2. Steady-State
andOne
Dimension
HeatTransfer
Heat loss through a wall
Isothermal
Heat conduction in a medium can be;
one-dimensional
multi-dimensional (two dimensional or three dimensional)
Heat transfer problems are often classified as being:
steady (also called steady state) 𝑄𝑐𝑜𝑛𝑑,𝑤𝑎𝑙𝑙 = 𝑐𝑜𝑛𝑠𝑡𝑎𝑛𝑡
transient (also called unsteady).
3. The Plane
Wall
Heat flow in a normal direction
Isothermal temperature at all points of the wall
Heat transfer steady and one dimensional
𝑇1 and 𝑇2 are constant – steady flow rate
𝑄𝑐𝑜𝑛𝑑,𝑤𝑎𝑙𝑙 = −𝑘𝐴
𝑑𝑇
𝑑𝑥
(𝑊)
𝑄𝑐𝑜𝑛𝑑,𝑤𝑎𝑙𝑙 = 𝑘𝐴
𝑇1−𝑇2
𝐿
(𝑊)
Wall parameters: k, A and L
4. TheThermal
Resistance
Concept
Heat conduction through a plane wall
𝑄𝑐𝑜𝑛𝑑, 𝑤𝑎𝑙𝑙 =
𝑇1−𝑇2
𝑅𝑤𝑎𝑙𝑙
(W) 𝑅𝑤𝑎𝑙𝑙 =
𝐿
𝑘𝐴
- thermal resistance of the wall against
heat conduction or conduction resistance of the wall
Newton’s law of cooling for convection heat transfer rate
𝑄𝑐𝑜𝑛𝑣 = ℎ𝐴𝑠 𝑇𝑠 − 𝑇∞ 𝑄𝑐𝑜𝑛𝑣 =
𝑇1−𝑇2
𝑅𝑐𝑜𝑛𝑣
𝑅𝑐𝑜𝑛𝑣 =
1
ℎ𝐴𝑠
-thermal resistance of
the surface against heat convection or convection resistance of the surface
ℎ → ∞; 𝑅𝑐𝑜𝑛𝑣 = 0
For radiation
𝑄𝑟𝑎𝑑 = 𝜀𝜎𝐴𝑠 𝑇𝑠
4 − 𝑇𝑠𝑢𝑟𝑟
4 = ℎ𝑟𝑎𝑑𝐴𝑠 𝑇𝑠 − 𝑇𝑠𝑢𝑟𝑟 =
𝑇𝑠−𝑇𝑠𝑢𝑟𝑟
𝑅𝑟𝑎𝑑
𝑅𝑟𝑎𝑑 =
1
ℎ𝑟𝑎𝑑𝐴𝑠
- thermal resistance of the surface against radiation
ℎ𝑟𝑎𝑑 =
𝑄𝑟𝑎𝑑
𝐴𝑠 𝑇𝑠−𝑇𝑠𝑢𝑟𝑟
= 𝜀𝜎 𝑇𝑠
2 − 𝑇𝑠𝑢𝑟𝑟
2 𝑇𝑠 − 𝑇𝑠𝑢𝑟𝑟 (𝑊 𝑚2 . 𝐾) – radiation
heat transfer coefficient
ℎ𝑐𝑜𝑚𝑏𝑖𝑛𝑒𝑑 = ℎ𝑐𝑜𝑛𝑣 + ℎ𝑟𝑎𝑑 - combined heat transfer coefficient (conv + rad)
5. Thermal
Resistance
Network
Therefore, the rate of steady heat transfer between
two surfaces is equal to the temperature difference
divided by the total thermal resistance between
those two surfaces.
6. TheOverall
Heat-Transfer
Coefficient
𝑄 =
𝑇∞1−𝑇∞2
𝑅𝑡𝑜𝑡𝑎𝑙
𝑄 = ∆𝑇 𝑅 the larger the resistance, the larger the
temp drop.
Expressing heat transfer through a medium as
Newton’s law of cooling
𝑄 = 𝑈𝐴∆𝑇 where U is the overall heat transfer
coefficient.
𝑈𝐴 =
𝑄
∆𝑇
𝑛𝑜𝑡𝑒 𝑡ℎ𝑎𝑡
𝑄
∆𝑇
=
1
𝑅𝑡𝑜𝑡𝑎𝑙
∴ 𝑈𝐴 =
1
𝑅𝑡𝑜𝑡𝑎𝑙
Therefore, for a unit area, the overall heat transfer
coefficient is equal to the inverse of the total
thermal resistance.
No need to know the surface temperatures of walls
to calculate the rate of steady heat transfer.
7. Multilayer
PlaneWalls
Total thermal
resistance
Different thermal
conductivities
Determining temp of
any surface
Temp drop across a
layer:
∆𝑇 = 𝑄𝑅
𝑄 - constant, steady
heat transfer with no
heat generation
8. Thermal
Contact
Resistance
Thermal contact resistance, 𝑅𝑐 is the resistance to heat transfer per unit
interface area that arises when surfaces are pressed against each other.
Air gaps act as insulators because of the low thermal conductivity of air.
𝑅𝑐, determined experimentally
Heat transfer through the interface: 𝑄 = 𝑄𝑐𝑜𝑛𝑡𝑎𝑐𝑡 + 𝑄𝑔𝑎𝑝 OR
𝑄 = ℎ𝑐𝐴∆𝑇𝑖𝑛𝑡𝑒𝑟𝑓𝑎𝑐𝑒 where ℎ𝑐 - thermal contact conductance
ℎ𝑐 =
𝑄 𝐴
∆𝑇𝑖𝑛𝑡𝑒𝑟𝑓𝑎𝑐𝑒
𝑊 𝑚2
.𝑂
𝐶 : 𝑅𝑐 =
1
ℎ𝑐
=
∆𝑇𝑖𝑛𝑡𝑒𝑟𝑓𝑎𝑐𝑒
𝑄 𝐴
𝑚2
.𝑂
𝐶/𝑊)
The thermal contact resistance (𝑅𝑐) for the entire interface is obtained by
dividing 𝑅𝑐 by the apparent interface area A.
