geometric optimisation of conjugate cooling channels · pdf fileof conjugate cooling channels...
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1
GEOMETRIC OPTIMISATION
OF CONJUGATE COOLING
CHANNELS WITH DIFFERENT
CROSS-SECTIONAL SHAPES
Department of Mechanical and Aeronautical Engineering,
University of Pretoria, South Africa
By
Olabode Thomas OLAKOYEJO
Prof. T. Bello – Ochende, Prof. J. P. Meyer
13 : 02 : 2013
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Outline
• Introduction
• Background
• Motivation/Application
• Aims/Objective
• Objective functions
• Methodology
• Work done
• Results/Graphs
• Conclusions
• Future work
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• Heat generating devices, such as high power electronic equipment and heat exchangers are
widely applicable in engineering fields e.g electronic chip cooling, power and energy sectors.
• Heat generation can cause overheating problems and thermal stresses and may leads to
system failure.
• Cooling of heat generating device critical challenge to thermal design engineers and
researchers.
• Heat generating devices are designed in such a way as to optimise the structural geometry by
packing and arranging array of cooling channels into given and available volume constraint
without exceeding the allowable temperature limit specified by the manufacturers.
• This translates into the maximisation of heat transfer density or the minimisation of overall
global thermal resistance, which is a measure of the thermal performance of the cooling
devices.
Heat generating devices and Thermal management
Introduction
H
L
W
sq
s
d
Global Volume V elElemental Volume v
Flow
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Optimsation
parameters
Heat transfer
Performance
Characteristic
length scale
Conductive
heat transfer
Convective
heat transfer
H
L
W
sq
s
d
Global Volume V elElemental Volume v
Flow
hNu
k
Geometry
Shape
, , , hw h L d
Fig 1. The Nusselt Number (Nu) , a measure of heat transfer performance
Modern Heat Transfer: Geometry and Shape Optimisation
Introduction
Channel geometric design affects the thermal performance of Heat transfer
Geometry optimization of various shapes and sizes
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Backgrounds: Constructal Theory and Design
• Bejan and Sciubba (1992),considered the optimization spacing of board to board of an array of parallel plate that can be fitted in a fixed volume in an electronic cooling system
• Muzychka (2005), analytical optimisation the geometry of circular and non-circular cooling channels.
• Ordonez (2004), Numerically, conducted a two-dimensional heat transfer analysis in a heat-generated volume with cylindrical cooling channels and air as the working fluid.
H
L
W
sq
s
d
Global Volume V elElemental Volume v
Flow
2d
HWn
4/1683.4 BeL
dopt
2/1
3
2'''* BeC
TTk
LQQ
is
Fig 2. Convectively conducting volume with cooling channels
2sd
HWn
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Method of intersection of asymptotes
When the channel cross-sectional area is at optimum
inT
P
0h
d
When the channel cross-sectional area is large, D ∞
inT
P
When the channel characteristic dimension scale is small
and sufficiently slender, D 0, D << L
inT
P
Fig 3. Method of intersection of asymptotes
hd
0hd
h optd
H
L
W
sq
s
d
Global Volume V elElemental Volume v
Flow
hd
R
2 0h hR d d
2/3
h hR d d
hR d
opthd
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Motivations/Applications
• The advent of high density components has required investigation of innovative techniques for removing heat from these devices
• Better and optimal performance
• Cost minimization
Applications
• Electronic cooling
• Compact heat exchanger,
• Automotive
• Nuclear power
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Aims/Objectives
• Aim : To carry out theoretical and numerical optimization studies in conjugate
heat transfer in cooling channels with different cross-sections and under
varoius conditions
• Objectives : To minimise the dimensionless maximal excess of temperature or
global thermal resistance
The objectives will be conducted in two phases:
• Analytical (Theory) Analysis
• Numerical Analysis
• Optimisation process by suitable mathematical algorithm
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Part 1 : Optimisation of Conjugate Heat Transfer In Cooling Channels with
Internal Heat Generation for Different Cross-sectional Shapes
Part 2 : Optimisation of Laminar-forced Convection Heat Transfer
Through a Vascularised Solid with Cooling Channels
Part 3 : Effect of flow orientation on forced convective heat transfer in
cooling channel with internal heat generation
Research activities/work done
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PART 1
Optimisation of Conjugate Heat Transfer In Cooling Channels with Internal
Heat Generation for Different Cross-sectional Shapes
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Numerical Modelling: Problem under consideration
H
L
W
sq
s
d
Global Volume V elElemental Volume v
Flow
L
H
W
sq
s Global Volume V
elElemental Volume v
Flow
cw
L
Global Volume V
elElemental Volume v
W
H
sq
flow
Fluid
PinT
L
Global Volume V
elElemental Volume v
flow
Fluid
PinT
q
W
H
Fig 4. Three-dimensional parallel channels with different cross section across a slab
with internal heat generation and forced flow.
