This document describes an experimental investigation of heat transfer enhancement in double tube heat exchangers using nanofluids. Six different double tube heat exchanger configurations were tested with and without nanofluids. Aluminum oxide nanoparticles were dispersed in water at 0.4%, 0.6%, and 0.8% volume concentrations to create nanofluids. Experimental results showed that heat transfer was increased by using circular finned tubes, and that nanofluids further improved heat transfer over water alone, with higher nanoparticle concentration and Reynolds number resulting in better performance. Heat transfer coefficient and thermal conductivity were found to increase up to 19.9% and 3% respectively for a 0.8% alumina nanofluid. Empirical correlations were

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International Journal of Mechanical Engineering and Technology (IJMET)
Volume 7, Issue 3, May–June 2016, pp.86–101, Article ID: IJMET_07_03_008
Available online at
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EFFECT OF ( ) NANOFLUID ON HEAT
TRANSFER CHARACTERISTICS FOR
CIRCULAR FINNED TUBE HEAT
EXCHANGER
Dr. Qasim S. Mahdi
Prof., Mechanical Engineering Department, College of Engineering,
Al Mustansiryah University, Baghdad–Iraq
Dr. Kamil Abdul_Hussein
Asst. Prof., Mechanical Engineering Department, College of Engineering,
Wasit University, Kut–Iraq
Aghareed Mohammed Isfayh
MS.c Candidate, Mechanical Engineering Department, College of Engineering,
Wasit University, Kut–Iraq
ABSTRACT
In the present work Experimental investigation of heat transfer
enhancement in double tube heat exchanger and circular finned double tube
heat exchanger. Experimental work included to design heat exchanger and
manufacture eight circular fins made of copper of (66mm) outer diameter,
(22mm) inner diameter, (1mm) thickness and (111.11mm) distance between
fins.
Six double tube heat exchangers have been studies:
Double tube heat exchanger consisted of annuli tube and straight copper tube.
Double tube heat exchanger consisted of annuli tube and circular finned tube.
Double tube heat exchanger consisted of annuli tube and circular finned tube with
three circular perforations at (120˚) angle and diameter (10mm) and (14mm).
Double tube heat exchanger consisted of annuli tube and circular finned tube with
four circular perforations at (90˚) angle and diameter (10mm) and (14mm).
The straight copper tube is of (1m) length, (19.9mm) inner diameter and
(22.2mm) outer diameter. The inner tube is inserted inside the insulated PVC tube of
(100mm) inner diameter. Sheet and roll insulation (arm flux) have been utilized to
cover outer surface of PVC tube for reducing heat losses. Cold water at various mass
flow rates (0.015 to 0.022) kg/sec flows through annuli and hot water at Reynold's

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numbers ranging from (750 to 2060) flows through the inner tube. Experimental
results showed (3.12 to 3.83) enhancement ratio when using circular finned tube heat
exchanger with three perforated of diameter (14mm). Oxide Aluminum
nanoparticle powder is dispersed in distilled water with different volume
concentrations (0.4, 0.6, and 0.8) % by volume is used as nanofluid. The nanofluids
were prepared by using ultrasonic cleaner with 10 hours of continuous sonication at
720 W (sonication power). The sedimentation in nanofluids was observed after about
six hours. The experimental results showed an increase in convective heat transfer
coefficient by increasing both volume concentration and Reynold's number. Heat
transfer coefficient and thermal conductivity increase at 0.8% volume concentration
by (19.9% and 3%) respectively when using alumina-nanofluid.
Six empirical correlations have been developed to predict Nusselt number for
double tube heat exchanger.
GENERAL TERMS
Q: Heat dissipation. (w), A : Area (m2
), h : Heat transfer coefficient (W/m2
.°C), Nu :
Nusselt number, Re : Reynold number, m.
: Mass flow rate (kg/s), Nf :Number of fins,
n:Number of perforations, T: Temperature (°C), Cp:, Specific heat of the fluid
(J/kg.°C), d: tube diameter (m), hi: inner side heat transfer coefficient (W/m2.°C), ho:
out side heat transfer coefficient (W/m2.°C), L: length of tube (m)., Ts: surface
temperature (°C), Tm: mean temperature (°C), Ui: inner side overall heat transfer
coefficient (W/m2.°C), Uo: air side overall heat transfer coefficient (W/m2.°C), uw :
velocity of water (m/s), ΔT: temperature difference (°C), ρw: density of water
(Kg/m3), μw : visocity of water (kg/m.s). Knf: thermal conductivity of nanofluid
(W/m.°C), : thermal conductivity of water (W/m.°C), : Nesselt number of
nanofluid : thermal conductivity of nanoparticale(W/m.°C),
: visocity of
nanofluid (kg/m.s), : visocity of water (kg/m.s). :φ volume fraction of
nanoparticles
Key words: Nanofluid, Nanoparticles Double tube heat exchanger, Circular
finned tube with three and four perforations, Laminar flow, Counter flow,
Heat transfer coefficient, Enhancement.
Cite this Article Dr. Qasim S. Mahdi, Dr. Kamil Abdul_Hussein and
Aghareed Mohammed Isfayh, Effect of ( ) Nanofluid on Heat Transfer
Characteristics for Circular Finned Tube Heat Exchange. International
Journal of Mechanical Engineering and Technology, 7(3), 2016, pp. 86–101.
http://www.iaeme.com/currentissue.asp?JType=IJMET&VType=7&IType=3
1. INTRODUCTION
Nano technology is creation of functional materials, devices, and system by
controlling matter at the nano – scale level, and the exploitation of their novel
properties and phenomena that emerge at that scale. Nanofluids have attracted
attention as a new generation of heat transfer fluids with superior potential for
enhancing the heat transfer performance of conventional fluids. These fluids are
obtained by a stable colloidal suspension of low volume fraction of ultrafine solid
particles in nanometric dimension dispersed in fluid, such as water, ethylene glycol or
propylene glycol in order to enhance or improve its rheological, mechanical, optical,
and thermal properties. Nanofluids consist of a base fluid and nanoparticles.