Factors affecting thermal contact resistance:
- surface roughness - material properties – temperature and pressure at the
interface - type of fluid trapped at the interface - *bolts, screws, rivets
Good conductors vs insulators for thermal contact resistance
Minimizing thermal contact resistance:
- Using thermally conducting liquid (thermal grease) – replace the air at the
interface with better conducting gas (helium/hydrogen) – insert a soft
metallic foil (tin/silver/nickel/aluminum) between the two surfaces
9. Generalized
Thermal
Resistance
Networks
Parallel layers or combined series-parallel arrangements.
Results are approximate (isothermal, heat transfer btn 1+2)
Assumptions in solving multidimensional heat transfer problems:
any plane wall normal to the x-axis is isothermal
any plane parallel to the x-axis is adiabatic
10. Heat
Conduction in
Cylinders and
Spheres
Fourier’s law of heat conduction for heat transfer through the cylindrical
layer can be expressed as:
𝑄𝑐𝑜𝑛𝑑, 𝑐𝑦𝑙 = −𝑘𝐴
𝑑𝑇
𝑑𝑟
(𝑊) where 𝐴 = 2𝜋𝑟𝐿
𝑄𝑐𝑜𝑛𝑑, 𝑐𝑦𝑙 = 2𝜋𝐿𝑘
𝑇1−𝑇2
ln(𝑟2 𝑟1)
𝑄𝑐𝑜𝑛𝑑,𝑐𝑦𝑙 =
𝑇1−𝑇2
𝑅cy𝑙
(𝑊)
𝑅cy𝑙 =
ln(𝑟2 𝑟1)
2𝜋𝐿𝑘
=
ln(𝑜𝑢𝑡𝑒𝑟 𝑟𝑎𝑑𝑖𝑢𝑠 𝑖𝑛𝑛𝑒𝑟 𝑟𝑎𝑑𝑖𝑢𝑠)
2𝜋×𝐿𝑒𝑛𝑔𝑡ℎ×𝑇ℎ𝑒𝑟𝑚𝑎𝑙 𝑐𝑜𝑛𝑑𝑢𝑐𝑡𝑖𝑣𝑖𝑡𝑦
- is the thermal
resistance of the cylindrical layer against heat conduction, or conduction
resistance of the cylinder layer.
Fourier’s law of heat conduction for heat transfer through a spherical
layer can be expressed as:
𝑄𝑐𝑜𝑛𝑑, 𝑠𝑝ℎ = −𝑘𝐴
𝑑𝑇
𝑑𝑟
(𝑊) where 𝐴 = 4𝜋𝑟2
𝑄𝑐𝑜𝑛𝑑, 𝑠𝑝ℎ = 4𝜋𝑟2𝑟1𝑘
𝑇1−𝑇2
𝑟2−𝑟1
𝑄𝑐𝑜𝑛𝑑, 𝑠𝑝ℎ =
𝑇1−𝑇2
𝑅cy𝑙
(𝑊)
𝑅sph =
𝑟2−𝑟1
4𝜋𝑟2𝑟1𝑘
=
𝑜𝑢𝑡𝑒𝑟 𝑟𝑎𝑑𝑖𝑢𝑠 −𝑖𝑛𝑛𝑒𝑟 𝑟𝑎𝑑𝑖𝑢
4𝜋×𝑜𝑢𝑡𝑒𝑟 𝑟𝑎𝑑𝑖𝑢𝑠×𝑖𝑛𝑛𝑒𝑟 𝑟𝑎𝑑𝑖𝑢𝑠×𝑇ℎ𝑒𝑟𝑚𝑎𝑙 𝑐𝑜𝑛𝑑𝑢𝑐𝑡𝑖𝑣𝑖𝑡𝑦
- is the
thermal resistance of the spherical layer against heat conduction, or
conduction resistance of the spherical layer.
12. Critical Radius
of Insulation
𝑄𝑐𝑜𝑛𝑣 = ℎ𝐴𝑠 𝑇𝑠 − 𝑇∞ : 𝑄𝑐𝑜𝑛𝑑 = −𝑘𝐴
𝑑𝑇
𝑑𝑥
Insulation, heat transfer area, thermal resistance
Increase in conduction resistance, decrease in
convection resistance
Critical radius of insulation of a cylindrical body,
𝑟𝑐𝑟,𝑐𝑦𝑙𝑖𝑛𝑑𝑒𝑟 =
𝑘
ℎ
(𝑚)
Critical radius of insulation of a spherical body,
𝑟𝑐𝑟,𝑠𝑝ℎ𝑒𝑟𝑒 =
2𝑘
ℎ
(𝑚)
Critical radius less in forced convection
Radius of electric wires - safety
13. HeatTransfer
From Finned
Surfaces
𝑄𝑐𝑜𝑛𝑣 = ℎ𝐴𝑠 𝑇𝑠 − 𝑇∞
𝑄𝑐𝑜𝑛𝑑 = −𝑘𝐴
𝑑𝑇
𝑑𝑥
• Fins – highly conductive material like aluminum
• Extruding, welding, or wrapping a thin metal sheet on a surface
• Assumptions: - steady operation – no heat generation – thermal
conductivity of material is constant – heat transfer coefficient, h is
constant and uniform over fin surface
• Many fins may decrease the overall heat transfer
14. Ref:
Yunus A. Cengel, (2000). HeatTransfer,A PracticalApproach,
Second Edition.