Paper id 28201451

International Journal of Research in Advent Technology, Vol.2, No.8, August 2014
E-ISSN: 2321-9637
Heat Transfer Simulation of Impinging Jet with Finned
110
Heat Sink
Shivakumar H1, Krishnamurthy K N2, Akashdeep B.N3
Department of Thermal power Engineering, M.Tech student1, Assistant professor2, VTU P G Centre Mysore,
Karnataka, India 1, 2.
Department of Mechanical Engineering Assistant Professor KSSEM Bangalore Karnataka, India3.
Email: shivu_bec@hotmail.com1, murthykrishnakn@gmail.com 2,bndeep@gmail.com3
Abstract- This study examines numerically details of the flow and temperature fields of heat sinks with short
plate fins cooled by impinging jet. The main focus is on the effect of fin spacing, fin material and jet velocities
on the heat sink performance. Conjugate heat transfer between airflow convection and conduction inside the fin
and base is considered. Three different fin spacing (2 mm, 3 mm, 4 mm), fin material (Aluminum, copper and
steel) and jet velocity of (5 m/s,10 m/s and 15 m/s ) are the parameters under study. Detailed temperature
contours, velocity vector, pressure drop are presented and compared. In this current work the effect of fin
material is observed that heat transfer rate varies in accordance with thermal conductivity of fin material. For the
considered geometry there was increase of 0.2 W and 0.7804 W heat transfer rate for copper fin material, when
it is compared to Aluminum and steel respectively for 15 m/s jet velocity. The effect of fin spacing on rate of
heat transfer rate for the considered geometry it is observed that there is increase of 19% and 48% heat transfer
rate for decrease of fin spacing of 2 mm and 3 mm respectively at 15 m/s jet velocity. Pressure drop is also
sensitive to fin spacing in all the combinations, as fin spacing decreases pressure drop increases. For the
considered geometry it is observed that pressure drop of 100 Pa, 120Pa and 140Pa for 4 mm, 3 mm, and 2 mm
fin spacing respectively for jet velocity of 15 m/s. In overall pressure drop and heat transfer rate are
contradicting with respect to fin spacing. However use of copper material makes heat sink heavier and
expensive. Hence it can be concluded that for considered geometry of fin spacing 2 mm at 15 m/s of jet velocity
for Aluminum fin material the numerical result was found to be optimum. The results of this can help in design
of heat sinks with jet impingement, which are commonly used in electronic cooling systems.
Index Terms: Jet impingement, heat sink, plate fin.
1. INTRODUCTION
The relentless trend of ever increasing
integrated circuit chip functionality and decreasing
chip dimensions for miniaturization of products have
led to the need to develop new thermal management
techniques to handle intense heat generation rate in IC
chips. The need for effective cooling of chips at an
acceptable cost is an urgent issue Extended surfaces
(fins) and impinging jets have commonly been used to
enhance heat transfer in many applications, for
example, electronic cooling and gas turbine cooling.
In electronic thermal management, heat sinks are
designed to take advantage of the combined effect of
fins and jet impingement such as jets impinging on an
array of pin fins or plate fins. Significant studies have
been focused on the thermal resistance, pressure drop,
and the parametric effect of Reynolds number, fin
thickness, density and height. Different correlations
based on one-dimensional heat conduction and
experimental data are developed to predict the heat
sink performance. Efforts to optimize the heat sink
design have also been made by using both
experimental and numerical methods.
2. CURRENT STUDY
This study applies numerical simulation to
examine the details of flow and temperature fields of
plate fin heat sinks with jet impingement. Based on
the literature review few studies have been done on
the effect of fin spacing, fin material and jet velocity.
Therefore, the main focus of this study is on the effect
of fin spacing of (2 mm, 3 mm and 4 mm), fin
material Aluminum, copper and steel, jet velocity of
(5 m/s, 10 m/s and 15 m/s) on the heat sink
performance. The characteristics of 3D temperature
field inside the fins and solid base are also explored. It
is observed that the fin spacing affects largely both
the heat transfer and pressure drop, fin material and
jet velocity effects on heat transfer rate especially of
the short fin cases .The results of this paper can help
in design of heat sinks with jet impingement.
2.1 Objectives:
1. This concerns the familiarization with the
methods and materials. This involves literature
reviews on the different methods of cooling
employed in electronic equipment’s.
2. This involves choosing the parameter on which
analysis should be carried out. In this work the
parameters selected are fin material (Aluminum,
copper and steel), fin spacing (2 mm, 3 mm, 4
mm), and velocity of jet (5 m/s, 10 m/s and 15
m/s).