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Nanoparticles are particles which are between (1 and 100) nm in diameter. Nanofluids
typically employ metal or metal oxide nanoparticles, such as copper and alumina, and
the base fluid is usually a conductive fluid, such as water, ethylene glycol and others.
Nanofluids are studied because of their heat transfer properties. They enhance the
thermal conductivity and convective properties over the properties of the base fluid
[1]. The convective heat transfer is very important for several industrial heating or
cooling equipment.
The technology of nanofluid may support the current industrial trend to
components and system miniaturization by enabling design of smaller and lighter heat
exchanger systems. Miniaturized systems may reduce the inventory of heat transfer
fluid and can result in cost savings [2].
It represents the ratio of nanoparticle to the total volume of nanofluid. It has a
very important effect on nanofluid properties as (thermal conductivity, specific heat,
density and viscosity). Thus, it plays a crucial role in nanofluid applications.
Nanofluids can be used to improve heat transfer and energy efficiency in a variety
of thermal system. Nanofluids appear to be a very interesting alternative heat transfer
fluids for many advanced thermal applications [3].
Heris et al.(2006) [4] studied experimentally nanofluids including (CuO and AL2O3)
nanoparticles in water as base fluid in different concentrations produced and laminar
flow convection heat transfer during (1m ) length circular copper tube and with
constant wall temperature boundary condition. Results indicate for using nanofluid
systems heat transfer coefficient is enhanced ith increasing nanoparticles
concentrations. The maximum enhancement is 29% and 23% for (AL2O3 /water) and
(CuO/water) respectively. In addition, an optimum concentration can be found for
each nanofluid systems in which better enhancements are available. It was concluded
that heat transfer enhancement by nanofluids depend on many factors including
increment of thermal conductivity, fluctuation and interaction of nanoparticles. The
experiment was performed by a widely range of Reynold number (650-2050) and for
(0.2-3.0 % Vol.) concentrations of (AL2O3 and CuO) nanoparticles.
Jung et al.(2006) [5] studied experimentally convective heat transfer for (water/Al2O3
) nanofluid in a rectangular micro channel (50 x 50) µm 2
of laminar fluid flow
conditions. The convected heat transfer coefficient can be increased larger than (32
%) for 1.8 vol % of nanoparticles in base fluids. Nusselt number increased with
increase Reynolds number in this region (5 < Re < 300). Depended on the results,
they suggested new correlation of convected heat transfer for nanofluids.
Diameter with respect to each micro channel ranges from 60μm to 120μm, and the
length of each segment is 800μm.
Firas (2014), [6] performed an experimental and numerical investigation for heat
exchanger with U-longitudinal finned tube to study its performance with water and
with nanofluid. (Al2O3 andTiO2) nanoparticles with nano concentrations (0.2%, 0.4%,
0.6% and 0.8%) were used to prepare nanofluid. For experimental results with
nanofluid, the convective heat transfer coefficient was increased with increasing of
both Reynold's number and nano concentration. At (0.8%) volume concentration, the
heat transfer coefficient increase by (21%) and thermal conductivity increased by
(5%), when using (Al2O3) nanofluid. Also, the heat transfer coefficient increase by
(16%) and thermal conductivity increased by (4.4%), when using (TiO2) nanofluid.

