 Γ 10β2
0.3 Γ 13= 76.92 Γ 10β3 β πβ
β΄ ππ€πππ =π‘π β π‘π
π 1 + π 2 + π 3=
40 β 15
2.564 Γ 10β3 + 76.92 Γ 10β3 + 2.564 Γ 10β3
ππ€πππ = 304.70 π
Heat transfer from glass window πππππ π
Resistance of glass,
π 4 =π4
π4π΄ππππ π =
12 Γ 10β3
1.2 Γ 2= 5 Γ 10β3 β πβ
2. Steady State Heat Conduction Heat Transfer (3151909)
Prepared By: Mehul K. Pujara Department of Mechanical Engineering Page 2.36 Darshan Institute of Engineering & Technology, Rajkot
β΄ πππππ π =π‘π β π‘π
π 4=
40 β 15
5 Γ 10β3= 5000 π
So total heat transfer is given by
ππ‘ππ‘ππ = 304.7 + 5000 = 5304.7 π = 5.304 ππ
Ex 2.2.
A cold storage room has walls made of 200 mm of brick on the outside, 80 mm of
plastic foam, and finally 20 mm of wood on the inside. The outside and inside air
temperatures are 25β and β3β respectively. If the outside and inside
convective heat transfer coefficients are respectively 10 and 30 π π2ββ , and the
thermal conductivities of brick, foam and wood are 1.0, 0.02 and 0.17 π πββ
respectively. Determine:
(i) Overall heat transfer coefficient
(ii) The rate of heat removed by refrigeration if the total wall area is 100π2
(iii) Outside and inside surface temperatures and mid-plane temperatures of
composite wall.
Solution:
Given data:
Brick: π1 = 1.0 π πββ , π1 = 200 ππ = 0.2 π
Plastic foam: π2 = 0.02 π πββ , π2 = 80 ππ = 80 Γ 10β3 π
Wood: π3 = 0.17 π πββ , π3 = 20 ππ = 20 Γ 10β3 π
π‘π = β3β, π‘π = 25β, βπ = 10π π2ββ , βπ = 30π π2ββ , π΄ = 100 π2
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.37
i. Over all heat transfer co-efficient U
Convection resistance of outer surface
π π =1
βππ΄=
1
10 Γ 100= 1 Γ 10β3 β πβ
Resistance of brick,
π 1 =π1
π1π΄=
0.2
1.0 Γ 100= 2 Γ 10β3 β πβ
Resistance of plastic foam,
π 2 =π2
π2π΄=
80 Γ 10β3
0.02 Γ 100= 40 Γ 10β3 β πβ
Resistance of wood,
π 3 =π3
π3π΄=
20 Γ 10β3
0.17 Γ 100= 1.176 Γ 10β3 β πβ
Convection resistance of inner surface
π π =1
βππ΄=
1
30 Γ 100= 0.333 Γ 10β3 β πβ
1
ππ΄= π π + π 1 + π 2 + π 3 + π π
= 1 Γ 10β3 + 2 Γ 10β3 + 40 Γ 10β3 + 1.176 Γ 10β3 + 0.333 Γ 10β3
= 44.509 Γ 10β3
β΄ π =1
44.509 Γ 10β3 Γ 100= 0.224 π π2ββ
ii. The rate of heat removed by refrigeration if the total wall area is A = 100π2
π = π Γ π΄ Γ (π‘π β π‘π) = 0.224 Γ 100 Γ (25 β (β3)) = 627.2 π
iii. Outside and inside surface temperatures and mid-plane temperatures of
composite wall
Temperature of outer surface π‘1
π =π‘π β π‘1
π π
π‘1 = π‘π β π Γ π π = 25 β 627.2 Γ 1 Γ 10β3 = 24.37β
Temperature of middle plane π‘2
π =π‘1 β π‘2
π 1
π‘2 = π‘1 β π Γ π 1 = 24.37 β 627.2 Γ 2 Γ 10β3 = 23.11 β
Temperature of middle plane π‘3
π =π‘2 β π‘3
π 2
π‘3 = π‘2 β π Γ π 2 = 23.11 β 627.2 Γ 40 Γ 10β3 = β1.97 β
Temperature of inner surface π‘4
π =π‘3 β π‘4
π 3
π‘4 = π‘3 β π Γ π 3 = β1.97 β 627.2 Γ 1.176 Γ 10β3 = β2.70 β
2. Steady State Heat Conduction Heat Transfer (3151909)
Prepared By: Mehul K. Pujara Department of Mechanical Engineering Page 2.38 Darshan Institute of Engineering & Technology, Rajkot
Ex 2.3.