3. The selection of geometry for the CAD model
was selected from literature [10] and the physical

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111
arrangement of fin is modeled using hyper mesh
V10 software.
4. Mesh generation of the modeled geometry
was carried out using hyper mesh V10
software.
5. The boundary conditions for the fluid flow
analysis were imposed and the solution was
obtained through the analysis software
FLUENT 6.3.26.
6. The analysis was carried out to obtain heat
transfer rate, pressure drop and contours of
temperature, Velocity vector are drawn
.
3. PROBLEM UNDER CONSIDERATION
There are generally two types of heat sinks
with jet impingement. One is with parallel plate fins,
and the other is with pin fins. In this study the plate
fin heat sink is considered. Figure 1 shows the
geometric schemes of this type of heat sink. The slot
jet impinges from the top to the plate fins and exits
from two sides into the surroundings. The sink base is
connected to the electronic modules to dissipate the
heat to the cooling airflow. The top can be either open
or confined, which is considered as confined in this
study. The performance depends on the jet velocity,
fin height, fin width, number of fins, and the base
thickness. In practice, there usually is a small gap
between the fin tip and jet plate
Fig 1 Geometric scheme of a heat sink of parallel
plate fins cooled by an impinging jet
The heat sink in Fig 1 is symmetric in both
the x- and z directions unless the flow or thermal
boundary conditions are applied differently. Figure 2
shows the symbolic dimension of the cases under
study. The fin shape considered is rectangular fins.
All the fins share the same height and base width,
which leads to a slightly different surface area and
thus different volume or weight. The total height in
the y-direction is H, and heights for the fin and base
are h1 and h2, respectively. The fin has a thickness of
b, and the distance between the fins is B1.The the
impinging slot jet has a width of( l1) and the rest of
the top surface is the confined wall (l2).In this study,
the air jet with constant properties impinges on the
heat sink vertically with a uniform inlet velocity and
temperature. Constant temperature is applied to the
heat sink bottom surface for simplification. The
considered dimensions and thermal Properties of fin
materials are presented in table 1 and 2 respectively.
b
H h1
B
h
2
B1
2
Fig. 2 shows the symbolic dimension of the cases
under study
Table 1 Dimensions of Fin geometry
Fin height( h1) 0.006 m
Base height( h2) 0.002 m
Total height (H) 0.01 m
Fin width (b) 0.002 m
Distance between the
fins(B1)
0.002 m, 0.003 m and
0.004 m
Jet width( l1) 0.01 m
Confined wall
length( l2)
0.015 m
Table 2 Thermal properties Fin materials
Material Density
(kg/m3)
Thermal
conductivity
(W/m-K)
Specific
heat
(J/kg-K)
Copper 8978 387.6 381
Aluminum 2719 202.4 871
Steel 8030 16.3 502.5
4. NUMERICAL METHADOLOGY
In CFD calculations, there are three main steps.
Pre-Processing
Solver Execution
Post-Processing
Pre-Processing is the step where the modeling
goals are determined and computational grid is
created. In the second step numerical models and
boundary conditions are set to start up the solver.
Solver runs until the convergence is reached. When
solver is terminated, the results are examined which is
the post -processing.
4.1 Pre-Processing
In this study, the aim is to investigate the
cooling characteristics of different fins. So, an
adequate numerical model is to be created. Pre-

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112
processing is the most time consuming and least
knowledge requiring part. There are two important
points here. The first one is the size of the domain,
and the second one is the density and quality of the
computational grid. Model size is the computational
domain where the solution is done. It is important to
build it as small as possible to prevent the model to be
computationally expensive. On the other hand it
should be large enough to resolve all the fluid and
energy flow affecting the heat transfer around the Fin.
In this problem, domain is selected to be the two fins
The model of the present problem is created
using hyper mesh 10 software major commands used
for creation are nodes; line .The obtained model is
meshed using the HYPERMESH 10 software. In
meshing first 2D meshing is done using the quad
elements it is because the model is in regular shape as
shown in Fig 3 to Fig 5.
Fig. 3 Meshed diagram of 2mm spacing
Fig 4 Meshed diagram of 3mm spacing
. Fig 5 Meshed diagram of 4mm spacing
4.2 Symmetry Condition
Symmetry boundary conditions are used
when the physical geometry of interest, and the
expected pattern of the flow/thermal solution, has
mirror symmetry. These can also be used to model
zero-shear slip walls in viscous flows. In the present
case single fin is considered and applying symmetry
boundary condition at one face it can obtain two fins.
The symmetry grid display is shown in Fig 6.