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Problem under consideration
flow
Fluid0
y
T
0
x
T
0
y
T
P
inT
0
z
T
hd
2
s
L
h
w
0T
z
flow
Fluid0
y
T
0
x
T
0
y
T
P
inT
0
z
T
0T
z
hd
cw2
s
L
h
w
hd
sq
L
w
h
flow
Fluid
P inT
0T
z
0T
z
Periodic
Periodic
Symmetry
cw
ch
2/ 2s
1/ 2s
0
y
T
Lw
ch
cw
h
0
x
T''', q
Solid
0
y
T
0
z
T
0
y
T
flowFluid
PinT
21s
22s
x
yz
Fig 5 The three dimensional computational domain Elemental volume with cooling
channels
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Objective functions and Assumptions
The objective is the minimisation of the global thermal resistance
max min
min 2
ink T T
fR
q L
min
min max, ,
opt opth elR f d v T
• Fluid flow and heat transfer :
• steady-steady state condition
• three dimensional.
• single phase
• Laminar
• Newtonian fluid with constant properties (Water)
• Micro-scale cooling channels
Assumptions
( P1.1)
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Numerical Modelling /Analysis/Optimisation
y
x
z
Fig 6: The discretised 3-D computational domain
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Numerical Modelling/Analysis
0u
2u u P u
2C u T k Tf Pf f
2 0k Ts
Govering Equations
Energy equation for a solid region is given as:
( P1.2)
( P1.3)
( P1.4)
( P1.5)
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Numerical Modelling/Analysis
– Unit cell using symmetry
– Internal heat generation
T T
k ks fn n
The continuity of the heat flux at the interface between the solid and the liquid
is given as
0u
A no-slip boundary condition is specified at the wall of the channel,
• Boundary Conditions
20, ,
Beu u T T P P
x y in in outL
At the inlet ( x = 0 )
1 P atmout
At the outlet ( x = L ), zero normal stress
At the solid boundaries
0T
( P1.6)
( P1.7)
( P1.8)
( P1.9)
( P1.10)
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Numerical Modelling/Analysis
Fig 7 The boundary conditions of the three dimensional Computational domain of the
cooling channel
Summary of Boundary Conditions
flow
Fluid0
y
T
0
x
T
0
y
T
P
inT
0
z
T
0T
z
hd
cw2
s
L
h
w
hd
sq
L
w
h
flow
Fluid
P inT
0T
z
0T
z
Periodic
Periodic
Symmetry
cw
ch
2/ 2s
1/ 2s
flow
Fluid0
y
T
0
x
T
0
y
T
P
inT
0
z
T
hd
2
s
L
h
w
0T
z
0
y
T
Lw
ch
cw
h
0
x
T''', q
Solid
0
y
T
0
z
T
0
y
T
flowFluid
PinT
21s
22s
x
yz
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The constraint ranges are:
Optimisation Constraints
0.1 0.2, 50 500 , 0 , 0 m w m d w s wh
2 , ,el hv w L w d s
An elemental volume constraint is considered to compose
of elemental cooling channel of hydraulic diameter
HWN
hw
The number of channels in the structure arrangement can be defined as:
c
el
v
v
The void fraction or porosity of the unit structure can be defined as:
flow
Fluid
L
0
y
T
w
0
x
T
0
y
T
PinT
Tk qs z
cw2
s
h
0T
z
x
y
z
ch
( P1.11)
( P1.12)
( P1.13)
( P1.14)
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Numerical analysis/ Grid independent tests
The numerical solution of the continuity, momentum and energy
Equations alongside with boundary conditions was obtained by
using a three dimensional commercial package FLUENT™
that employs a finite volume method.
The solution is said to be converged when
the normalized residual of the mass and
momentum equations falls below 10-6 and
that of the energy equation is less than 10-10.
Grid independent tests for several mesh
refinement were carried out to ensure
the accuracy of the numerical results.