A furnace wall is made up of three layer of thickness 250 mm, 100 mm and 150 mm
with thermal conductivity of 1.65, k and 9.2 π πββ respectively. The inside is
exposed to gases at 1250β with a convection coefficient of 25 π π2ββ and the
inside surface is at 1100β, the outside surface is exposed to air at 25β with
convection coefficient of 12 π π2ββ . Determine:
(i) The unknown thermal conductivity k
(ii) The overall heat transfer coefficient
(iii) All surface temperatures
Solution:
Given data:
Layer 1: k1 = 1.65 W mββ , X1 = 250 mm = 0.25 m
Layer 2: k2 = k W mββ , X2 = 100 mm = 0.1 m
Layer 3: k3 = 9.2 W mββ , X3 = 150 mm = 0.15 m
ti = 1250β, to = 25β, t1 = 1100β ho = 12W m2ββ , hi = 25W m2ββ , Take A = 1 m2
i. Unknown thermal conductivity k
Convection resistance of inner surface
π π =1
βππ΄=
1
25 Γ 1= 0.04β πβ
Resistance of layer 1,
π 1 =π1
π1π΄=
0.25
1.65 Γ 1= 0.1515β πβ
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.39
Resistance of layer 2,
π 2 =π2
π2π΄=
0.1
π2 Γ 1= 0.1
π2β β πβ
Resistance of layer 3,
π 3 =π3
π3π΄=
0.15
9.2 Γ 1= 0.0163β πβ
Convection resistance of outer surface
π π =1
βππ΄=
1
12 Γ 1= 0.083β πβ
Heat transfer by convection is given by
π =π‘π β π‘1
π π=1250 β 1100
0.04= 3750 π
Heat transfer through composite wall is given by
π =π‘π β π‘0
π π + π 1 + π 2 + π 3 + π 0
3750 =1250 β 25
0.04 + 0.1515 + π 2 + 0.0163 + 0.083
0.04 + 0.1515 + π 2 + 0.0163 + 0.083 =1250 β 25
3750
π 2 = 0.0358
β΄ 0.1π2
β = 0.0358
β΄ π2 = 0.10.0358β = 2.79W mββ
ii. Overall heat transfer co-efficient U 1
ππ΄= π π + π 1 + π 2 + π 3 + π π
= 0.04 + 0.1515 + 0.0358 + 0.0163 + 0.083 = 0.3103
π =1
0.3103 Γ 1= 3.222 π π2ββ
iii. All surface temperature
Temperature of inner surface π‘1 = 1100β
Temperature of middle plane π‘2
π =π‘1 β π‘2
π 1
π‘2 = π‘1 β π Γ π 1 = 1100 β 3750 Γ 0.1515 = 531.87 β
Temperature of middle plane t3
π =π‘2 β π‘3
π 2
π‘3 = π‘2 β π Γ π 2 = 531.87 β 3750 Γ 0.0358 = 397.62 β
Temperature of outer surface π‘4
π =π‘3 β π‘4
π 3
π‘4 = π‘3 β π Γ π 3 = 397.62 β 3750 Γ 0.0163 = 336.49 β
2. Steady State Heat Conduction Heat Transfer (3151909)
Prepared By: Mehul K. Pujara Department of Mechanical Engineering Page 2.40 Darshan Institute of Engineering & Technology, Rajkot
Ex 2.4.
A heater of 150 mm X 150 mm size and 800 W rating is placed between two slabs A
and B. Slab A is 18 mm thick with π = 55 π π πΎβ . Slab B is 10 mm thick with π =
0.2 π π πΎβ . Convective heat transfer coefficients on outside surface of slab A and B
are 200 π π2 πΎβ and 45 π π2 πΎβ respectively. If ambient temperature is 27β,
calculate maximum temperature of the system and outside surface temperature of
both slabs.
Solution:
Given data:
π΄πππ ππ βππ‘ππ π΄ = 150 ππ Γ 150 ππ = 22500 ππ2 = 22.5 Γ 10β3 π2
π ππ‘πππ ππ βπππ‘ππ = 800 π, toA = toB = to = 27β
Slab A: kA = 55 W mKβ , XA = 18 mm = 18 Γ 10β3 m, hoA = 200W m2Kβ
Slab B: kB = 0.2 W mKβ , XB = 10 mm = 10 Γ 10β3 m, hoB = 45W m2Kβ
i. Maximum temperature of the system
Maximum temperature exist at the inner surfaces of both slab A and slab B
So, maximum temperature π‘πππ₯ = π‘1π΄ = π‘1π΅
Under the steady state condition heat generated by the heater is equal to the
heat transfer through the slab A and slab B.
