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Performance Analysis of Electronics Cooling using Nanofluids in
Microchannel
Heat Sink Siti Natasha Malik Fesal1, SitiSyazwaniIlmin2,
ZurainiGani3
1Mechanical Engineering Department, 2Mathemathics Science and
Computer Department, Polytechnic Ungku Omar, Ipoh, 31400, Perak,
Malaysia
3Mechanical Engineering Department,UniversitiKebangsaan
Malaysia, 43600Bangi.Malaysia. [email protected]
[email protected] [email protected]
Abstract—Performance analysis of thermal enhancement for cooled
microchannel heat sink (MCHS) using nanofluidsmathematical
formulation was investigated and presented in this paper. Heat
transfer capability in terms of thermal conductivity, heat transfer
coefficient, thermal resistance, heat flux and required pumping
power were evaluated on the effectiveness of copper oxide (CuO),
silicon dioxide (SiO2) and titanium dioxide (TiO2) with water as a
base fluid. The results showed that thermal performance augmented
by 12.2% in thermal conductivity at particle volume fraction of 4%
to CuO-water nanofluid, 11.8% for SiO2-water and 10.0% for
TiO2-water. The maximum heat transfer coefficient enhances of 12.4%
for CuO, SiO2 is 8.22% and 7.4% for TiO2 with the same inlet
velocity of 3 m/s. The addition of nanoparticle concentration
significantly enhances the heat transfer, but elevates the expenses
of higher required pumping power to increase the pressure drop. The
maximum enhancement of heat flux in CuO-water was found to be 2575
kW/m2, 2501 kW/m2 for SiO2-water and 2485 kW/m2 for TiO2-water
nanofluid at 4% of volume fraction. The pressure drop is increased
with the mass flow rate of 1021 kg/m3 for CuO-water at 0.5% of
volume fraction and 47925 Pa to 54314 Pa pressure drop at 4% of
volume fraction. The CuO-water pumping power was found to be the
highest at 4% of volume fraction with 102.3 W at 3 m/s inlet
velocity compared to SiO2 and TiO2 also increased the pumping power
of 75.0 W to 90.6 W with increasing volume fraction and pressure
drop. The positive thermal results implied that CuOnanofluid is a
potential candidate for future applications in MCHS.Further
analysis is recommended to be done with various Reynolds number,
pumping power and flow rate of nanoparticles to obtain better heat
transfer performance of cooling fluids. Keywords: Electronics
cooling, nanofluids, microchannel heatsink
I. INTRODUCTION In the last three decades, the emergence of
nanotechnologyis rapidly approaching, were utilized to improve the
heat transfer rate to apply on the electronicdevices in order to
reach a satisfactory level of thermal efficiency. The heat transfer
rate can passively be improved by changing the geometry’s flow,
boundary conditions or by improving thermo physical properties such
as increasing the thermal conductivity of fluid [1]. To meet the
high dissipation rate requirements and maintain a low junction
temperature in electronic devices, many cooling technologies have
been pursued. Among of these, the microchannel heat sink (MCHS) was
introduced because of its ability to produce high heat transfer
coefficient, small size and volume per heat load and small coolant
requirements [2].
Working fluids was applied to enhance the heat transfer by
changing the fluid transport properties and flow features in MCHS.
Recently, this concept has focused on heat transfer enhancement by
using a nanofluid that has a nanoscale metallic or non-metallic
particles in the base fluids.Besides, nanofluids has become a
concern because they display higher potential as heat transfer
fluid than normally utilized base fluids and micron sized
particle-fluids. This is due to clogging in pumping and flow
apparatus which is caused by rapid settling of the micron sized
particle. Nanofluids do not indicate this behavior. This makes
nanofluids a better choice as heat transfer fluid [3]. Nanofluids
(1-100nm-size particles), often called as ultra-fine solid
particles, engineered colloidal suspension, are stable and prepared
by dispersing a certain percentage of nanoparticles in base
fluids[4-6]. The factors that causes heat transfer enhancement are
solid particles and host fluids chemical composition, size, shape
and concentration of nanoscale particles, thermal condition and
surfactants. Some of these factors also affect the stability of the
nanofluids. There are three strategies to attain good stability,
namely addition of surfactants, pH control and ultrasonification
[7]. From the literature, heat transfer coefficient depends on
Reynolds number, volume fraction of the nanofluids (concentration),
temperature, base-fluid
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thermal properties and nanofluids purity. Generally, nanofluids
are highly potential to be used as coolant in electronic packaging
since their heat transfer coefficient exceeded the predicted value
in laminar flow region in many analyses and from the famous
Dittus-Boelter correlation in turbulent correlations [8].