The convergence criterion for the
overall thermal resistance as the
quantity monitored
1max max
max
0.01ii
i
T T
T
27
27.5
28
28.5
0 1
7500 Cells
68388 Cells
108750 Cells
Sta
tic T
em
pe
ratu
re (
0C
)
ZL
Fig 8 : Grid independent tests
( P1.15)
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0.001
0.0019
0 0.05 0.1
Be= 108
Pr = 1
Ordonez [15]
Present study
hd
L
300s
f
k
k
maxT
27
28
29
30
31
0 1 2 3 4 5
P = 50kPa
Cyl (
Sqr (
Cyl (
Sqr (
Cyl (
Sqr (T
max (
0C
)
vel ( mm
3 )
Fig 9a. Thermal resistance curves : present study
and ordoenez
Fig 9b Effect of optimised elemental
volume on the peak temperature
Numerical Results Findings /Graphs
max minT
Porosity Increasing
max minT
CASE STUDY 1: Cylindrical and square cooling channel
embedded in high-conducting solid
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Fig 10 Effect of optimised hydraulic diameter and spacing on the peak temperature
27
28
29
30
31
0 50 100 150 200 250 300 350
P = 50kPa Cyl (
Sqr (
Cyl (
Sqr (
Cyl (
Sqr (
Tm
ax (
0C
)
dh ( m )
27
28
29
30
31
0 100 200 300 400 500
P = 50kPa
Cyl (
Sqr (
Cyl (
Sqr (
Cyl (
Sqr (
Tm
ax (
0C
)
s ( m )
Numerical Results Findings /Graphs
max minT
Porosity Increasing max minTPorosity Increasing
CASE STUDY 1: Cylindrical and square cooling channel
embedded in high-conducting solid
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Numerical Results Findings /Graphs
CASE STUDY 2: Truagular cooling channel embedded in high-
conducting solid
28
30
0 3 6
I - R Triangle (
Equi Triangle (
I - R Triangle (
Equi Triangle (
Tm
ax (
0C
)
vel ( mm
3 )
28.5
30
0 0.015 0.03
I-R Triangle (
Equi Triangle (
I-R Triangle (
Equi Triangle (
Tm
ax (
0C
)
dh
/ L
Numerical Results Findings /Graphs
max minT
Porosity Increasing Porosity Increasing
max minT
Fig. 11 Effect of optimised hydraulic diameter and elemental volume on the peak temperature
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27.6
27.8
28
28.2
0 10 20
Tm
ax (
0C
)
ARc
27.6
27.8
28
28.2
0.012 0.018
Tm
ax (
0C
)
dh/L
Numerical Results Findings /Graphs
max minT max min
T
CASE STUDY 3: Rectangular cooling channel embedded in high-
conducting solid
Fig. 12. Effect of optimised aspect ratio and hydraulic diameter on the peak temperature
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Mathematical Optimisation:
• Standard optimization problem
2
0.1 0.2c h
el
v d
v w
optoptopth sdfR ,,min
DYNAMIC-Q Algorithm (by Prof. Snyman)
• Constraints
Porosity
min ; , ,.... ... , , 1 2
T nf x x x x X xi n i
x
0, 1,2,....j
g x j p
0, 1,2,....k
h x k q
Subject to
hoptd 0
hd
0 s
To search for the:
opts
( P1.16)
( P1.17)
( P1.18)
( P1.19)
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Mathematical Optimisation
• DYNAMIC-Q Algorithm Very robust
CFD simulation
converged?
Setting design variables
Importing geometry and mesh to
FLUENT
Post-processing:
data and results processing
Yes
No
FLUENT Journal file
3-D CFD simulation ( solving model)
FLUENT Journal file
CFD simulation ( solving model)
Defining the boundary conditions
Geometry & mesh generation
GAMBIT Journal file
Mathematical optimisation
( Dynamic-Q Algorithm )
Optimisation
solution converged?
Start
No
Yes
Initialise the optimisation by
specifying the initial guess of the
design variables xo
Stop
Predicted new optimum design
variables and objective function f(x)
1
2
1, 1,....
2
1, 1,....
2
Tl l l l lT
Tl l l l l lT
i i i i
Tl l l l l lT
j j j j
f x f x f x x x x x A x x
g x g x g x x x x x B x x i p
h x h x h x x x x x C x x j q
Gradient based method
• Penalty function technique
• Approximation of numerical functions
by spherical quadratic function
• Forward differencing for gradient approximations.
