improvement of heat transfer by nanofluid and magnetic...

International Journal of Mechanical & Mechatronics Engineering IJMME-IJENS Vol:20 No:03 110

I J E N S 2020 IJENS JuneIJENS © -IJMME-7171-202303

Improvement of Heat Transfer by Nanofluid and

Magnetic Field at Constant Heat Flux on Tube

Humam Kareem Jalghaf1*, Ali Habeeb Askar1*, Mahir Faris Abdullah2*

*Corresponding author: [email protected]*, [email protected], [email protected] 1Department of Mechanical Engineering, University of Technology, Baghdad-Iraq

2Department of Refrigeration and Air Conditioning Engineering, Al-Rafidain University College. Iraq.

Abstract-- This paper experimentally probes the impacts of

using nanoparticles with and without the use of a magnetic field

throughout flow behaviour characteristics and the heat

transfer rate on forced convection heat transfer of Fe3O4–

water nanofluid with laminar flow regime in a horizontal tube

under constant heat flux conditions. The base working fluid is

distilled water, and the added nanoparticles are Iron Oxide

(Fe3O4), with a volume fraction of (φ = 0. 3, 0.6 and 0.9%). The

intensity of supplied magnetic field is (0.1Tesla). The

experiments are conducted at different constant heat fluxes

(12.7, 15.9, 19.8 kw/m2), two different inlet temperatures (23, 45

o C), four different flow rates (2, 3, 3.5, 4, l/min) and a wide

range of Reynolds numbers (3930-7860). It was derived from

the experiment that an increase in the concentration of

nanofluids and in the heat flux, resulted in an increase in

Nusselt number. Furthermore, it was found that the use of

magnetic intensity enhances the heat transfer even further. The

maximum enhancement in Nusselt number is about 18.3%

without using a magnetic field, whereas it becomes

approximately 20.1% when supplied with a magnetic field at a

nanofluid concentration of (φ = 0.9%) and lower heat flux. It is

proven that as the inlet temperature increases, the heat transfer

decreases.

Index Term-- magnetic nanofluids, heat flux, heat transfer,

Fe3O4, Ferro fluid.

NOMENCLATURE

As Cross-sectional area (m2) B Magnetic field (Tesla) Subscripts

Q Heat transfer rate (W) q Heat flux (W/m2) CCl4 Carbon tetrachloride

C Specific heat (J/kg.K) Re Reynolds number (-) H heat

Nu Nusselt number (-) t time (sec) f fluid

f Friction factor T Temperature (K) (i,o,s) in , out ,surface

h Heat transfer coefficient (W/m2.K) Volume fraction of nanofluid w water

f Friction factor ρ Mass density (kg/m3) nf Nanofluid

𝑙 Length of the test section (m) V Voltage (volts) x Distance

k Thermal conductivity (W/m.K) γ Specific weight pf Particle fluid

ΔP Pressure drop across the tube u Velocity (m/s) v vessel (aluminum vessel)

I Electric Current (A) r Radius of pipe (m) f fluid

D Diameter (m) Volume fraction of nanofluid P Particle

1. INTRODUCTION

Over the years, many researchers faced setbacks in

addressing issues related to heat transfer in engineering

systems. To overcome the problems, a limited number of

methods were employed. In one such approach, heat

transfer could be refined by improving the efficiency of

industrial and engineering applications [1–5]. Studies

indicated that nanofluids were a feasible coolant that

upgraded many engineering devices' performance

efficiency [6].

Magnetic fluid, also called ferrofluid, is a magnetic

colloidal suspension consisting of magnetic nanoparticles

such as iron, nickel, cobalt and their base fluid oxides, and

so on. This magnetic fluid behaves as an intelligent and

functional fluid due to its special properties. As a result, it

finds its niche in different fields such as electronic

packaging and mechanical packaging [7-10].

Nanofluid is a suspension of nanoparticles such as Fe3O4-

in distilled water. The thermal conductivity of most solids

is greater as compared to conventional heat transfer fluids.

Different techniques and methods to reduce the

temperature of surfaces with a high heat transfer rate have

been proposed, all of which enhances the heat transfer rate.