Zakaria et al.[9] has studied on numerical analysis of thermal
enhancement for a single Proton Exchange Membrane Fuel Cell (PEMFC)
cooling plate by using a low concentration of Al2O3 in
Water-Ethylene Glycol mixtures as a coolant. It shown that the
higher volume percent concentration of Al2O3 the better the heat
transfer enhancement but at the higher expense of pumping power.
Moraveji et al. [10] used a model of MCHS with 20 x 20 mm bottom
with five nanoparticle volume fractions in five inlet velocities
for two types of nanoparticle containing TiO2 and SiC.By using
different value of Reynolds Numbers, the effect of a nanoparticle
volume fraction on the convective heat transfer coefficient was
investigated. The modelling results was compared to analytical
calculations and it showed that, it was accurate for the correlated
equations that were obtained for Nusselt number and friction factor
were acceptable.
The numerical simulations is studied on the laminar and
turbulent forced convection heat transfer in a MCHS with a mixture
of nanofluid consisting of CuO-water [11]. The method used to solve
the continuity, momentum and energy equations was the finite volume
method with the parameters of the particle volume faction ( 0.204%,
0.256%, 0.294% and 0.4%), and the volumetric flow rate ( 10 mL/min,
15mL/min and 20mL/min). From the comparisons of thermal resistance
predicted by the single-phase and two-phase models with the
experimental results, it revealed that, two-phase model was more
accurate than the single-phase model. Other than that, the thermal
resistance of nanofluids is smaller than that of water, which
decreases as the particle volume fraction and the volumetric flow
rate increase in laminar flow. In addition, the pressure drop
increases slightly for nanofluid-cooled MCHS in the laminar flow
case.
This study deals with three types of nanoparticles which are
copper oxide(CuO), silica(SiO2) and titanium oxide (TiO2) suspended
in a water as a base fluid. The microchannel heat sink (MCHS)
operation was analyzed with the nanofluids serve as a working
fluid.Performance of nanofluids as coolant is predicted in terms of
thermal conductivity, heat transfer coefficient, thermal
resistance, heat flux and required pumping power.
II. METHODOLOGY The performance of CuO-water, SiO2-water and
TiO2-water nanofluids has been analyzed by using
mathematical formulation to compare the performance of cooling
of electronics. Thermophysical properties of the water and
nanoparticles (CuO, SiO2, TiO2) at 30oC areas shownin Table I.
TABLE I. Thermophysical properties of the base fluid and
nanoparticles [10, 12]
A. Nanofluid Properties The thermophysical properties of the
nanofluidswiththe volume fractions, , of nanoparticles and base
fluid were used; 0.5%, 1.0%, 1.5%, 2.0%, 2.5%, 3.0%, 3.5% and 4.0%
are determined by utilizing the following equations: Density of
nanofluid is calculated by the use of Pak and Cho
[13]correlation:
∅ 1 ∅ (1) Effective thermal conductivity is given by Hamilton
and Crosser [13] equation, can be expressed as follow:
∅∅ (2)
Nanofluid specific heat equation is evaluated from Xuan
andRoetzelcorrelation [14] which shown below: 1 ∅ ∅ (3)
Effective viscosity of nanofluid is given by Einstein equation
as suggested for particle in volume fractions less than 5.0 vol.%
and is defined [15]:
Fluid/Nanoparticles Properties ρ(kg/m3) µ(N.s/m3) Cp(J/kg.K)
k(W/m.K)
Base Water, H2O 994.2 724.6 x 10-6 4178 0.6248 Copper Oxide, CuO
6320 - 385 76.5 Silica Dioxide, SiO2 3970 - 765 36 Titanium
Dioxide, TiO2 4157 - 710 8.4
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1 2.5∅ (4) Where subscript f, p, nf are correspond to fluid,
particle and nanofluids respectively. Nanoparticle shape factor, n,
was assumed to be 3 for spherical particles as tabulated in Table
II.