• Automation of the process
Fig. 13. flow chart of numerical simulation
( P1.20)
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Numerical Results Findings /Graphs
0, 1,2,....j
g x j p
10-5
10-4
10-3
109
1010
1011
Cyl (
Sqr (
Cyl (
Sqr (
Rm
in
Be
10-4
10-3
109
1010
1011
I-T Triangle (
E-T Triangle (
I-T Triangle (
E-T Triangle (
Rm
in
Be
Cylindrical, square , triangular and rectangular cooling channel
embedded in high-conducting solid
10-5
10-4
10-3
109
1010
1011
Rect ( Rect (
Rm
in
Be
Fig. 14 : Effect of dimensionless pressure difference on the minimised dimensionless global
thermal resistance
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Numerical Results Findings /Graphs
0, 1,2,....j
g x j p
0.008
0.009
0.01
0.02
0.03
109
1010
1011
Numerical Cyl (Numerical Cyl (Numerical Sqr (Numerical Sqr (Analytical results CylAnalytical results Sqr
(dh/L
) op
t
Be
Fig. 15 Effect of dimensionless pressure difference on optimised dimensionless hydraulic
diameter
10-2
10-1
109
1010
1011
I-T Triangle (
E-T Triangle (
I-T Triangle (
E-T Triangle (
dh
op
t /L
Be
0.01
0.012
0.014
0.016
0.018
0.02
109
1010
1011
Rect (
Rect (
dh
op
t /L
Be
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Fig. 16 Effect of dimensionless pressure difference on optimised dimensionless spacing
Numerical Results Findings /Graphs
10-1
100
109
1010
1011
I-T Triangle (
E-T Triangle (
I-T Triangle (
E-T Triangle (
( s
1/s
2 )
op
t
Be
10-2
10-1
100
109
1010
1011
Rect (
Rect (
( s
1/s
2 )
op
t
Be
0.007
0.008
0.009
0.01
0.02
109
1010
1011
sopt (um)cyl (0.1)
sopt (um)cyl (0.2)
sopt (um)sqr (0.1)
sopt (um)sqr (0.2)
(s/L
) opt
Be
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Analytical Solution
max 214
2
inh
od
h
k T Tdf
R P BeLq L
max 2 / 31/ 30.7643
2
inh
k T Tdf
R BeLq L
When the channel characteristic dimension scale is small
and sufficiently slender, D 0, D << L
inT
P
When the channel cross-sectional area is large, D ∞
inT
P
The hydraulic diameter becomes lager, the
global thermal resistance increases.
The hydraulic diameter becomes smaller, the
global thermal resistance increases.
(P1.21) (P1.22)
EXTREME LIMIT 1: SMALL CHANNEL EXTREME LIMIT 2: LARGE CHANNEL
Method of intersection of asymptotes for conjugate
channels with internal heat generation
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When the channel cross-sectional area is at optimum
inT
P
3/8 1/ 41.8602hod
hopt
dP Be
L
1/ 2 3/8 1/ 41.8602 1 1 o
dhopt
sP Be
L
min
1/ 4 1/ 21.156 od
h
R P Be
The geometric optimisation in terms of channel diameter could be achieved
by combining Eqs. (P1.21) and (P1.22) using the intersection of asymptotes
method as shown in
(P1.23)
(P1.24)
(P1.25)
Fig. 17: Intersection of asymptotes method
hd
R
2 0h hR d d
2/3
h hR d d
hR d
opthd
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Comparison of the Theoretical Method and
Numerical Optimisation
10-5
10-4
109
1010
1011
Numerical Cyl (
Numerical Sqr (
Numerical Cyl (
Numerical Sqr (
Analytical results Cyl
Analytical results Sqr
Rm
in
Be
10-5
10-4
109
1010
1011
I-T Triangle (
E-T Triangle (
I-T Triangle (
E-T Triangle (
Analytical results I-T Triangle
Analytical results E-T Triangle
Rm
in
Be
10-5
10-4
109
1010
1011
Rectangle (
Rectangle (
Analytical results
Rm
in
Be
Fig. 18 : Correlation of the numerical and analytical solutions for the minimised global
thermal resistance
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0.008
0.009
0.01
0.02
0.03
109
1010
1011
Numerical Cyl (Numerical Cyl (Numerical Sqr (Numerical Sqr (Analytical results CylAnalytical results Sqr
(dh/L
) op
t
Be
10-2
10-1
109
1010
1011
I-T Triangle (
E-T Triangle (
I-T Triangle (
E-T Triangle (
Analytical results I-T Triangle
Analytical results E-T Triangle
dh
op
t /L
Be
0.008
0.009
0.01
0.02
109
1010
1011
Rectangle (
Rectangle (
Analytical results
dh
opt
/L
Be
Comparison of the Theoretical Method and
Numerical Optimisation
Fig. 19: Correlation between the numerical and analytical solutions for the optimised
hydraulic diameter
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Comparison of the thermal performance of the cooling
channels shapes studied
10-4
10-3
109
1010
1011
Cyl (
Sqr (
I- R Triangle (
Equi Triangle ( Rect (
Cyl (
Sqr (
I - R Triangle (
Equi Triangle ( Rect (
Rm
in
Be
Fig. 20: Comparison of the thermal performance of the
cooling channels shapes studied
It was clearly observed that the cooling effect
was best achieved at a higher aspect ratio of
rectangular channels. However the optimal
design scheme could well lead to a design that
would be impractical at very high channel
aspect ratios, due to the channel being too thin
to be manufactured
flow
Fluid0
y
T
0
x
T
0
y
T
P
inT
0
z
T
hd
2
s
L
h
w
0T
z
0
y
T
Lw
ch
cw
h
0
x
T''', q
Solid
0
y
T
0
z
T
0
y
T
flowFluid
PinT
21s
22s
x
yz
hd
sq
L
w
h
flow
Fluid
P inT
0T
z
0T
z
Periodic
Periodic
Symmetry
cw
ch
2/ 2s
1/ 2s
Best
Poor
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Numerical Results : Temperature distribution
0, 1,2,....j
g x j p
Fig.21. Temperature distribution on (a) the elemental volume and (b) cooling fluid and inner wall.