Fig 6 symmetry grid display
5. SOLVER SET UP
The solver set up is very important in any of
the fluid flow problem; the solver setting indicates the
method and also a procedure for solving (analysis) the
problem. The flow analysis has studied using ANSYS
FLUENT (6.3.26) [17]
5.1 Turbulence Modeling
The turbulence model used for this work is
standard k-epsilon. The 3D space pressure based
solver is used and implicit formulation is used for
solution scheme. Solution controls uses flow and
turbulence equations. The simple algorithm is used for
pressure velocity coupling and for discretization
second order scheme is used [9]. The convergence
criteria for all case studies are taken as 0.001.
5.2 Governing Equations to be solved
Time independent flow equations with
turbulence are to be solved. The viscous dissipation
term will be omitted. Therefore the governing
equations for the fluid flow, Above Equation are
modified as follows:

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113
Mass
X momentum (ρu ) =
Ymomentum: (ρv )=
Zmomentum: (ρ )=
Energy: ( ) = -p + +
Equation of state: p=
5.3. BOUNDARY CONDITIONS
The boundary conditions are the important
values for the mathematical model. The boundary
condition is applied to different zones. There are
different kinds of boundary conditions for the fluid
flow to enter and exit the domain. The boundary
condition is depending on type of fluid use for the
analysis. The fluid used for this analysis is
incompressible hence velocity inlet condition applies.
Inlet velocity profile was assumed, slip condition
assigned to all surfaces. The boundary conditions used
for the analysis are listed in table 3
Table 3 Boundary conditions used in CFD analysis.
Sl no Quantities Condition/value
1 Working fluid Air
2 Gauge pressure 0 Pa
3 Inlet velocity 5m/s,10m/s and 15m/s
4 Fin material Aluminum, copper and
steel
6. RESULTS AND DISCUSSION
In this study two rectangular fin geometry is
considered. The parameters like fin material
(Aluminum, copper and steel) are considered and fin
spacing varied as (2 mm, 3 mm, 4 mm) and jet
velocity of (5 m/s, 10 m/s and 15 m/s) are considered.
The detailed effect of these parameters are analysed as
shown below Simulation technique is used in the
present work which involves selection of geometry
from the literature, modeling and meshing of the
geometry was performed using HYPERMESH10
software. The physical boundary conditions were
applied to meshed model by importing meshed model
to FLUENT 6.3.26 and analysis is carried out using
CFD solver. The different graphs of heat transfer rate,
pressure drop and temperature distribution, velocity
vectors for varied combinations of fin material, fin
spacing and jet velocity (27 combinations) were
analyzed in detail.
6.1 Convergence
Only a well converged simulation can give
reliable results. Convergence is determined by the
order of magnitude residuals drop the convergence of
simulation is required to get the parameters of the fin.
It also gives accurate value of parameters for the
requirement of heat transfer rate, pressure drop.
Continuity, X-velocity, Y-velocity, Z-velocity,
energy, k, epsilon are the part of scaled residual which
have to converge in a specific region. For the
continuity residuals set are 10-3, X velocity, Y
velocity, Z-velocity, k, epsilon should be less than
10-5 and the energy should be less than 10-6. If all
values in same manner then solution will be
converged. For the considered problem convergence
is obtained at 500 iterations.
6.2 Heat transfer rate in impinging jet with finned
heat sink:
Heat transfer rate is defined as the amount
heat transferred from the fin and base to the
surrounding fluid. The effect of velocity and fin
material is examined and tabulated in table 4, table 5
and table 6 for 2 mm, 3 mm and 4 mm fin spacing
respectively.
Table 4 Heat transfer rates for 2mm spacing between
the fins.