TABLE II. Calculated thermophysical properties for
nanofluids
CuO/Water Properties Particle Volume Fraction(∅ %) ρCuO kCuO
ρCpCuO µCuO
0.5% 1020.83 0.63399 4145165 0.00073 1.0% 1047.46 0.64327
4136562 0.00074 1.5% 1074.09 0.65265 4127959 0.00075 2.0% 1100.72
0.66211 4119356 0.00076 2.5% 1127.35 0.67167 4110753 0.00077 3.0%
1153.97 0.68133 4102151 0.00078 3.5% 1180.60 0.69109 4093548
0.00079 4.0% 1207.23 0.70094 4084945 0.00080
SiO2/WaterProperties Particle Volume Fraction(∅ %) ρ SiO2 k SiO2
ρCpSiO2 µ SiO2
0.5% 1009.08 0.63374 4148184 0.00073 1.0% 1023.96 0.64277
4142600 0.00074 1.5% 1038.84 0.65189 4137017 0.00075 2.0% 1053.72
0.66109 4131433 0.00076 2.5% 1068.60 0.67038 4125850 0.00077 3.0%
1083.47 0.67977 4120266 0.00078 3.5% 1098.35 0.68924 4114682
0.00079 4.0% 1113.23 0.69881 4109099 0.00080
TiO2/WaterProperties Particle Volume Fraction(∅ %) ρ TiO2 k TiO2
ρCpTiO2 µTiO2
0.5% 1010.01 0.63238 4147756 0.00073 1.0% 1025.83 0.64003
4141745 0.00074 1.5% 1041.64 0.64773 4135733 0.00075 2.0% 1057.46
0.65550 4129722 0.00076 2.5% 1073.27 0.66333 4123710 0.00077 3.0%
1089.08 0.67123 4117699 0.00078 3.5% 1104.90 0.67919 4111687
0.00079 4.0% 1120.71 0.68722 4105676 0.00080
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B. Microchannel Heat Sink (MCHS) The MCHS which typically
contains lot of parallel microchannel has the capability of
producing high heat transfer coefficient, less dimension-volume per
heat load and lesser requirement of coolant [2]. There were few
assumptions have been made in order to simplify this analysis
whereby[9]:
The flow is incompressible, laminar and in steady state. The
effect of body force is neglected. The fluid properties are
constant and viscous dissipation is neglected. The fluid phaseand
nanoparticles are in thermal equilibrium with zero relative
velocity and the resultant
mixture can be considered as a conventional single phase. The
geometric configuration of this microchannel is considered based on
research of Tsai and Chein[2]
shown in Fig.1 whereby the nanofluids is forced to flow through
the fin slot in x-direction with mean velocities of 3 m/s. Table
III below shows the details of MCHS dimensions.
Fig. 1. MCHS schematic diagram [2]
TABLE III. Dimensions of MCHS [2]
Symbol Size Size Lhs x Whs 1 cm x 1cm Channel height, H 365 µm
Channel width, Wch 57 µm Porosity, 0.5 Fin thickness, Wfin 57 µm
Number of channels,n 25 Aspect ratio, 6.4
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Parameters like hydraulic diameter and other dimensionless
correlations for Reynolds number, Prandtl number and Nusselt number
are consideredunder the assumption of single phase, constant
thermal properties applicablefor laminar and turbulent flows in
order to analyze the efficiency of MCHS by applying nanofluids to
achieve the heat dissipation capability [16, 17]. The heat transfer
coefficient is calculated by using:
(5)
Where;
Hydraulic diameter : (6)
Reynolds number : (7)
Prandtl number : (8)
Nusselt number : 0.023 . . (9) The calculation for Reynolds,
Prandtl and Nusselt number are based on the assumption that the
fluid flow with the inlet speed of 3m/s for various volume fraction
of nanoparticle. The efficiency of the microchannel is computed
using:
(10)
Where;
(11)
is the MCHS thermal conductivity which is 400W/mK. Furthermore,
total thermal resistance is computed using the summation of all the
three resistances:
(12)
where is the area of MCHS bottom part and is the total nanofluid
mass flowrate [12]. The surface area is calculated by the formula
of: (13) where is the channel area.
