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1 Copyright © 2015 by ASME
Proceedings of the ASME 2015 International Mechanical Engineering Congress & Exposition IMECE15
November 13-19, 2015, Houston, Texas, USA
IMECE2015-54166
MULTI-OBJECTIVE OPTIMIZATION OF MICRO PIN-FIN ARRAYS FOR
COOLING OF HIGH HEAT FLUX ELECTRONICS
Sohail R. Reddy Florida International University
Department of Mechanical and Materials Eng., MAIDROC Laboratory, Miami, FL 33174, USA.
George S. Dulikravich Florida International University
Department of Mechanical and Materials Eng., MAIDROC Laboratory, Miami, FL 33174, USA.
ABSTRACT
The thermal management capability of various candidates of
micro-pin fin arrays is investigated. An integrated circuit having
a footprint of 4 x 3 mm with micro-pin fin array having circular,
airfoil and convex cross-section is considered. The three pin fin
cross-sections along with the cooling schemes are optimized to
handle a uniform heat flux of 500 W/cm2 applied to the top
surface of the electronic chip. A fully three-dimensional, steady-
state conjugate heat transfer analysis was performed on each
cooling configuration and a constrained multi-objective
optimization was carried out for each of the three micro-pin fin
shapes to find pin fin designs configurations capable of cooling
such high heat fluxes. The design variables were the geometric
parameters defining each pin fin cross section, height of the chip
and inlet speed of the coolant. The two simultaneous objectives
were to minimize maximum temperature and pressure drop
(pumping power), while keeping the maximum temperature
below 85oC. A response surface was constructed for each
objective function and was coupled with a genetic algorithm to
arrive at a Pareto frontier of the best trade-off solutions. Stress-
deformation analysis incorporating the hydrodynamic and
thermal loads was performed on each of the three optimized
configurations. The maximum displacement was found to be on
the nano-level, and the Von-Mises stress for each configuration
was found to be significantly below the yield strength of Silicon.
INTRODUCTION
A continuous growth in the demand of computing power
from electronic chips has led to extremely high production of
heat. The performance of cooling systems is quickly turning into
a major limiting factor in modern electronic devices. There are
various methods of cooling electronics, such as micro-channels,
micro-jets and spray cooling, to name a few. An alternative
method for thermal management in integrated circuits is the use
of micro-pin fins. Benefits of micro-pin fins include higher heat
removal capacity and compact packaging of chips since they
allow for stacking. Micro-pin fins not only acts as heat sinks but
also allow for interconnection between stacked layers of chips
due to the Through-Silicon Vias (TSV) housed inside.
Numerous authors have previously investigated various
methods of cooling. Abdoli et al. [1] carried out conjugate heat
transfer analysis on two floor, single phase flow in micro
channels to study their effects in cooling chips with hotspots. Wu
and Mudawar [2] investigated the thermal management
capabilities of heat sinks with rectangular cross-sections. Their
work considered a heat flux of 90 W cm-2 applied uniformly on
the top surface. In other research, Abdoli et al. [3] also
investigated single-floor and double-floor, various micro-pin fin
configurations and their ability to cool high heat flux chips with
hotspot. They investigated circular, airfoil and convex lens
shaped micro-pin fin arrays and their effects on temperature and
pumping power. It was shown that the convex shape require less
pumping power while offering similar performance in thermal
management. Alfieri et al. [4] numerically studied the effects of
size and distribution of pin fins on the thermal performance of
3D stacked circuits with integrated cooling. In another work,
Alfieri et al. [5] computationally modelled the vortex shedding
in water-cooled array of micro-pin fins. Their work showed that
even at low Reynolds number, vortex shedding is present.