The basis of these techniques comprises of the application

of an electrical or a magnetic field, vibration of a heated

surface, structure variation or injection as well as suction

mailto:[email protected]:[email protected]:[email protected]



of a fluid, as proposed by Razi and Saeedinia [11]. Al-

dulaimy [12] conducted a study of Al2O3/water nanofluid

in examining the laminar force convection with two

different mass flow rates and heat fluxes of 150, 90,

50W/cm2. An experimental study was undertaken by

Saeedinia and Nasr [13] with the principal aim of analysing

heat transfer rate in addition to the pressure drop of a

laminar flow nanofluid, specifically known as CuO/Base

oil, where this experiment was conducted with different

insertions of coils in a tube under a known and constant

heat flux. It was observed that, on an average, at the highest

values of the Reynolds numbers within the tube inserted

with wire coils, the heat transfer coefficient peaked at 45%,

whereas the pressure drop diminished by 63%. Malvandi et

al. [14] theoretically studied the migration of nanoparticles

on a magneto-hydrodynamic heat transfer by convection

for a nanofluid denoted as alumina/water, flowing through

the inlet side of a microchannel placed vertically. The

boundary condition was specified as a boundary subjected

to varying heat fluxes, and the results demonstrated that

nanoparticles accumulated in the core zone of the heated

walls. Additionally, they tend to accumulate in a region

near the wall close to the lower heat transfer rate.

Furthermore, it was stated that the asymmetric distribution

of the nanoparticles increases the heat transfer rate as

nanoparticles causes velocities that produced movements

headed to the wall, which has a higher thermal energy.

Contrarily, Sheikholeslami et al. [15] conducted an

experimental analysis of heat transfer by the means of

forced convection in a lid-driven semi annulus enclosure

filled with a nanofluid denoted as Fe3O4-water, with an

asymmetric magnetic flux. The assumption made was that

the fluid temperature increased linearly with the intensity

of the magnetic flux as well as with the magnetisation of

the fluid. The governing equations were solved by

vorticity-stream, a finite element method based on the

management of the volume. The equations were solved for

certain parameters such as the Hartmann, Reynolds and

volume fraction of the nanoparticle varieties. It was

observed that the Reynolds number variety increased

linearly with the volume fraction of the nanoparticle,

however, it was on the contrary with the Hartmann variety.

Moreover, Hatami et al. [16] experimentally investigated

magnetic flux under forced convection heat transfer for a

nanofluid, denoted as Fe3O4–water, with a laminar flow

behaviour contained in a pipe placed horizontally and

under constant heat fluxes. The heat transfer rate was

measured by means of convection inside a pipe subjected

to a heat flux, as previously mentioned, with a magnetic

fluid flowing through it. It was observed that the

dimensions of the Fe3O4 nanoparticles were approximately

100 nm with different concentrations and are well

distributed in the water. The results showed an external

flux, Ha, between 33.4x10-4 and 136.6, and with a

concentration of nanoparticles of 1%, 0.5%, 0.1% and 0%,

which is conceded to study the characteristics of the heat

transfers. Also, the results of this investigation indicated

that the presence of a heat flux in the pipe increases the

concentration of nanoparticles, which caused a decline in

the heat transfer coefficient. The study was also conducted

on heat transfer without an external flux, and it was

observed that the addition of magnetic nanoparticles

enhanced the convection heat transfer by 60 times.