2 (14) Number of cooling channels, n = 25 [18]. Thus, the
total heat transfer (Q) and the bottom heat flux is computed
using:
(15)
and
(16)
Where, is the fluid temperature at the inlet and Tmax is the
largest of bottom temperature of microchannels. From Xie et.al [19]
the maximumdifferenceof is taken to be 50oC. C. Effectiveness
Evaluation of Nanofluid for Electronics Cooling The effectiveness
of nanofluid as coolant is evaluated in term of performance of
microchannel heat sink. This analysis is crucial in order to see
the impact of the viscous pressure drop on the performance of MCHS.
Coefficient of performance, COP for MCHS is defined as the ratio of
the dissipated heat to the invested pumping power [20].
(17)
Where; ∆ (18)
(19) (Ppow: Idealized pumping power and: Volumetric flowrate of
nanofluid, n: Number of channels). The pressure drop is calculated
using [21],
∆ (20)
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with Darcy friction factor : 1.82 1.64 (21) III. RESULT AND
DISCUSSION
Nanoparticle addition in fluid base will result higher thermal
conductivity compared to a conventional liquid and conventional
two-phase mixture coolant. Solid particle are added as they conduct
heat much better than a liquid on its own. In this study, three
types of nanofluids were used as coolant in microchannel heat sink.
Performance of nanofluids as coolant were predicted in terms of
thermal conductivity, heat transfer coefficient, thermal
resistance, heat flux and required pumping power. The result was
compared with conventional liquid which is water. Table IV shows
the properties of water as coolant in MCHS with inlet velocity of 3
m/s.
TABLE IV. Properties of water in MCHS with inlet velocity of 3
m/s.
Properties Values Thermal conductivity, k (W/m.K) 0.6248 Heat
transfer coefficient, h (W/m2.K) 30111.41 Reynolds No, Re 405.87
Prandtl No, Pr 4.85 Nusselt No, Nu 4.75
The prediction of performance of CuO-water, SiO2-water and
TiO2-water nanofluids were calculated using Eq. (1)-Eq (21). The
calculated data is shown in Table V, Table VI and Table VII.
TABLE V. Thermal conductivity, heat transfer coefficient and
mass flow rate of CuO-water nanofluid.
CuO/Water
Particle Volume Fraction(∅ %) k(W/m.K) h(W/m2.K) ṁ (kg/s) 0.5%
0.63399 30584 0.01455 1.0% 0.64327 31055 0.01493 1.5% 0.65265 31525
0.01531 2.0% 0.66211 31993 0.01569 2.5% 0.67167 32460 0.01606 3.0%
0.68133 32926 0.01644 3.5% 0.69109 33392 0.01682 4.0% 0.70094 33856
0.01720
TABLE VI. Thermal conductivity, heat transfer coefficient and
mass flow rate of SiO2-water nanofluid.
SiO2/Water Particle Volume Fraction(∅ %) k(W/m.K) h(W/m2.K) ṁ
(kg/s)
0.50% 0.63374 30419 0.01438 1.00% 0.64277 30727 0.01459 1.50%
0.65189 31037 0.01480 2.00% 0.66109 31347 0.01502 2.50% 0.67038
31658 0.01523 3.00% 0.67977 31970 0.01544 3.50% 0.68924 32283
0.01565 4.00% 0.69881 32597 0.01586
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A. ThermTherm
and TiO2plotted rein Fig.2.fraction, water anW/m.K fshown
innanofluidtransfer renhancemhigher thThese res
B. Heat The t
increasinThe heat coolants the rangethe highetransfer c7.4%
res
TABLE V
Pa
mal Conductivmal conductiv2-water nanofesults show th The
differenand is as larg
nd finally 10.for CuO-waten Table V, Tdascompared trate, which
dment mechanihermal conducsults also com
Transfer Coefthermal perfo
ng effects of ttransfer coeffusing Eq. (5)
e of Reynoldsest volume frcoefficient wipectively for
VII. Thermal cond
article Volum0.5
1.0
1.5
2.0
2.5
3.0
3.5
4.0
vity of nanofluvity enhancemfluids was obthe thermal connce in
thermae as 12.2% at .0% for TiO2er, 0.69882 WTable VI anto other
nanof
directly indicaism may be ductivity compa
mparable with
Fig 2: Increas
fficient of nanormances of the nanofluid ficient was ca. Fig.