π = ππ΄ + ππ΅
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.41
Heat transfer through the slab A, ππ΄:
Resistance of slab A,
π π΄ =ππ΄
ππ΄π΄=
18 Γ 10β3
55 Γ 22.5 Γ 10β3= 0.0145πΎ πβ
Convection resistance of outer surface of slab A
π ππ΄ =1
βππ΄π΄=
1
200 Γ 22.5 Γ 10β3= 0.222πΎ πβ
β΄ ππ΄ =π‘1π΄ β π‘ππ΄
π π΄ + π ππ΄
Resistance of slab B,
π π΅ =ππ΅
ππ΅π΄=
10 Γ 10β3
0.2 Γ 22.5 Γ 10β3= 2.22 πΎ πβ
Convection resistance of outer surface of slab B
π ππ΅ =1
βππ΅π΄=
1
45 Γ 22.5 Γ 10β3= 0.987πΎ πβ
β΄ ππ΅ =π‘1π΅ β π‘ππ΅
π π΅ + π ππ΅
β΄ π = ππ΄ + ππ΅ =π‘1π΄ β π‘ππ΄
π π΄ + π ππ΄+
π‘1π΅ β π‘ππ΅
π π΅ + π ππ΅
β΄ π = (π‘πππ₯ β π‘π
0.0145 + 0.222+
π‘πππ₯ β π‘π
2.22 + 0.987) = (π‘πππ₯ β π‘π) {
1
0.2365+
1
3.207}
π = (π‘πππ₯ β π‘π) Γ 4.54
π‘πππ₯ =π
4.54+ π‘π =
800
4.54+ 27 = 203.21β
ii. Outside surface temperature of both slabs
Heat transfer through slab A
ππ΄ =π‘1π΄ β π‘ππ΄
π π΄ + π ππ΄=
203.21 β 27
0.0145 + 0.222= 745.07 π
Outside surface temperature of slab A, π‘2π΄
ππ΄ =π‘1π΄ β π‘2π΄
π π΄
π‘2π΄ = π‘1π΄ β ππ΄ Γ π π΄ = 203.21 β 745.07 Γ 0.0145 = 192.4 β
Heat transfer through slab B
π = ππ΄ + ππ΅
β΄ ππ΅ = 800 β 745.07 = 54.93 π
Outside surface temperature of both slab B, π‘2π΅
ππ΄ =π‘1π΅ β π‘2π΅
π π΅
π‘2π΅ = π‘1π΅ β ππ΅ Γ π π΅ = 203.21 β 54.93 Γ 2.22 = 81.2 β
Ex 2.5.
A 240 mm dia. steam pipe, 200 m long is covered with 50 mm of high temperature
insulation of thermal conductivity 0.092π πββ and 50 mm low temperature
2. Steady State Heat Conduction Heat Transfer (3151909)
Prepared By: Mehul K. Pujara Department of Mechanical Engineering Page 2.42 Darshan Institute of Engineering & Technology, Rajkot
insulation of thermal conductivity 0.062π πββ . The inner and outer surface
temperatures are maintained at 340β and 35β respectively. Calculate:
(i) The total heat loss per hour
(ii) The heat loss per π2 of pipe surface
(iii) The heat loss per π2 of outer surface
(iv) The temperature between interfaces of two layers of insulation.
Neglect heat conduction through pipe material.
Solution:
Given data:
r1 =240
2= 120 mm = 0.12 m
r2 = 120 + 50 = 170 mm = 0.17 m, r3 = 170 + 50 = 210 mm = 0.21 m
k1 = 0.092 W mββ , k2 = 0.062 W mββ
L = 200 m, t1 = 340 β, t3 = 35 β
i. Total heat loss per hour
Resistance of high temperature insulation
R1 =ln
π2π1
β
2ππ1πΏ=
ln(0.170.12β )
2π Γ 0.92 Γ 200= 0.3012 Γ 10β3 β Wβ
Resistance of low temperature insulation
R2 =ln
π3π2
β
2ππ2πΏ=
ln(0.210.17β )
2π Γ 0.062 Γ 200= 2.712 Γ 10β3 β Wβ
β΄ π =π‘1 β π‘3
π 1 + π 2=
340 β 35
0.3012 Γ 10β3 + 2.712 Γ 10β3= 101221.3 π½ π β
= 101221.3 Γ 3600 1000 = 364.39 Γ 103 π½ βπβ = 364.39 ππ½ βπββ
ii. The heat loss per π2 of pipe surface
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.43
=π
2ππ1πΏ=
101221.3
2π Γ 0.12 Γ 200= 671.24 π π2β
iii. The heat loss per π2 of outer surface
=π
2ππ3πΏ=
101221.3
2π Γ 0.21 Γ 200= 383.56 π π2β
iv. The temperature between interfaces of two layers of insulation
β΄ π =π‘1 β π‘2
π 1
π‘2 = π‘1 β π Γ π 1 = 340 β 101221.3 Γ 0.3012 Γ 10β3 = 309.51 β
Ex 2.6.