Moreover, it was noted that the Nusselt variety diminished

with an increase in the Hartmann variety for a specified

magnetic nanofluid concentration, and this reduced the heat

transfer rate by 25 times. On the other hand, Karamallah et

al. [17] conducted an experimental analysis on the distilled

water flow and nanofluids, as well as in the heat transfer

rate for concentrations of 0.9%, 0.6% and 0.3% in a pipe

placed horizontally and subjected to a uniform magnetic

field. The experimental analysis was conducted with a

varying Reynolds number from 2900 to 9820, and using a

uniform heat flux from 11262 W/m2 to 19562 W/m2. It was

observed that the concentration of the nanofluid, the

Nusselt Number as well as the intensity of the magnetic

field rose. The maximum percentage increases of the

Nusselt numbers with a magnetic nanofluid were 42.7%,

26.4% and 5.4% for the volume concentrations of 0.9%,

0.6% and 0.3% respectively. Conjointly, with a volume

concentration of 0.9%, the enhancement of the intensity of

the magnetic field was 0.1, 0.2 and 0.3 Tesla, with

percentage increases of 43.9%, 44.3% and 46%

respectively. The enhancement on the heat transfer rate

decreased as the Reynolds number increased when the

magnets were used. On the other hand, the friction factor

raised its magnitude when the volume concentration

increased, while the magnet intensity diminished with an

increase of the Reynolds number. A similar study was

conducted by Goharkhah et al. [18] in order to

experimentally investigate the conduction heat transfer rate

of a ferrofluid subjected to dynamic conditions. The

experiment involves the analysis of heat transfer rate

strength by means of conduction of the nanofluid known as

Fe3O4/water ferrofluid moving through a pipe subjected to

a uniform heat flux with several Reynolds number from

400 to 800 and a volume fraction from 1% to 2%. The

results demonstrated that the heat transfer rate by means of

conduction increased when the concentration of the

nanofluids were also increased. Moreover, it was revealed

that a heat flux of zero enhances the conduction heat

transfer rate with an increase in the Reynolds variety, while

contrary behaviour was observed when the system was

subjected to a heat flux. In comparison to the thermal



conduction in water, the higher heat transfer rate by means

of conduction increased to 32.3% for a ferrofluid with 2

Vol% of concentration at a variety Reynolds Number of

400 and under a magnetic flux with a magnitude of 800 G.

In this assignment, different heat fluxes were applied on the

pipe to observe the effects of heat transfer enhancement by

using different magnetic fields with magnetic oxide Fe3O4.

2. Nanofluid Preparation and Properties

Twenty minutes before each experiment is executed, the nanoparticles and purified water were incorporated directly

with a mixer at (2400 rpm), with the volume fraction used in the experiments being (π = 0, 0.3, 0.6 and 0.9 percent by

volume). The test rig was performed by using a water volume of 5 L. Equation (1) specifies the percentage relation for the

determination of the volume concentration:

𝜑 =𝑣𝑜𝑙𝑢𝑚𝑒 𝑜𝑓 𝑛𝑎𝑛𝑜𝑝𝑎𝑟𝑡𝑖𝑐𝑙𝑒

𝑣𝑜𝑙𝑢𝑚𝑒 𝑜𝑓 𝑛𝑎𝑛𝑜𝑝𝑎𝑟𝑡𝑖𝑐𝑙𝑒 + 𝑣𝑜𝑙𝑢𝑚𝑒 𝑜𝑓 𝑤𝑎𝑡𝑒𝑟 × 100 (1)

𝜑 =(𝑚 𝜌⁄ )𝑛𝑎𝑛𝑜𝑝𝑎𝑟𝑡𝑖𝑐𝑙𝑒

(𝑚 𝜌⁄ )𝑛𝑎𝑛𝑜𝑝𝑎𝑟𝑡𝑖𝑐𝑙𝑒 + (𝑚

𝜌⁄ )𝑤𝑎𝑡𝑒𝑟× 100 (2)

The properties of nanoparticle and base fluid (viscosity, density and specific heat) are listed in Table (1) below.

Table I

material properties. [18].

Substance

Averagedi

ameter

(nm)

Density

(Kg/m3)

Thermal

conductivity

(W/m.K)

Specific

heat

(J/kg.K)

viscosity

(pa.s)

Fe3O4 80 5180 80.4 670 -

Water - 997 0.607 4180 0.000891

The measurement of the density as well as the specific heat of a nanofluid can be evaluated by applying the mixture laws of

convection shown in equations (3) and (4) [19]:

𝐶𝑛𝑓 = (1 − 𝜑)𝐶𝑏𝑓 + 𝜑𝐶𝑛𝑝 (3)

𝜌𝑛𝑓 = (1 − 𝜑)𝜌𝑏𝑓 + 𝜑𝜌𝑛𝑝 (4)

Brickman [20] explained viscosity correlation as it applies to concentrated particle suspension:

𝜇𝑛𝑓 = (𝜇𝑏𝑓

(1 + 𝜑)2.5) (5)

In order to determine the thermal conductivity, the Wasp model is taken into account [21]:

𝐾𝑚 = 𝐾𝑓 [2 + 𝐾𝑝𝑓 + 2∅(𝐾𝑝𝑓 − 1)

2 + 𝐾𝑝𝑓 − ∅(𝐾𝑝𝑓 − 1)] (6)

Where:

𝐾𝑝𝑓 =𝐾𝑝𝐾𝑓

(7)

3. Experimental Setup

The experiment was executed with a tube of copper of

(0.014, 0.0158 m) inner and outer diameters and (1.5 m)

test section length, helical heat exchanger nanofluid tank,

pumps, flow meters, thermos recorder, variac, electric

board, magnets and fittings, as shown in Figure (1). The

copper tube is heated uniformly by wrapping it with a

Nichrome heater of 2000 watt. To achieve a uniformed heat



flux, the outer layer of the pipe was subjected to an

electrical current using a coil. The electrical fibreglass

insulator winds through the tube. To insulate the electrical

heater, drilled ceramic bead elements were placed around

the wire heater and then the wire heater is wound around

the tube. Aluminium foil and sectional pipe insulation glass

wool form were used to reduce heat despite of this.