3a) exh
s number fromraction, CuO-ith the compathe same inle
ductivity, heat tra
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00%
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uids ment as a functtained using Hnductivity lineal
conductivitparticle volum
2-water nanofW/m.K for Sid Table VIIfluids is due toated the
high ue to the addi
are to the basother studies d
ing thermal cond
nofluids to MCthe nanofluidconcentration
alculated and eibits that ther
m 400 and also-water nanofl
arison of the Set velocity of
ansfer coefficient
TiO2/Water
%) k(W/m0.632
0.640
0.647
0.655
0.663
0.671
0.679
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tion of particlHamilton and early increasety enhancememe
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for inlet veo large particlthermal condition of these se fluid
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with increasluid providedSiO2-water an3 m/s. Also h
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le volume fracCrosser statics as the partic
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ds with particle v
n the conveche heat transf
ncrease if thermive enhancemesing of volum
around 12.4nd TiO2-wateheat transfer c
ate of TiO2-water
m2.K) ṁ (kg87 0.014
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ction for the Cc analysis mecle volume frawith the incr-water,
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CuO-water, Sithod from Eqaction increasereased particl
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fluid (water) wtivity of the n
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ansfer coeffict as shown in
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which found 8CuO-water Si
iO2-water q. (2). The es as seen le volume for SiO2-t 0.70094
ofluids as
CuO-water igher heat icles. The which has nanofluid.
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heat
8.22% and iO2-water
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and TiO2percentagby inlet vit will inSo, the sias a bette
Additthe chaotincrease transfer cof nanopand 3057water nanin
Fig.3b
Fig 3a): I
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Increasing heat tr
33847 W/me 3.0 m/s inlee coolant and noparticles mrease in
Nusstead of a convarticles in liqt of nanopartif nanofluids
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and lead to an ncreasing ther
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nt with particle vote Fig 3c) Increas
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tranofCuO-water
f the base liqun of nanopart
Eq.(5) it showsreasing volumflow rate of 0
mass flow rate inlet velocity
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% volume influenced d velocity, nsfer rate. nanofluid
uid due to ticles will s that heat
me fraction 0.015 kg/s for CuO-as shown
on of mass
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increasesof heat f2485kW/however higher thincreasesheat flux
C.Therm
MCSH, mfound thaconvectiv4 represethe CuO-in convec
C. PumpAnother pumpingthicknessall types
High heat fluxs for all typesnflux in CuO-/m2 for TiO2-wits
thermal c
hermal condus the thermal as shown in F
al Resistance Thermal resismass flow ratat the increasive
thermal resents the divers-water, SiO2-wctive heat tran
ping Power important par power. Params Ww, and inlof
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x removal is cnanofluids wi-water was fowater nanofluonductivity
is
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Fig.3c). of nanofluids
stances are the of the nanoing the volumsistance and thsity of
the conwater and TiOnsfer coefficie
Fig.4: Decrea
rameter in themeters that inflet velocity V are shown in
crucial for eleith increasing found to be 2uid at 4% of vs lower
than maddition of mof the coolan
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me concentratihermal dispernvective thermO2-water nanoent
ultimately
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Vm .Using Eq.Figure 7.
ctronic devicevolume fract
2575 kW/m2, volume fractiomost metal an
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f many paraml conductivityion of the nanrsion for all comal
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ation is the prpressure drop (20), the pre
es. From this ion of nanopa
followed byon. Water has nd metal oxid
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meters such asy, k, and channnoparticle showoolants and co
with the dispange of Reynothermal resist
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in thermal re
s heat transfernel depth, H. ws a declinin
onsistently canparity of the volds number otance of the na
olume fraction
which relates width Wc, cha
for pressure
found that themaximum enh
for 2501 kWs a single-phasal and metal ase-fluid or w
esistance and
r coefficient, By using Eq.
ng trend to dimn be seen at Folume concen
of 400. Thus, eanofluid.
to the requireannel height Hdrops was ob
e heat flux hancement W/m2 and se coolant oxide has water can
give high
h, area of . (12) it is minish the ig. 4. Fig.
ntration of enhancing
ed coolant Hc, bottom btained for
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Fig.7: a):
as the vo1021 kg/increasinthe viscopower redirectly pThe
pumnanofluidsink. Them/s inletfrom 75.between directly
nanofluid
Increasing pressu
Fig.7a) demoolume percent/m3 at 0.5% ong volume fracosity of
nanoflequired in theproportional t
mping power ads,it has causee pumping pot velocity. Th0 W up to
90pumping powdependence od.