Sl no Material Velocity
5m/s
Velocity
10m/s
Velocity
15m/s
Heat transfer rate in watts
1 Copper 1.4189 2.2440 2.9054
2 Aluminum 1.3076 2.0990 2.7054
3 Steel 1.1969 1.7456 2.1250
Fig 7 variation of heat transfer rate at 2mm spacing
the fins
Sl
no
Material Velocity
5m/s
Velocity
10m/s
Velocity
15m/s
1 Copper 1.3351 2.124 2.7084
2 Aluminum 1.3224 2.005 2.6615

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114
3 steel 1.1674 1.6225 1.9434
the fins
Sl
no
Material Velocity
5m/s
Velocity
10m/s
Velocity
15m/s
1 Copper 1.2927 1.9200 2.4190
2 Aluminum 1.1999 1.8050 2.3900
3 steel 1.1307 1.5928 1.785
Heat transfer rate is the important parameter
to judge performance of a fin. The variation of heat
transfer rate for Aluminum, copper and steel is
tabulated and variation is plotted in Fig 7, Fig 8 and
Fig 9. In all these cases heat transfer rate is increasing
as the velocity increases and also heat transfer rate is
high for the copper, than Aluminum and lowest for
the steel .The variation of heat transfer rate depend on
fin material, jet velocity and fin spacing. Heat transfer
rate increases with increase in thermal conductivity of
fin material and also with increase in jet velocity. But
increase in fin spacing there was decrease in heat
transfer rate for all the cases of fin material and jet
velocity. For 2 mm spacing of copper material at
15m/s there was increase of 0.4864 W of heat transfer
rate when compared to 4 mm spacing at 15 m/s jet
velocity. It is due to decrease in fin spacing, velocity
loss will be less and also volume flow rate of fluid
particles will be higher between the two fins. Due to
which there is increase in heat transfer rate at 2 mm
fin spacing.
From the CFD analyses the obtained graphs
shows that when the steel is used as fin material there
will be a drastic reduction in heat transfer rate for all
the cases of fin spacing and jet velocity. When
aluminum is used as fin material there was increase in
heat transfer rate when compared to steel but slightly
less when copper is used as fin material. For 2 mm
spacing of aluminum material at 15 m/s there was
0.5804 W of heat transfer rate increase with respect to
steel, but 0.2 W of heat transfer rate decrease when
compared to copper fin material. From the above
obtained graphs it can be concluded that for 2mm
spacing at 15 m/s when copper is used as fin material
heat transfer rate will be maximum for the considered
geometry when compared to other materials and fin
spacing
6.3 Temperature Distributions in Fins
For the considered geometry, the temperature
distribution is mainly dependent on fin material used
and inlet jet velocity, But it is invariant with fin
spacing so temperature distribution is presented for
fin material of copper ,aluminum and steel for varying
inlet velocity 15 m/s for only 2 mm spacing. Fig 10,
Fig 11 and Fig 12 shows temperature contour for
copper, aluminum and steel at 15 m/s jet velocity
.
Fig 10 Temperature contour for copper 2 mm fin
spacing @15 m/s
Fig 11 Temperature contour for Al 2 mm fin spacing
@15 m/s

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115
Fig 12 Temperature contour for steel 2mm fin spacing
@ 15 m/s
It is reasonable to see that the temperature in
the region close to the fin tip and jet inlet is lowest. It
is observed that the temperature gradient for the fin
base and tip of the fin for copper and aluminum is
around 2 K to 3 K but for steel it is around 10 K it is
because the Thermal conductivity for copper and
aluminum is high as compared to steel. The
conduction heat transfer takes place from bottom
surface of the base to the top surface of the fin .The
temperature in region close to the fin tip and jet inlet
is lowest, because as the jet inlet velocity is maximum
at the inlet and also heat transfer coefficient increases
with increase in the Reynolds number due to which
heat transfer rate is maximum at the inlet of the jet
corresponding to fin tip. So it is observed that
minimum temperature will be at the inlet of the jet.
From this there will be effective heat transfer
takes place when the impinging jet technique is used
for heat sink in an electronic cooling purpose.
6.5 Velocity Analysis
Velocity of jet around the fin and between
the fins is predominant factor for rate of heat transfer
by the heat sink. The variation of velocity from inlet
to the outlet is presented by plotting velocity vectors
since the velocity variation is mainly depends on inlet
velocity of the jet and it is invariant with fin material
so for the considered geometry velocity variation for
copper material is presented. Fig 13, Fig14 and Fig15
shows the velocity variation for inlet jet velocity of
5m/s for copper material at 2 mm, 3 mm and 3 mm
spacing respectively.
Fig 13 Velocity vector for cu at 5m/s for 2mm fin
spacing
spacing
spacing
It is observed from velocity vectors for all the
cases of varying inlet velocity the outlet velocity close
to the base is higher due to the impinging effect. For
the considered geometry for inlet velocity of 5 m/s,
10 m/s and 15 m/s the outlet velocity close to the base
is around 13 m/s, 25 m/s and 38 m/s respectively.
For the decrease in fin spacing it is observed
from velocity vectors there was increase in average
channel velocity of jet. As the fin spacing decreases
the pressure drop increases which results in increase
of velocity. Since the velocity variation is mainly
depends on fin spacing and inlet velocity but it is
invariant of fin material so only for copper material
velocity variation is presented in this work but
velocity variation for aluminum and steel is also
analyzed.