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Asmaa, et al (2015)[7]studied experimentally the enhancements of heat transfer
coefficient and Nusselt number in a heat exchanger system by using Titanium-dioxide
(TiO2) nanoparticles with an average diameter of (10 nanometer), experimental results
show that the Nusselt number increased by (17%) as with respect to water at a
(0.0192) m/s nanofluid velocity at inlet temperature of (60) o
C.
2. PREPARATION OF NANOFLUID
Two – step methods have been used to prepare the nanofluid. The first step is
Preparation of nanofluid by applying nanoparticles for enhancing the convective heat
transfer performance of fluid. The nanofluid does not easily refer to a liquid – solid
mixture, but some special requirements are essentially, as even "suspension, stable
suspension, durable suspension, low agglomeration of particles", and no change in
chemical properties of fluid.This process is very difficult and complex and these
nanoparticles are expensive and costly. The second step is dispersing the nanopowder
in the base fluid.
2.1. Nanoparticles and Basefluid
In the present study, the nanoparticles have been Utilized alumina Al2O3, and distilled
water is used to make Nanofluid. [8].
Table 1 Shows physical properties of nanoparticle (Al2O3).
Particle Mean diameter nm Density kg/
Thermal
conductivity
w/m.
Specific heat
J/kg.
Al2O3 20-30 3970 40 765
3. OBJECTIVES OF THE RESEARCH
3.1. The Aims
This study aims to enhance the heat transfer characteristics for heat exchanger with
use of nanofluid as a working substance.
3.2 The Scope
Design the test section counter flow heat exchanger to obtain the flow and heat
transfer coefficient for smooth, circular finned tube and circular finned tube with
perforations, investigate the effect of using ((Al2O3) nanofluid instead of hot water on
heat transfer characteristics of circular finned tube with three perforations will be
carried out experimentally , develop empirical correlations for Nusselt number for
inner side of as function of Reynold's number, Prandtl's number. and empirical
correlations for hot water and nanofluid.
4. THEORITICAL EQUATIONS
The heat transfer rate are computed by heat balance according to first law of
thermodynami [9]:
Q c= Cpc ( ) (4-1)
And:
Q h = Cp h ( ) (4-2)

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Figure 1 Temperature profiles in a counter-flow.
In heat exchanger analysis, it is always convenient to share the product of the
mass flow rate and the specific heat of a fluid into a single quantity. This quantity is
named the heat capacity rate and is defined to the hot and cold fluid streams as:
Cc = Cp c and C h= Cp h (4-3)
With the heat capacity rate, equations (3-1) and (3-2) can also be expressed as:
Q c= Cc ( ) and Q h = C h ( ) (4-4)
The rate of heat transfer in a heat exchanger also can be showed in the following
formula:
(4-5)
The correction factor can be taken (1). This is because of the counter flow
arrangement within the present heat exchanger
Logarithmic mean temperature difference is estimate from the relation [10]:
= (4-6)
Where:
The overall heat transfer coefficient (U) for heat exchanger typically contains two
flowing fluids separated by a solid wall (for counter flows) [11].
= (4- 7)
The calculation of inner side heat transfer coefficient (laminar flow) for hot water is
achieved:
(4-8)
Where:
the average surface temperature is calculated according to expression:

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Then Nusselt's number in inner tube can be calculated as follows:
(4-9)
Reynold number for inner side:
Re= (4-10)
For smooth tube, (ho) can be calculated as:
ho= 4-11)
Reynold number can be calculated as:
Re = (4-12)
And the hydraulic diameter is:
= - (4-13)
For finned tube the hydrulic diameter is calculated according to expression:
(4-14)
Where:
(4-15)
And:
(4-16)
The Nusselt's number of annuli side can be estimated as:
Nu= (4-17)
Where:
(4-18)
Where:
= (4-19)
For finned tube with perforations the the hydrulic diameter is calculated according
to expression:
+ (4-20)
And:
(4-21)
The Nusselt's number of annuli side can be estimated as:
Nu= (4-22)
Where:
(4-23)

