EFFECT OF (AL2 O3) NANOFLUID ON HEAT TRANSFER CHARACTERISTICS FOR CIRCULAR FINNED TUBE HEAT...

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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

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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

Effect of ( ) Nanofluid on Heat Transfer Characteristics For Circular Finned Tube Heat

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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/m

2.°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.

http://www.iaeme.com/currentissue.asp?JType=IJMET&VType=7&IType=2

Dr. Qasim S. Mahdi, Dr. Kamil Abdul_Hussein and Aghareed Mohammed Isfayh


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) oC.

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)



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)



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).



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.



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



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.



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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EFFECT OF (AL2 O3) NANOFLUID ON HEAT TRANSFER CHARACTERISTICS FOR CIRCULAR FINNED TUBE HEAT...

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