6.6 Pressure drop analysis
Pressure drop is the resistance to the air
movement and it is related with flow cross sectional
area, fin spacing and fin length. The heat sink should
be designed so as to yield a smaller pressure drop than
the static pressure of the fan. In general, the total heat
sink pressure drop depends on four major factors the
friction factors, the heat sink geometry, the approach
velocity and the heat sink channel velocity. The
friction factors arise from the airflow entering and
exiting heat sink channel are known as the contraction
loss coefficient and expansion loss coefficient
respectively, whereas the friction factor that due to the

E-ISSN: 2321-9637
116
transition of airflow from developing flow to fully
developed flow is called the apparent friction.
Pressure drop values were tabulated in table 7, table 8
and table 9 for 2mm, 3mm and 4mm fin spacing
respectively.
Table 7 pressure drop for 2 mm spacing between the
fins
Sl
Velocity
Velocity
Velocity
Material
no
5m/s
10m/s
15m/s
Pressure drop in (Pascal)
1 Copper 140 520 1200
2 Aluminum 140 520 1200
3 Steel 140 520 1200
Table 8 pressure drop for 3 mm spacing between the
fins
Sl
no
Material
Velocity
5m/s
Velocity
10m/s
Velocity
15m/s
1 Copper 120 450 1000
2 Aluminum 120 450 1000
3 Steel 120 450 1000
Table 9 pressure drop for 4mm spacing between the
fins
Sl
no
Material
Velocity
5m/s
Velocity
10m/s
Velocity
15m/s
1 Copper 100 300 800
2 Aluminum 100 300 800
3 steel 100 300 800
Fig 16 pressure drop variation with fin spacing
Since from the table 7 table 8 and table 9. It
is observed that pressure drop is invariant with fin
material so pressure drop along the fin is presented
with the variation of fin spacing only. From Fig 16 It
can be observed that as the fin spacing decreases
pressure drop increases. With the decrease in fin
spacing flow between the fin spacing is fully
developed because due to high Reynolds number
friction Factor will be very much greater for minimum
fin spacing this affects heat transfer rate. Increase in
pressure drop affects the fluid flow particles
movement over the fin material.
Sometimes negative pressure will be
developed at inlet with respect to exit. Due to which
the flow will be reversed which affects performance
of the heat sink. For the considered geometry it is
observed increase in pressure drop as the decrease in
fin spacing but not less than static pressure.
7. CONCLUSIONS
The analytical model is developed for high
Reynolds number turbulent flow and heat transfer in
inter fin channels of impingement flow plate fin heat
sink. The simple model is suitable for heat sink
parametric design study. From the obtained numerical
results the following conclusions can be drawn.
1. From the obtained numerical analysis maximum
heat transfer rate was for copper fin material at 2
mm spacing for 15 m/s jet velocity. The results
shows that there was increase in 0.2 W and
0.7804 W heat transfer rate compared to
aluminum and steel respectively at 2mm fin
spacing and 15m/s.
When aluminum is used as fin material and
compared with respect to copper and steel. The
rate of heat transfer was maximum compared to
steel but there was slight reduction in rate of heat
transfer compared to copper at all fin spacing (2
mm, 3 mm and 4mm ) and at all jet velocity (5
m/s ,10 m/s).
In overall copper fin material showed good
results but the use of copper as fin material makes
heat sink heavier and expensive so aluminum can
be selected as fin material for thermal heat sink
which gives optimum result compared to copper.
2. For all combinations it is observed as the fin
spacing decreases there is an increase in heat
transfer rate. For the considered geometry 2mm
fin spacing gives optimum heat transfer.
3. Pressure drop plays vital role with respect to fin
spacing. With decrease in fin spacing for the
considered geometry pressure drop increases
which affects the rate of heat transfer. But for
considered geometry the effect of pressure drop is
negligible. But when higher dimensions are
considered with impinging jet the rate of heat
transfer decreases with increase in pressure drop
for the reduced fin spacing.
4. From the velocity vectors it was observed that
there was an increase in jet velocity as the fluid
flows from inlet to exit. It is because of the
impinging effect and reduced fin spacing. This

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117
results in increase of heat transfer rate when
compared to parallel flow arrangement.
5. From the temperature contours it can be
concluded that temperature close to the fin tip at
inlet of the jet is observed minimum. This
indicates maximum temperature difference
resulting in high heat transfer rate at the inlet.
6. In overall for the considered geometry and
boundary conditions it can be concluded that fin
material of aluminum with 2 mm fin spacing at
15 m/s jet velocity gives the optimum result for
electronic cooling systems.
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