7. Dr. Qasim S. Mahdi, Dr. Kamil Abdul_Hussein and Aghareed Mohammed Isfayh
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Where:
= - (4-24)
4.1 Thermo-physical Properties of Nanofluid.
4.1.1 Volume Fraction.
The volume fraction (φ) is the percentage of volume of nanoparticles to the mixture
volume of base fluid (water) with nanoparticles.
4.1.2 Thermal Conductivity
Many semi empirical correlations were reported to calculate the nanofluid effective
thermal conductivity, Maxwell formulated the following expression [12].
(4-26)
4.1.3 Densit
The nanofluid density is calculated by (Pak and Cho) correlations, [13]
4.1.4 Specific Heat
The specific heat is calculated from Xuan and Roetzel as following, [14].
4.1.5 Viscosity
The viscosity of the nanofluid can be calculated using the Drew and Passman
relation, [15]
5. EXPERIMENTAL SET UP
5.1. Preparation of ( ) Nanofluid
The process of preparation of stable nanofluid with no agglomeration is the first step
in the experimental procedure which uses the nanofluid in heat transfer enhancement.
Nanoparticle that is using to preparation of nanofluid is expensive in price and
dangerous in treatment. Two-step method is used in preparation of nanofluid in
present work. This method requires produce nanoparticle, then the ultrasonic vibration
homogenizer device is used for mixing with the base fluid. The ultrasonic device was
filled with water to make sure no damage will happen to the device as recommended
by the instructions of the supplier, and then the basket was put inside the bath.
( ) nanoparticles are mixed with distilled water after weighting it by electronic
balance. A (3) liters of distilled water are used in all volume concentration. Four
volume concentrations of ( ) nanofluid have been used in this study are shown
with weights in table (6.1). The ultrasonic vibration homogenizer device is shown in
figure (2).

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Table 2 Weight of ( ) nanoparticles with volume concentrations.
Volume Concentrations (%) 0.04 0.06 0.08
Weight of ( ) powder (grams) 16.33 38.18 60.12
Figure 2 Photograph of ultrasonic vibration homogenizer device
5.2 Test section
The test section consists of double tube configuration, where cold water flows in
annuli side while hot water flows inside the tube. Annuli side was produced from
PVC tube of (100mm) inner diameter, (1.52m) length and (5mm) thickness. It is
insulated from outside by sheet and roll insulation (arm flux) which has (25.4mm)
thickness, (0.036 ) thermal conductivity, to reduce heat losses to the minimum
level as shown in figure (1). The annuli side was ended by two caps of (120 mm) out
diameter made from PVC. These caps drilled in the center part to make a hole of
(22mm) diameter. This hole allows to enter the copper tube through it. To prevent the
water leakage from end of the annuli side silicone is used on both annuli side caps.
The inner tube side is made of copper with or without circular copper fins. The
smooth copper tube has (1.85m) long, (19.9mm) inner diameter and (22.2mm) outer
diameter. Circular fins are manufactured from copper. Eight fins are fixed perfectly
on the external surface of tube having (22mm) inner diameter, (66mm) outer
diameter, (1mm) thickness and (111.1mm) distance between each two fins as shown
in figure (2). Also manufactured fins with three perforations at an angle 120 degree
and fins with four perforations at an angle 90 degree of (10mm) and (14mm) diameter
as shown in figure (3).All these parts dimensions test rig appear in the schematic
diagram in figure (4).

9. Dr. Qasim S. Mahdi, Dr. Kamil Abdul_Hussein and Aghareed Mohammed Isfayh
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Figure 3 Experimental test rig
Figure 3 Circular finned tube.
Figure 4 Types of fin

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Figure 5 Schematic diagram for test rig.
5.2.2 The hot and cold water cycles
It includes cold water storage tank, main water heater, water pumps and pipes.
 Cold Water Storage Tank
Cylindrical tank has capacity of (500 liter) that may be used for storage and supply
system with cold water.
 Main Water Heater :
Electric water heater has been used to heat water passing through heat exchanger. It
was made of galvanized material and insulated by sheet and roll insulation (arm flux)
which has (25.4mm) thickness, (0.036 ) thermal conductivity. Electric water
heater is operated with 220V, 1 kw and capacity 20 liter.
 Water Pumps:
Two type of water pumps were used to circulate water through experimental test rig
.One type is called a centrifugal pump which is driven by electrical motor having
(220V), (370 W) and it has a maximum volumetric flow rate (36 liter/minute) and a
maximum head (33 m). It was used to pump the water in tubes of cold water cycle.
Another type of pump is water pump with (220V). It has a maximum flow rate of
(1000 liter/hr). Water pump is used for pumping hot water from water heater to inlet
tube side. Fig. (5) show a schematic diagram of air supply system.
6. MEASUREMENT DEVICES
The temperature measuring device used in the present work are:
A 12- channel temperature recorder,type (K), range (-100 to 1300) °C were used
for measuring water temperature in test section and in the inlet and outlet of the test
tube. Nine thermocouples are used during the experimental work. The other
measurement devices are:
[Temperature recorder, flow meter and pressure gauges]. Fig (5) shows the
photography of 12- channel temperature recorder.