A hot fluid is being conveyed through a long pipe of 4 cm outer dia. And covered
with 2 cm thick insulation. It is proposed to reduce the conduction heat loss to the
surroundings to one-third of the present rate by further covering with some
insulation. Calculate the additional thickness of insulation.
Solution:
Given data:
r1 =4
2= 2 cm = 0.02 m
r2 = 2 + 2 = 4 cm = 0.04 m, r3 =?
i. Heat loss with existing insulation π1
Resistance of existing insulation
R1 =ln
π2π1
β
2ππ1πΏ
π1 =π‘1 β π‘2
π 1
ii. Heat loss with additional insulation π2
Resistance of existing insulation
R2 =ln
π3π2
β
2ππ1πΏ
2. Steady State Heat Conduction Heat Transfer (3151909)
Prepared By: Mehul K. Pujara Department of Mechanical Engineering Page 2.44 Darshan Institute of Engineering & Technology, Rajkot
π2 =π‘1 β π‘2
π 2
But, π1 = 13β π2
π‘1 β π‘2
π 1=
1
3Γ
π‘1 β π‘2
π 2
π 2 =1
3π 1
lnπ3
π2β
2ππ1πΏ=
1
3Γ
lnπ2
π1β
2ππ1πΏ
lnπ3
π2β =
1
3Γ ln
π2π1
β =1
3Γ ln 0.04
0.02β = 0.231
π3π2
β = π0.231 = 1.259
β΄ π3 = 1.259 Γ π2 = 1.259 Γ 0.04 = 0.0503 π = 5 ππ
β΄ ππππ‘πππππ π‘βππππππ π ππ πππ π’πππ‘πππ π‘ = π3 β π2 = 5 β 4 = 1 ππ
Ex 2.7.
A hot gas at 330β with convection coefficient 222 π π2 πΎβ is flowing through a
steel tube of outside diameter 8 cm and thickness 1.3 cm. It is covered with an
insulating material of thickness 2 cm, having conductivity of 0.2 π πβ πΎ. The outer
surface of insulation is exposed to ambient air at 25β with convection coefficient of
55 π π2 πΎβ .
Calculate: (1) Heat loss to air from 5 m long tube. (2) The temperature drop due to
thermal resistance of the hot gases, steel tube, the insulation layer and the outside
air. Take conductivity of steel = 50 π π πΎβ .
Solution:
Given data:
r2 =8
2= 4 cm = 0.04 m
r1 = 4 β 1.3 = 2.7 cm = 0.027 m, r3 = 4 + 2 = 6 cm = 0.06 m
k1 = 50 W mKβ , k2 = 0.2 W mKβ , βπ = 222 π π2 πΎβ , βπ = 55 π π2 πΎβ
L = 5 m, ti = 330 β, to = 25 β
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.45
i. Total heat loss to air from 5 m long tube, Q
Convection resistance of hot gases
Ri =1
βππ΄1=
1
βπ2ππ1πΏ=
1
222 Γ 2π Γ 0.027 Γ 5= 5.31 Γ 10β3 β Wβ
Resistance of steel
R1 =ln
π2π1
β
2ππ1πΏ=
ln(0.040.027β )
2π Γ 50 Γ 5= 0.25 Γ 10β3 β Wβ
Resistance of insulation
R2 =ln
π3π2
β
2ππ2πΏ=
ln(0.060.04β )
2π Γ 0.2 Γ 5= 64.53 Γ 10β3 β Wβ
Convection resistance of outside air
Ro =1
βππ΄π=
1
βπ2ππ3πΏ=
1
55 Γ 2π Γ 0.06 Γ 5= 9.64 Γ 10β3 β Wβ
β΄ π =π‘π β π‘π
π π + π 1 + π 2 + π π
=330 β 25
5.31 Γ 10β3 + 0.25 Γ 10β3 + 64.53 Γ 10β3 + 9.64 Γ 10β3= 3825.4 π
ii. Temperature drop
Temperature drop due to thermal resistance of hot gases
π =π‘π β π‘1
π π
β΄ π‘π β π‘1 = π Γ π π = 3825.4 Γ 5.31 Γ 10β3 = 20.31 β
Temperature drop due to thermal resistance of steel tube
π =π‘1 β π‘2
π 1
β΄ π‘1 β π‘2 = π Γ π 1 = 3825.4 Γ 0.25 Γ 10β3 = 0.95 β
Temperature drop due to thermal resistance of insulation
π =π‘2 β π‘3
π 2
β΄ π‘2 β π‘3 = π Γ π 2 = 3825.4 Γ 64.53 Γ 10β3 = 246.85 β
Temperature drop due to thermal resistance of outside air
π =π‘3 β π‘π
π π
β΄ π‘3 β π‘π = π Γ π π = 3825.4 Γ 9.64 Γ 10β3 = 36.87 β
Ex 2.8.