In previous optimization work, Jelisavcic et al. [6] and
Gonzales et al. [7] found an optimum configuration of network
of cooling passages. Abdoli and Dulikravich [8, 9, 10, 11] also
optimized multi-floor microchannel configurations. Fabbri and
Dhir [12] optimized an array of microjet for cooling of high
performance electronics. Their work showed that a maximum
heat flux of 310 W/cm2 is attainable while keeping the maximum
temperature below a threshold. Tullius et al. [13] performed
parametric optimization of six micro-pin fin cross-sections that
lead to important correlations between geometric parameters,
Nusselt number and heat transfer coefficients. It can be seen that
optimization studies have previously been carried out but very
few efforts have been dedicated to find an optimum
configuration for micro-pin fin heat sinks.
An optimization study was carried out to find an optimum
shape for each of the three micro-pin fin geometries to handle a
2 Copyright © 2015 by ASME
uniform heat flux of 500 W cm-2 while keeping the maximum
temperature below 85oC. The simultaneous objectives include
minimizing maximum temperature while minimizing the inlet
pressure. The minimization of inlet pressure results in reduced
pumping power. A heat flux of 500 W cm-2 was chosen as a
realistic projection of future heat dissipation requirements, as
typical electronic chips experience heat fluxes around 100 W cm-
2. The optimization was carried out in a commercial software
modeFRONTIER [14] and involved a response surface coupled
with a genetic algorithm to arrive at a Pareto frontier. Figure 1
shows the typical micro-pin fin configuration used in this study.
Figure 1: Dimension of the chip used in this study
CONJUGATE HEAT TRANSFER ANALYSIS
The thermal management capabilities of the three proposed
micro-pin fin shapes were previously investigated by Abdoli et
al. [3]. Unlike the heat flux in this work which if uniform, Abdoli
et al. [3] applied a non-uniform heat flux featuring a hot spot.
Reddy et al. [15] optimized the proposed pin fin shapes for a
background heat flux of 500 W cm-2 and a hot spot heat flux of
1000 W cm-2.
Figure 2 shows the three pin fin shapes considered in this
study. Each configuration analyzed in this work was fitted with
special pin-fins at the outlet to increase heat transfer at the outlet
and suppress backflow.
a)
b)
c)
Figure 2. A micro pin-fin cooling configuration with pins having: a) circular, b) airfoil, and c) symmetric convex cross sections.
Figure 3 shows typical hybrid computational grids of
approximately seven to eight million cells, used for each
conjugate heat transfer analysis. A total of four layers of
structured cells were placed on each solid-fluid interface. The
minimum allowable length scale for the computational mesh was
one micron, to satisfy continuum so that the Reynolds Averaged
Navier-Stokes (RANS) [16] equations can be solved in the fluid
domain. The standard k-e turbulence model was used to model
vortex shedding displayed by Alfieri et al. [5]. This model was
chosen due to it stability and good convergence.
a) b)
c)
Figure 3. Typical hybrid structured/non-structured 3D computational grid for arrays of micro pin-fins having: a) circular, b) symmetric airfoil, and c) symmetric convex cross sections.
The mass and linear momentum balances are given as
0=⋅∇ Vr
(1)
ρr
V ⋅∇( )
r
V = ∇⋅ − pt
1+ µ ∇r
V +r
∇V( )T
( )
(2)
The energy balance for incompressible flows, neglecting viscous
dissipation and heat sources) takes the form
( ) ( ) ( )TkpVTVCp
∇⋅∇+∇⋅=∇⋅rr
ρ (3)
4 mm
1.5 mm
Line of Symmetry
Chord
Length
Thickness
3 Copyright © 2015 by ASME
The solid domain consists of the micro-pin fins and the
sidewalls. The steady-state heat equation was solved for the solid
domain, where k is the thermal conductivity and T is the absolute
temperature.
( ) 0=∇⋅∇ Tk (4)
Stress-deformation analysis was also performed on the three
optimized configuration to investigate the effect of
hydrodynamic and thermal loads on the configurations. The
conservation of momentum for an isotropic solid body element
is written as
2
2
u.σ F 0
tρ∂
−∇ − =∂ (5)
The stress tensor, σ, for a linear elastic solid is written as
σ 2G tr( ) Iε λ ε= + (6)
where G and λ are the modulus of elasticity and the first Lame
coefficient, respectively.