Temperature was gauged using eight thermocouples (k–

type), which allowed determining the temperature in

different test rig points. On the contrary, in order to

measure temperature along the outer layer of the tube

heated section, six thermocouples were used. The

thermocouples were located along the test section with a

distance of 22 cm between them. Two immersed

thermocouples were used to measure the fluid temperatures

at the inlet and outlet of the pipe. A stainless steel tank of

(24 L) capacity was used to supply the pump with the

required amount of working fluid. The spiral heat

exchanger consisted of a copper tube coil with a diameter

of 24 L. A coil was then placed in a stainless steel tank of

125 L capacity filled with re-circulating water. To measure

the pressure drop along the test section, a manometer U-

Tube type with CCL4, Carbon Tetrachloride, was used.

Magnets were used in this experimental work as illustrated

in Table (2). It was determined by the researchers using a

gauss meter [17].

Table II

strength of the magnet.

Magnet type Number of

magnet used

Strength at center of

pipe (20 mm). (Gauss)

Strength of magnet at

surface (Gauss)

Ferrite 5 600 1000

http://www.zhaobao-magnet.com/product/77.shtml?gclid=*



Fig. 1. Diagram of experimental apparatus.

The experiment was conducted with distilled water, nanofluid: Iron Oxide (Fe3O4- distilled water) with the volume

fraction (φ = 0. 3, 0.6 and 0.9 % by volume), magnetic field with each concentration with the intensity of (0.1Tesla),

different constant heat fluxes (12.7, 15.9, 19.8 kw/m2), and different inlet temperatures (23, 45) o C. All of these tests were

carried out under a turbulent flow at the entrance, with magnitudes of Reynolds Number from (3930 to 7860), heat fluxes

of (12.7 to 19.8 kW/m2) and flow rates of (2, 3, 3.5 and 4 L/min).

4. Data Reduction

Equation (8) specifies the heat transfer rate produced by an electrical current, which is the heat flux applied to the outer

layer of the tube:

𝑃 = 𝑉 × 𝐼 (8)

The heat transfer rate exchanged to the nanofluid from the heating wire can be determined by applying equation (9):

𝑄𝑛𝑓 = �̇� × 𝐶𝑛𝑓 × (𝑇𝑜 − 𝑇𝑖) (9)



The balance between the heat input P and the nanofluid𝑄𝑛𝑓 can be computed by using equation (10), where common

values are under 10%:

𝜂 =𝑃 − 𝑄𝑛𝑓

𝑃< 10 % (10)

The heat flux is given by:

�̇� =𝑄𝑛𝑓𝐴𝑠

=𝑄𝑛𝑓

𝜋𝐷𝑜𝐿 (11)

The following steps indicate the processes to determine the local heat transfer coefficient:

1. The following values are known: {�̇�, Tso(x)}.

2. The temperature on the outer surface of the tube, Tsi(x), can be determined from the following equation [21]:

�̇� =𝑄𝑛𝑓𝐴𝑠

=2𝜋𝑘∆𝑥[𝑇𝑠𝑜(𝑥) − 𝑇𝑠𝑖(𝑥)]

𝜋𝐷∆𝑥 × ln (𝑟𝑜

𝑟𝑖)

=2𝑘[𝑇𝑠𝑜(𝑥) − 𝑇𝑠𝑖(𝑥)]

𝐷 × ln (𝑟𝑜

𝑟𝑖)

(12)

3. The mean temperature of the bulk fluid, Tm(x) at section (x):

𝑑𝑞 = 𝑞"𝑝𝑑𝑥 = �̇� 𝐶𝑛𝑓 𝑑𝑇𝑚 (13)

Where 𝑝 = 𝜋𝐷𝑖 is the

𝑑𝑇𝑚 =𝑞"𝜋𝐷𝑖�̇�𝐶𝑛𝑓

𝑑𝑥 (14)

The changes in the mean of the bulk fluid temperature in the function of position x is computed by an integration of

equation (14). The limits of the integration are from 0 to x, and this yields to:

𝑇𝑚(𝑥) = 𝑇𝑖 +(𝑇𝑜 − 𝑇𝑖)

𝐿 𝑥 (15)