(a) (b)
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Optimisation of Laminar-forced Convection Heat Transfer
Through A Vascularised Solid with Cooling Channels
PART 2
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Introduction
• Material with the property of self-healing and self-cooling is becoming
more promising in heat transfer analysis.
• The development of vascularisation of the material indicates flow architectures that conduct and
circulate fluids at every point within the solid body.
• This solid body (slab) may be performing or experiencing mechanical functions such as mechanical
loading, sensing and morphing.
• This self-cooling ability of the vascularised material to bathe at every point of a solid body gave
birth to the name “smart material”.
• a solid body of fixed global volume, which is heated with uniform heat flux on the right side; the
body is cooled by forcing a single-phase cooling fluid (water) from the left side into the parallel
cooling channels
L
H
W
s
v Global olume V v elElemental olume v
q
flow
Fluid
h c cd w h
HP
inTHeating
Fig 22. Three-dimensional parallel square channels across a slab with
heat flux from one side and forced flow from the other side.
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Objective functions and Assumptions
The objective is the minimisation of the global thermal resistance
max min
min
ink T T
fR
q L
min
min max, ,
opt opth elR f d v T
Assumptions as in part 1
( P2.1)
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Numerical Modelling /Analysis
y
x
z
Fig. 23: The discretised 3-D computational domain
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Numerical Modelling/Analysis
Governing Equations and BCs as in Part 1 except
2 0k Ts
Energy equation for a solid region is given as:
Tk qs z
• Boundary Conditions
L
H
W
s
v Global olume V v elElemental olume v
q
flow
Fluid
h c cd w h
HP
inTHeating
flow
Fluid
L
0
y
T
w
0
x
T
0
y
T
PinT
Tk qs z
cw2
s
h
0T
z
x
y
z
ch
– Unit cell using symmetry
– Heat flux input at the left side
( P2.2)
( P2.3)
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The constraint ranges are:
0.1 0.2, 0.02 0.5 , 0 , 0 L w L d w s wh
2 , , ,el hv w L h w w d s
An elemental volume constraint is considered to compose
of elemental cooling channel of hydraulic diameter
2
h
HWN
d s
The number of channels in the structure arrangement can be defined as:
2
c
el
dv h
v w
The void fraction or porosity of the unit structure can be defined as:
flow
Fluid
L
0
y
T
w
0
x
T
0
y
T
PinT
Tk qs z
cw2
s
h
0T
z
x
y
z
ch
L
H
W
s
v Global olume V v elElemental olume v
q
flow
Fluid
h c cd w h
HP
inTHeating
Optimisation Constraints
( P2.3)
( P2.4)
( P2.5)
( P2.6)
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25
33
42
50
1 101
102
(
(
(T
ma
x ( 0
C )
vel ( mm
3 )
Porosity increasing
30
40
50
0.01 0.1
(((
Tm
ax (
0C
)
dh/L
Porosity increasing
Fig. 24. Effect of optimised dimensionless hydraulic diameter and elemental volume on the
peak temperature
Numerical Results Findings /Graphs
max minT
0, 1,2,....j
g x j p
max minT
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Optimisation Results
Fig. 25 Effect of dimensionless pressure difference on the dimensionless thermal resistance
and the optimised hydraulic diameter
10-3
10-2
10-1
105
106
107
108
109
(((
Rm
in
Be
10-2
10-1
100
105
106
107
108
109
((
(
dh
op
t/L
Be
DYNAMIC-Q Algorithm
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Fig. 26. Effect of material properties on optimised
geometry minimised and thermal resistance
25
30
35
40
45
0 0.05 0.1
Be = 108
kr = 10
kr = 100
Tm
ax (
0C
)
dh/L
0
0.001
0.002
102
103
104
Be = 108
Rm
in
kr
0.03
0.04
0.05
102
103
104
Be = 108
dh
op
tn/L
kr
Numerical analysis/results : Effect of material properties
4000r
K
max minT
Kr Increasing
4000r
K
At higher thermal conductivity ratio, the thermal
conductivity has negligible effect on minimised
thermal resistance and optimised hydraulic diameter.