The strain tensor is defined as
v
1[ u ( u) ] ( T )I
2= ∇ + ∇ + ∆
Τε α
(7)
where
0T T T∆ = −
(8)
A computational grid of approximately 12-million grid cell
was used for each stress-deformation analysis.
PROBLEM FORMULATION
The gains in performance reported by Abdoli et al. [3] can
further be increased through an optimization study. The multi-
objective optimization in this work was carried out in the
commercial package, modeFRONTIER [14]. Three design
variables were used to define the circular pin fins configurations:
inlet velocity, diameter and pin fin height. The airfoil and convex
pin fin cooling configurations were defined using the inlet
velocity, pin fin height, chord length and thickness. The airfoil
profile was defined using a four series, NACA 00XX series
airfoil. The thickness of all sidewalls of the electronic chip were
held constant at 30 ��.
A gauge pressure of 20kPa was applied at the outlets since
most electronic cooling configurations are pressurized to avoid
cavitation. The inlet temperature of the water is held constant at
30oC. A heat flux of 500 W cm-2 was uniformly applied to the
top surface of all configurations. The bottom and sidewalls were
thermally insulated.
Table 1 shows the range and step size of each variable used
to define the three pin fin configurations. The ranges were
selected so as to avoid self-intersecting geometries.
Table 1. Range for design variables defining the pin-fin configuration.
Design Variable Range Step size
Inlet velocity (m/s) 1 - 5 0.2
Height of pin-fins (µm) 100 – 250 50
Diameter of circular pin-fins
(µm)
100 – 200 10
Chord length of pin-fins (µm) 200 – 300 10
Thickness of pin-fins (µm) 80 - 160 10
MULTI-OBJECTIVE OPTMIZATION
The optimization performed in this study features two
objectives:
1. Minimize maximum temperature
2. Minimize inlet pressure (pumping power)
A total of three optimization runs were performed, one for each
pin fin shape.
Figure 4 shows the various software packages used and the
optimization workflow used in this study. The computational
grids were created in ANSYS Meshing® and the conjugate heat
transfer analysis was performed in ANSYS Fluent® [16]. The
multi-objective optimization was performed using
modeFRONTIER [14] while the stress-deformation analysis was
performed in ANSYS Structural®.
Due to the large computational cost for each conjugate heat
transfer analysis (eight hours on eight cores), a metamodel in the
form of response surface approximation based on Hardy’s
Multiquadrics Radial Basis Functions (MRBF) [17] was used.
It is known that the accuracy of the metamodel is highly
dependent on the size and distribution of the dataset. The
response surfaces were constructed using 30 candidate design in
the case of circular pin fin and 50 designs in the case of airfoil
and convex pin fins. The SOBOL’s algorithm [18] was used to
evenly distribute the candidate configuration through the design
space.
The optimization was carried out by coupling the response
surfaces (one for each objective function) with the Non-
Dominated Sorting Genetic Algorithm (NSGA-II) [19]. The
NSGA-II algorithm was used to navigate the objective function
space produced by the response surfaces to arrive at Pareto
frontier of best trade-off solutions.
4 Copyright © 2015 by ASME
Figure 4. Workflow of different modules and software used.
RANDOM NON-OPTIMIZED CONFIGURATIONS
For comparison purposes, benchmark designs were creased
using SOBOL’s algorithm. Figure 5 shows the temperature field
for the three non-optimized configurations.
a)
b)
c)
Figure 5. Temperature field for non-optimized configurations of pin-fins having: a) circular, b) symmetric airfoil, and c) symmetric convex cross sections
Figure 6 shows the pressure field at mid-height of the three
non-optimized configurations. The high-pressure stagnation
regions can be seen for both circular and airfoil configurations.