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nstrates the intage for all typof volume fracction with maluid
is larger te nanofluids Mo pressure droalso depends edmore
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ower for CuO-he observed tr0.6 W with inwer with pressuon the
higher
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ncreasing linepes of nanofluction and 4792aximum pressuthan the
pure MCHS operatiop thus whenon the nanofr needed to d-water was
forending also ancreasing voluure drop for ar density and
m/s inlet velocity.
early in pressuuids. From the25 Pa pressurure drop of 54fluid, a
largerion. From Eq
n pressure dropfluid concentrrive the coola
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ure drop as the result, it shore drop. The p4314 Pa at 4%r
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increases lationship ssure drop
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ISSN (Print) : 2319-8613 ISSN (Online) : 0975-4024 Siti Natasha
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2017 2635
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In order coefficienof MCHSCOP dec
This studdioxide (inlet veloconductivconfirmethermal pcould
bemicro-scawith the fluid velothe increapower is heat
tranexperime
The authHigher Egiven to t
[1] R. DaB: Ap
[2] T.S. TFlow,
[3] N. A.engin
[4] E. M.using
[5] E. B. TopraScien
[6] M. R.heat t74, pp
[7] A. Gcondi
[8] R. SaEnerg
to measure ent of performaS as thermoph
creases with th
dy analysed t(SiO2)/water aocity. Mathemvity, heat tra
ed that at higperformances proposed as ale equipmenincrease of
p
ocity entrancease of volumerequired to m
nsfer by reduental analysis.
ors would likeEducation of Mthe authors in
avarnejad and R. pplications, vol. 2Tsai and R. Chein, vol. 28,
pp. 1013 Roberts, and D.
neering, vol. 30(16. Tokit, H. A. Mnanofluids,” InteHaghihi, M.
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Y. Leongy Reviews, vol.
efficiency of ance of the Mhysical prope
he increasing v
the thermal pand titanium
matical formulansfer coefficgher particle v for
electronipotential sub
nts. The resultparticle volume effects and ae fraction and move
the coolucing the the
e to acknowleMalaysia and Un carrying out
M. Ardehali, “M27, no.2, pp. 195-n, “Performance 3-1026, Mar.
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Fig.8: COP wit
nanofluids asMCHS. This anerties of nanofvolume fractio
IVperformance odioxide (TiO
lation were usient, thermal volume fractiics cooling cobstitutes
for cts revealed th
me fraction ofas function ofit is affected
lant. The voluermal resistan
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s coolant for nalysis shows fluid changedon
nanoparticlV.CONCLUSIOof rectangular2)/water nano
sed to comparresistance, h
ion the CuO-ompared to S
conventional chat there is cof nanofluids.Ff Reynolds nuthe
amount oume fraction nce of MCH
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Technology (IJET)
DOI: 10.21817/ijet/2016/v8i6/160806219 Vol 8 No 6 Dec 2016-Jan
2017 2636
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AUTHOR PROFILE
Siti Natasha Malik Fesalreceived the Bachelor degree and
Masterin Mechanical Engineering from UniversitiTun Hussein Onn,
Bt.Pahat,Johor in 2004 and 2015, respectively. Currently she is
working as lecturer at Mechanical Department, Polytechnic
UngkuOmar, Ipoh, Perak.
SitiSyazwaniIlminreceived the Bachelor degree in Applied Science
of Maritime Technology from Universiti Malaysia Terengganu, Kuala
Terenganu, Terenganu in 2010 and Masterin Mechanical Engineering
from University Tun Hussein Onn,Bt.Pahat,Johor in 2015. Currently
she is working as lecturer at Mathematics Science and Computer
Department, Polytechnic UngkuOmar, Ipoh, Perak
ZurainiGanireceived the Bachelor degree in Mechatronic from
KolejUniversitiTun Hussein Onn (KuiTTHO), Bt.Pahat, Johor in 2002
and Master in Mechanical Engineering from Universiti Kebangsaan
Malaysia, Bangi, Selangor in 2010. Currently she is pursuing
post-graduate studiesat Mechanical Engineering Department,
University Kebangsaan Malaysia,Bangi,Selangor.
ISSN (Print) : 2319-8613 ISSN (Online) : 0975-4024 Siti Natasha
Malik Fesal et al. / International Journal of Engineering and
Technology (IJET)
DOI: 10.21817/ijet/2016/v8i6/160806219 Vol 8 No 6 Dec 2016-Jan
2017 2637