A pipe carrying the liquid at β20β is 10 mm in outer diameter and is exposed to
ambient at 25β with convective heat transfer coefficient of 50 W m2 Kβ . It is
proposed to apply the insulation of material having thermal conductivity of
0.5 W m Kβ . Determine the thickness of insulation beyond which the heat gain will be
reduced. Also calculate the heat loss for 2.5 mm, 7.5 mm and 15 mm thickness of
insulation over 1m length. Which one is more effective thickness of insulation?
2. Steady State Heat Conduction Heat Transfer (3151909)
Prepared By: Mehul K. Pujara Department of Mechanical Engineering Page 2.46 Darshan Institute of Engineering & Technology, Rajkot
Solution:
Given data:
r1 =10
2= 5 mm = 0.005 m, r2 = 5 + 2.5 = 7.5 mm = 0.0075 m
r3 = 5 + 7.5 = 12.5 mm = 0.0125 m, r4 = 5 + 15 = 20 mm = 0.02 m
k = 0.5 W mKβ , βπ = 50 π π2 πΎβ
L = 1 m, ti = β20 β, to = 25 β
Heat Transfer (3151909) 2. Steady State Heat Conduction
Department of Mechanical Engineering Prepared By: Mehul K. Pujara Darshan Institute of Engineering & Technology, Rajkot Page 2.47
i. Thickness of insulation beyond which heat gain will be reduced
Critical radius of insulation
rc = kβπ
β = 0.550β = 0.01 m = 10 mm
t = rc β r1 = 10 β 5 = 5 mm
ii. Heat loss for 2.5 mm thickness of insulation, Q1
Resistance of insulation
R1 =ln
π2π1
β
2πππΏ=
ln(0.00750.005β )
2π Γ 0.5 Γ 1= 0.129 K Wβ
Convection resistance of outside air
Ro =1
βππ΄π=
1
βπ2ππ2πΏ=
1
50 Γ 2π Γ 0.0075 Γ 1= 0.424 K Wβ
β΄ Q1 =π‘π β π‘π
π 1 + π π=
25 β (β20)
0.129 + 0.424= 81.37 π
iii. Heat loss for 7.5 mm thickness of insulation, Q2
Resistance of insulation
R2 =ln
π3π1
β
2πππΏ=
ln(0.01250.005β )
2π Γ 0.5 Γ 1= 0.291 K Wβ
Convection resistance of outside air
Ro =1
βππ΄π=
1
βπ2ππ3πΏ=
1
50 Γ 2π Γ 0.0125 Γ 1= 0.254 K Wβ
2. Steady State Heat Conduction Heat Transfer (3151909)
Prepared By: Mehul K. Pujara Department of Mechanical Engineering Page 2.48 Darshan Institute of Engineering & Technology, Rajkot
β΄ Q2 =π‘π β π‘π
π 2 + π π=
25 β (β20)
0.291 + 0.254= 82.56 π
iv. Heat loss for 15 mm thickness of insulation, Q3
Resistance of insulation
R3 =ln
π4π1
β
2πππΏ=
ln(0.020.005β )
2π Γ 0.5 Γ 1= 0.441 K Wβ
Convection resistance of outside air
Ro =1
βππ΄π=
1
βπ2ππ4πΏ=
1
50 Γ 2π Γ 0.02 Γ 1= 0.159 K Wβ
β΄ Q3 =π‘π β π‘π
π 3 + π π=
25 β (β20)
0.441 + 0.159= 75 π
Hence the insulation thickness of 15 mm is more effective
2.14 References: [1] Heat and Mass Transfer by D. S. Kumar, S K Kataria and Sons Publications.
[2] Heat Transfer β A Practical Approach by Yunus Cengel & Boles, McGraw-Hill
Publication.
[3] Principles of Heat Transfer by Frank Kreith, Cengage Learining.