This stagnation region virtually disappears for the convex shape.
a)
b)
c)
Figure 6. .Pressure field for non-optimized arrays of micro pin-fins having: a) circular, b) symmetric airfoil, and c) symmetric convex cross sections
OPTIMIZATION RESULTS
Figure 7 shows the Pareto fronts obtained by coupling
NSGA-II algorithm and the MRBF response surfaces as well as
the candidate designs used to create the response surfaces.
Although the response surfaces were validated before coupling
with the NSGA-II algorithm, global validation is extremely
difficult. For this reason five Pareto designs for each pin fin
configuration were randomly selected and analyzed in ANSYS
Fluent.
5 Copyright © 2015 by ASME
a)
b)
c)
Figure 7. Objective function space for initial population and virtual Pareto designs for arrays of micro pin-fins having: a) circular, b) airfoil, c) symmetric convex cross sections,
The objective function values calculated using the response
surfaces deviated by less than 3% from those computed by
ANSYS Fluent thereby demonstrating the acceptable accuracy
of the metamodels.
Table 2 shows the geometric parameters and inlet condition
for each of the three optimized configurations of arrays of pin
fins with the two objective function values.
Table 2. Parameters and objective function values for the three Pareto-optimized pin-fin geometries.
Pin-fin Configuration
Parameters
Circular Symmetric
airfoil
Symmetric
convex
Diameter (��) 120 - -
Chord length (��) - 210 290
Thickness (��) - 90 90
Height (��) 250 250 250
Inlet speed (m/s) 2.2 3 4.4
Max. temperature (C) 56 52 53
Inlet pressure (kPa) 101.40 96.55 89.00
Figure 8 shows the temperature distribution on the solid
domain of the three optimized configurations. Figure 8 and Table
2 show that the use of circular cross section pin-fins results in
both higher maximum temperature and inlet pressure. The lower
temperature towards the bottom of the airfoil pin-fin
configurations suggests that more heat is being transfer from the
pin-fins to working fluid.
a)
b)
6 Copyright © 2015 by ASME
c)
Figure 8. Temperature distribution on the solid domain due to Pareto-optimized: a) circular, b) symmetric airfoil and c) symmetric convex cross sections of micro pin-fins.
Figure 9 shows the pressure field at mid-height of the three
optimized configurations. It can be seen that the high-pressure
stagnation point for the circular and airfoil has reduced. Figure 8
and Table 2 show that the airfoil and convex shapes also result
in lower inlet pressure and therefore lower pumping power
requirement.
a)
b)
c)
Figure 9 Pressure distribution for Pareto-optimized arrays of pin-fins having: a) circular, b) symmetric airfoil, and c) symmetric convex cross sections.
Figure 10 shows the velocity magnitude and velocity vectors
for the three optimized configurations. The large separation
region behind the circular pin fin is clearly visible. The
stagnation point at the leading edge of the circular and airfoil pin
fins is clearly visible. This is not seen in the case of convex pin
fins.
Figure 10. Velocity magnitudes and flow vectors for the three Pareto-optimized pin-fin cross sections.
The objective function values for the three optimized and
non-optimized configurations are shown in Table 3. It is well
known that in the case of multi-objective optimization, there is
no single optimum design but rather best trade-off designs. When
selecting the three optimum configurations, priority was given to
a design with lower inlet pressure. It should be mentioned that
another Pareto optimum configuration can be selected from the
Pareto front that best meets the required performance. Table 3
shows that the airfoil and convex pin fin configurations result in
both lower temperature and lower pumping power than the
circular pin fin configurations. It shows that the convex pin fin
results in similar temperatures but require significantly lower
pumping power.
Table 3. Objective function values for non-optimized and Pareto-optimized arrays of micro pin-fins for each of the three pin-fin geometries.