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0.01
0.1
1
106
107
108
Kr=1 (
Kr=1 (
Kr=10 (
Kr=10 (
Kr=100 (
Kr=100 (
so
pt/L
Be
0.01
0.1
1
106
107
108
Kr=1 (
Kr=1 (
Kr=10 (
Kr=10 (
Kr=100 (
Kr=100 (
dh
op
t/L
Be
0.001
0.01
0.1
1
106
107
108
Kr=1(
Kr=1(
Kr=10(
Kr=10(
Kr=100(
Kr=100(
Rm
in
Be
Fig. 27 Effect of material properties Kr on thermal resistance and optimised geometry
Optimisation Results
Effect of material properties Kr on thermal resistance
and optimised geometry
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Temperature Profile
Fig 28. Temperature distribution on (a) the elemental volume and (b) cooling fluid
and inner wall.
(a)
(b)
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Analytical Solution
EXTREME LIMIT 1: SMALL CHANNEL EXTREME LIMIT 2: LARGE CHANNEL
When the channel characteristic dimension scale is small
and sufficiently slender, D 0, D << L
inT
P
When the channel cross-sectional area is large, D ∞
inT
P
As the hydraulic diameter becomes larger,
the global thermal resistance increases. As the hydraulic diameter becomes smaller,
the global thermal resistance increases.
(P2.8) max in 1
232f
dk T T hR Beq L L
1 2max in 10.75 ,f h
r
k T T dR k
q L L
( P2.7)
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hd
maxT
When the channel cross-sectional area is at optimum
inT
P
The geometric optimisation in terms of channel diameter could be achieved by
combining Eqs. (P2.7) and (P2.8) using the Intersection of asymptotes method
as shown in Fig. 9.
Fig. 29: Intersection of asymptotes method
1 6 1 3 1 33.494opth
r
dk Be
L
max 0hT d
max hT d
max h optT d
opthd
Analytical Solution
2 3max in 1 3minmin 2.62 ,
f
r
k T TR k Be
q L
( P2.9)
( P2.10)
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Optimisation Results
Effect of material properties Kr on optimised geometry
10-3
10-2
10-1
105
106
107
108
109
kr = 1
kr = 10
kr = 100
kr = 1
kr = 10
kr = 100
Analytical results
Rm
in (k
r)2/3
Be
10-3
10-2
10-1
105
106
107
108
109
kr = 1
kr = 10
kr = 100
kr = 1
kr = 10
kr = 100
Analytical results
( dh
op
t/L )
(k
r)-1/3
Be
10-3
10-2
10-1
105
106
107
108
109
kr = 1
kr = 10
kr = 100
kr = 1
kr = 10
kr = 100
Analytical results
( s
op
t/L )
(
kr)-1
/3
Be
Fig. 30 : Correlation of the numerical and analytical solutions for the minimised global
thermal resistance
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PART 3
Effect of flow orientation on forced convective heat transfer
in cooling channel with internal heat generation
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H
L
W
hd
Flow
sq
s
Global Volume V elElemental Volume v
H
L
W
hd
Flow
sq
s
Global Volume V elElemental Volume v
H
L
W
hd
Flow
sq
s
Global Volume V elElemental Volume v
hd
L
w
sh
flow
Fluid
P inT
0T
z
0T
z
Periodic
Periodic
sq
s
Introduction : Numerical Anaysis
The array of channels with
parallel flow refer as PF-1.
The array of channels in
which flow of the every
other row channel is in
counter direction to one
another refer as CF-2 .