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Figure 6 Temperature recorder
7. UNCERTAINTY ANALYSIS
Random Error refers to “the spread in the values of a physical quantity from one
measurement of the quantity to the next, caused by random fluctuations in the
measured value. The solution is to repeat the measurement several times”; this
uncertainty analysis is based on the method is suggested by the reference [17].
The maximum measurement uncertainties were: the heat flux , while
for the heat transfer coefficient, for the Nesselt number and
for the vibrational Reynolds number.
8. RESULTS AND DISCUSIONS
Figures (7, 8, 9 and 10) show properties after adding nanoparticles with
concentrations of (0.4%, 0.6%, 0.8%) to the distilled water. The thermal conductivity
is the most important property, therefore, figure (7) shows increasing the thermal
conductivity by increased the concentration of nanoparticles, the maximum increase is
(3%) with volume fraction of (0.8%). The density increases by increasing volume
fraction as shown in figure (8), the maximum increment in density is about (2.5%) at
volume fraction of (0.8 %). Figure (9) shows decreasing of the specific heat with
increasing the concentration of nanoparticles, maximum decrement is about (2.5%).
The viscosity is increased by increasing, the maximum increment in vicosity is about
(8.5%) at volume fraction of (0.8 %) the concentration of nanoparticles as shown in
figure (10).
Figure (11) clarify the variation of heat dissipation rate with water and different
nano concentration for circural finned tube with three perforation of diameter (14mm)
at different Reynold number. It's clear from these figures increasing of heat
dissipation rate with increasing of ( ) nanoparticles in the nanofluid at similar
boundary conditions. The maximum enhancement was (12.4%) occurs at nano
concentration of (0.8%).
Figure (12) reveal the variation of inner side heat transfer coefficient with
different nano concentration for circular finned tube of diameter (14mm) at different
Reynold number. These figures present the increasing of air side heat transfer

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coefficient (hi) with increasing of ( ) nanoparticles in similar boundary
conditions. The maximum enhancement of ( ) nanofluid was (19.24%) over
the use of water.
Figure (13) show the variation of inner side Nusselt's number with different nano
concentration for circular finned tube with three perforations of diameter (14mm) at
different Reynold number. These figures reveal the increasing of inner side Nusselt's
number (Nu) with increasing of ( ) nanoparticles at similar boundary conditions.
Nanofluid makes a maximum enhancement of (18%) over the water.
9. CONCLUSIONS
The following comments could be concluded:-
 The heat dissipation rate (Q) are increase with the increase of nanoparticle
concentration in the water, the maximum percentage of enhancement was (12.4%)
over the base fluid, occurs at (0.8%) nanoparticle concentration.
 The inner side heat transfer coefficient are increase with the increase of nanoparticle
concentration in the base fluid, for finned tube with nanofluid, The maximum
percentage of enhancement was (19.24%) over the base fluid, occurs at (0.8 %)
nanoparticle concentration.
 The inner side Nusselt's number are increase with the increase of nanoparticle
concentration in the base fluid, The maximum percentage of enhancement was (18%)
over the base fluid, occurs at (0.8%) nanoparticle concentration
 Increasing the nanoparticle concentration in the nanofluid have a substantial effect on
enhancement of thermal conductivity and heat transfer coefficient, at the same time,
it's increasing the density and viscosity, whereas decreasing the specific heat.
Figure 7 Relation between ( ) at different volume concentration

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Figure 8 Relation between at different volume concentration
Figure 9 Relation between ( ) at different volume concentration
Figure 10 Relation between ( ) at different volume concentration.

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Figure 11 Effect of volume concentration on heat dissipation at different Reynold number for
alumina-nanofluid.
Figure 12 Variation of inner heat transfer coefficient with volume concentrations of alumina-
nanofluid at different Reynolds number.
Figure 13 Variation of Nusselt number with different volume concentration for alumina-
nanofluid at different Reynold number.

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ACKNOWLEDGMENTS
I would like to express my deep thanks and respect to Prof. Dr. Qasim S. Mahdi, Dr.
Kamil Abdul Hussien and all members of the (College Of Engineering / Mechanical
Engineering Department at the University of Wasit) for their cooperation.
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