T (oC) ∆T% p (kPa) ∆P%
Non-Optimized Circular 54 - 146.18 -
Optimized Circular 56 +2 101.4 -30
Non-Optimized Airfoil 57 - 188.36 -
Optimized Airfoil 52 -5 96.55 -49
Non-Optimized Convex 56 - 180.47 -
Optimized Convex 53 -6 89 -51
7 Copyright © 2015 by ASME
STRESS-DEFORMATION ANALYSIS
Depending on the sensitivity of the design, slight deviation
from the optimum configuration can significantly reduce
performance. These deviations can be due to manufacturing
defects or externally applied loads. For this reason, stress-
deformation analysis was performed on the three optimum
configurations to investigate the magnitude of deviation from the
optimum configurations. A typical grid of approximately four
million cells was used for each stress-deformation analysis.
The hydrodynamic and thermal loads from the conjugate
heat transfer analysis were applied and all external sides of the
chips were fixed to investigate the effects of the loads on the
micro-pin fin configurations.
Figure 11 shows the displacement field for the three
optimum configurations due to hydrodynamic and thermal loads.
It can be seen that the maximum displacement is on the nano-
level, suggesting geometric deviations from the optimum
configurations are miniscule.
a)
b)
c)
Figure 11. Displacement field due to hydrodynamic and thermal loads on Pareto-optimized pin-fins having: a) circular, b) airfoil, and c) symmetric convex cross sections
Figure 12 shows the Von-Mises stress field for the three
optimum configurations. It can be seen that the higher stress are
concentrated towards the outlets. This is due to the increased
thermal loads as the heat transfer properties of the warmer fluid
are diminished. It can be seen that the maximum Von-Mises
stress for the three configurations is between 47 and 75 MPa,
which is significantly lower than the yield strength of 7000 MPa
for silicon [20]. This suggests that, from a structural viewpoint,
the hydrodynamic and thermal loads can significantly be
increased without compromising structural integrity.
a)
b)
c)
Figure 12. Von-Mises stress distribution due to hydrodynamic and thermal loads on pin-fins having: a) circular, b) airfoil, and c) symmetric convex cross sections
CONCLUSION
This study investigated the thermal management capabilities
of three micro-pin fins geometries in cooling of micro-
electronics with a uniform heat flux of 500 W cm-2. Conjugate
heat transfer analysis was performed on each configuration and
showed that the airfoil and convex shapes virtually eliminated
the recirculation region experience by the circular pin fins. A
multi-objective optimization was performed for the three
configurations where the two objectives were to minimize
��
��
8 Copyright © 2015 by ASME
maximum temperature and pumping power. The design
variables were the geometric parameters defining each
configuration in conjunction with the inlet velocity. The
optimization was efficiency performed by coupling response
surfaces with the NSGA-II algorithm. The optimum
configurations showed that the airfoil and convex shapes
outperformed the circular pin fins in both objectives. Stress-
deformation analysis incorporating hydrodynamic and thermal
loads from the conjugate heat transfer analysis was also
performed to analyse the structural integrity of the three
optimum configurations. It was shown that the maximum
displacement for all three configurations is on the nano-level.
The maximum Von-Mises stress for the three configurations was
in the range of 47 to 75 MPa, which is significantly lower than
the yield strength for silicon of 7000 MPa, indicating the
structural integrity of the three optimum configurations.
ACKNOWLEDGMENTS The authors are grateful for the partial financial support of
this research provided by DARPA via GaTech in the framework
of ICECool project under supervision of Dr. Avram Bar-Cohen.
They are also grateful for the partial financial support
provided by DOE/NETL grant DE-FE0023114. The authors also
gratefully acknowledge the FIU Instructional and Research
Computing Center for providing HPC resources to perform
calculations for this project.
The first author would like to express his appreciation to
Prof. George S. Dulikravich and Dr. Abas Abdoli for their
guidance and for providing suggestions for the manuscript. He is
also grateful for Cesar Pacheco’s and Rajesh Jha’s help with
creation of hybrid computational grids.
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