The every flow in the array
of channels is in counter
direction to one another,
refers as CF-3
hd
L
w
sh
flow
Fluid
P inT
0T
z
Symmetry
0T
z
Symmetry
sq
s
hd
L
w
sh
flow
Fluid
P inT
0T
z
0T
z
Periodic
Periodic
sq
Fig. 31 : Three dimensional parallel circular of PF-1, CF-2 and CF-3
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Objective functions and Assumptions
The objective is the minimisation of the global thermal resistance
Assumptions as in part 1
max min
min 2
ink T T
fR
q L
minmin max, , , ,
opt opth opt elR f d s v T flow orientation
( P3.1)
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Numerical Modelling /Analysis
x
yz
Fig 32. The discretised 3-D computational domain
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Numerical Modelling/Analysis
Governing Equations as in Part 1
Fig. 33 The boundary conditions of the three dimensional Computational domain of the
cooling channel
Boundary Conditions
hd
L
w
sh
flow
Fluid
P inT
0T
z
Symmetry
0T
z
Symmetry
sq
s
hd
L
w
sh
flow
Fluid
P inT
0T
z
0T
z
Periodic
Periodic
sq
s
hd
L
w
sh
flow
Fluid
P inT
0T
z
0T
z
Periodic
Periodic
sq
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The constraint ranges are:
3 30.125mm 20mm , 0.1 0.3, 0 , 0 , 0 el
v w L d w s wh
2 , , ,el hv w L h w w d s
An elemental volume constraint is considered to compose
of elemental cooling channel of hydraulic diameter
The number of channels in the structure arrangement can be defined as:
4 c
el
v
v
The void fraction or porosity of the unit structure can be defined as:
2
4c hv d L
sA HW
For a fixed length of the channel, the cross-sectional area of the structure is
HW
Nhw
Optimisation Constraints
( P3.2)
( P3.3)
( P3.4)
( P3.5)
( P3.6)
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27
27.5
28
28.5
29
29.5
30
30.5
0.005 0.01 0.015 0.02 0.025 0.03 0.035
PF-1 (
CF-2 (
CF-3 (
PF-1 ( CF-2 (
CF-3 (
PF-1 (
CF-2 ( CF-3 (
Tm
ax (
0C
)
dh/L
Porosity increasing27
27.5
28
28.5
29
29.5
0 2 4 6 8 10 12 14
PF-1 (
CF-2 (
CF-3 ( PF-1 (
CF-2 (
CF-3 (
PF-1 (
CF-2 ( CF-3 (
Tm
ax (
0C
)
vel ( mm )
Porosity increasing
Numerical Results
max minT
max minT
Fig. 34 Effect of optimised dimensionless hydraulic diameter and elemental volume on the peak
temperature
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10-5
10-4
10-3
109
1010
1011
PF-1 (
CF-2 (
CF-3 (
PF-1 ( CF-2 (
CF-3 (
PF-1 (
CF-2 (
CF-3 (
Rm
in
Be
0.01
0.02
0.03
0.04
109
1010
1011
PF-1 (
CF-2 (
CF-3 (
PF-1 ( CF-2 (
CF-3 (
PF-1 (
CF-2 (
CF-3 (
dh
op
t /L
Be
0.001
0.01
0.1
109
1010
1011
PF-1 (
CF-2 (
CF-3 (
PF-1 ( CF-2 (
CF-3 (
PF-1 (
CF-2 (
CF-3 (
sop
t /L
Be
Numerical Results
Fig. 35 Effect of dimensionless pressure difference on the dimensionless thermal resistance
and the optimised geometries
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Conclusion : Part 1
• Size and shapes significant have effect on the thermal performance of heat-generating devices.
• The global thermal resistance is a function of applied dimensionless pressure difference number
(pumping power) and the channel configurations.
• Existence of unique optimal design variables for a given applied dimensionless pressure number for
each configuration studied.
• Therefore, thermal designers can pick an optimal solution according to the applied dimensionless
pressure difference number (Be) available to drive the fluid or thermal resistance required.
• The cooling effect was best achieved at a higher aspect ratio of rectangular channels. The performance
of the cylindrical channel was poorer than that of any other channels, it was a more viable option and
more often used in industry due to the ease of manufacturability and packaging.
• The optimal channel spacing ratio (s1/s2) remains unchanged and insensitive to the performance of the
system regardless of the pressure difference number for the two triangular configurations
• The optimal design scheme could well lead to a design that would be impractical at very high channel
aspect ratios, due to the channel being too thin to be manufactured
It is all about size and shapes
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Conclusion : Part 2
• This part studied the numerical optimisation of geometric structures of square cooling
channels of vascularised material with the localised self-cooling property subject to heat
flux on one side in such a way that the peak temperature is minimised at every point in
the solid body.
• There is existence of unique optimal design variables (geometries) for a given applied
dimensionless pressure number for fixed porosity.
• Minimized thermal resistance decreases with increasing Kr and Be. That is the material
property and driving force have great influence on the performance of the cooling channel.
Therefore, when designing the cooling structure of vascularised material, the internal and
external geometries of the structure, material properties and pump power requirements are
very important parameters to be considered in achieving efficient optimal designs for the
best performance.
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• The results also show that the flow orientation has a strong influence on the convective heat
transfer.
• For specified applied dimensionless pressure difference and porosity, CF-2 and CF-3
orientations perform better than the PF-1 orientation.
• Therefore, when designing the cooling structure of heat exchange equipment, the internal
and external geometries of the structure, flow orientation and the pump power requirements
are very important parameters to be considered in achieving efficient and optimal designs
for the best performance.
• The thermal designers can pick an optimal solution according to the applied dimensionless
pressure difference number (Be) available to drive the fluid or thermal resistance required.
Conclusion : Part 3
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min, , 1 , 2 , , ,
hopt hopt opt opt opt opt optR f D d L L w
c
el
v
v
2D d D d
Recommendation for Future work
• Circular Y-shape cooling channel
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Recommendation for Future work
• Multi-scale design of compact cooling channels
H
L
W
sq
s Global Volume V elElemental Volume v
FlowhD
Flowh
d
Future model
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Recommendation for Future work
• Effect of temperature-dependent of the thermo-physical properties of fluid on
the minimised thermal resistance.
sensitive to temperature changes due to relatively large variation of working
fluid properties at high heat flux and low Reynolds number (Re).
min( ( ), ( ), ( ))R f T T k T
• Turbulent and transient fluid flow.
• Investigation of the effect of pin fins of any shape transversely arranged
along the flow channel of the configurations on the temperature distribution
and dimensionless pressure difference characteristics with the global objective
of minimising thermal resistance and improving thermal performance.
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The following articles, book chapter and conference papers were produced during this research.
1. O.T. Olakoyejo, T. Bello-Ochende and J.P Meyer, “Mathematical optimisation of laminar forced
convection heat transfer through a vascularised solid with square channels”, International Journal
of Heat and Mass Transfer, Vol. 55, pp. 2402-2411, 2012. ( Published)
2. O.T. Olakoyejo, T. Bello-Ochende and J.P Meyer; “Constructal conjugate cooling channels with
internal heat generation”, International Journal of Heat and Mass Transfer, Vol. 55, pp. 4385-4396,
2012. ( Published)
3. T. Bello-Ochende, O.T. Olakoyejo and J.P Meyer, Chapter 11, “Constructal Design of Rectangular
Conjugate Channels” Published in the book, “Constructal Law and the Unifying Principle of
Design”, L.A.O Rocha, S. Lorente and A. Bejan, eds., pp. 177-194, Springer Publishers, New York,
2012. ( Published)
4. J.P Meyer, O.T. Olakoyejo, and T. Bello-Ochende; “Constructal optimisation of conjugate
triangular cooling channels with internal heat generation”, International communication of Heat and
Mass Transfer, Vol. 39, pp. 1093 - 1100, 2012. (Published).
List of Publications from the Research
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5. T. Bello-Ochende, O.T. Olakoyejo, and J.P Meyer; “Constructal flow orientation in conjugate
cooling channels with internal heat generation”, International Journal of Heat and Mass Transfer,
Vol. 57, pp. 241 - 249, 2013. (Published).
6. O.T. Olakoyejo, T. Bello-Ochende and J.P Meyer, “Optimisation of circular cooling channels with
internal heat generation”, Proceedings of the 7th International Conference on Heat Transfer, Fluid
Mechanics and Thermodynamics, Antalya, Turkey, pp. 1345-1350, 19-21 July 2010. ( Presented)
7. O.T. Olakoyejo, T. Bello-Ochende and J.P Meyer, “Geometric Optimisation of Forced Convection
In Cooling Channels With Internal Heat Generation Proceedings of the 14th International Heat
Transfer Conference, Washington D.C, USA, pp. 1345-1350, 8 -13 August 2010. ( Presented)
8. O.T. Olakoyejo, T. Bello-Ochende and J.P Meyer, “Geometric optimisation of forced convection in
a vascularised material”, Proceedings of the 8th International Conference on Heat Transfer, Fluid
Mechanics and Thermodynamics, Pointe Aux Piments, Mauritius, pp. 38 - 43, 11-13 July, 2011
(Presented and awarded best paper of the session).
List of Publications from the Research
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9. O.T. Olakoyejo, T. Bello-Ochende and J.P. Meyer, “Constructal optimisation of rectangular
conjugate cooling channels for minimum thermal resistance”, Proceedings of the Constructal Law
Conference, 01-02 December, 2011, Porto Alegre, Universidade Federal do Rio Grande do Sul,
Brazil. ( Presented)
10. O.T. Olakoyejo, T. Bello-Ochende and J.P Meyer, “Optimisation of conjugate triangular cooling
channels with
internal heat generation”, 9th International Conference on Heat Transfer, Fluid Mechanics and
Thermodynamics, Malta, 16 -18 July, 2012. (Presented)
9. O.T. Olakoyejo, T. Bello-Ochende and J.P Meyer, “Flow orientation in conjugate cooling channels
with internal heat generation”, 9th International Conference on Heat Transfer, Fluid Mechanics and
Thermodynamics, Malta, July 16 – 18, 2012. (Presented).
List of Publications from the Research
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Acknowledgments
• Supervisors :
- Prof. T. Bello-Ochende
- Prof. J.P. Meyer.
Prof Leon Liebenberg
Profs. Bejan and Lorente
Prof. Snyman (Emeritus)
Academic and non-academic staff
Thermo-fluid research students
Friends.
• The Almighty God
• Parents and Siblings
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