Hence, the local heat transfer coefficient is computed from equation (16):

ℎ(𝑥) =�̇�

𝑇𝑠𝑖(𝑥) − 𝑇𝑚(𝑥) (16)

The local Nusselt Number is given by [2]:

𝑁𝑢(𝑥) =ℎ𝑥𝐷

𝑘𝑛𝑓 (17)

Equation (18) can be used to determine the mean Nusselt Number for the thermal developing zone:

𝑁𝑢 =1

𝐿∫ 𝑁𝑢 (𝑥)

𝐿

0

𝑑𝑥 (18)

Based on the empirical correlation of Gnielinski’s [22] as shown in equation (19), the experimental magnitudes of the

Nusselt Number were compared [23].

𝑁𝑢 =(

𝑓

2) (𝑅𝑒 − 1000)𝑃𝑟

1 + 12.7 (𝑓

2)

0.5(𝑃𝑟

3

2 − 1) (19)

And represented in Figure (2)

Where



𝑓 = (1.58𝑙𝑛𝑅𝑒 − 3.82)−2 𝑓𝑜𝑟 2300 < 𝑅𝑒 < 5 × 106,0.5 < 𝑃𝑟 < 2000

Experimental Friction Factor

The Darcy Friction Factor can be determined by using equation (20), which is based on the pressure drop [24].

𝑓 =2 × ∆𝑝 × 𝐷

𝐿 × 𝜌 × 𝑢2 (20)

Where:

∆𝑃 = 𝛾𝑛𝑓 (𝜌𝐶𝐶𝑙4𝜌𝑛𝑓

− 1) × 𝐻 (21)

This is the pressure drop across the test section. The comparison of the present work with Gnielinski’s and Blasius

equation (𝑓 = 0.316𝑅𝑒−0.25) for distilled water, to validate the rig performance, show positive concordance.

5. Results and Discussion

The Nusselt Number variation with the Reynolds Number at different uniform heat fluxes and (a, b, c), using a volume

concentration of 0.3%, 0.6% and 0.9%, respectively, and shown in Figures (2) without magnetic and Figures (3) with

magnetic field with the strength of (0.1Tesla), the increase in heat flux, volume concentration, Reynolds number, and

magnetic field due to the increase in Nusselt number and enhanced heat transfer.

(a)

(a)



(b)

(b)

(c)

(c)

Fig. 2. The impact of Reynolds number on average Nusselt number

with different constant heat flux and without magnets. Fig. 3. The impact of Reynolds number on average Nusselt number

with different constant heat flux and with magnets.

The average Nusselt number increases with a surge in the concentration of ferrofluid and magnetic strength for each

concentration, and decreases with an increase in the number of Reynolds since the effective thermal conductivity of

nanofluid decreases with an increase in the volume fraction of nanoparticles as shown in Figures (4) and (5). The effect of heat flux (nanoparticles migration from the surface with heat flux increase) with the magnetic field is due to the fact that

the viscous sub-layer is very small (at the entrance region), and the particles accumulate on the surface increasing in

fraction, both of these reasons due to the increase in heat transfer [16].



(a)

(a)

(b)

(b)

(c)

(c)

Fig. 4. The impact of Reynolds number on Nusselt number with

different constant heat flux, volume concentration and without

magnets.

Fig. 5. The impact of Reynolds number on Nusselt number with

different constant heat flux, volume concentration and with

magnets.



The effect of inlet temperature on heat transfer is discerned when the temperature increases, the heat transfer decreases as

shown in Figure (6) and the friction factor decreases when temperature increases as shown in Figure (7). The pressure drop

is increased with the increase of Reynolds number, ferrofluid concentration and the magnetic field intensity. It was

acknowledged that the friction factor heightens in magnitude when the volume concentration and the intensity of the magnet

increased, and the friction factor diminishes in magnitude when the Reynolds number decreased, as illustrated in Figure

(8).

Fig. 6. the impact of Reynold on Nusselt number with different

inlet temperature and Volume concentration =0.9% and constant

heat flux =19.8Kw.m2.

Fig. 7. the impact of Reynold on friction factor with different inlet

temperature and Volume concentration =0.9% and constant heat

flux =19.8Kw.m2.

Fig. 8. The impact of Reynolds number on friction factor without

magnets at different constant heat flux. Fig. 9. The impact of Reynolds number on friction factor with

magnets at different constant heat flux.

The increase in the Nusselt Number of the magnetic nanofluid with respect to the water reaching maximum value is

presented in Table (3). Table III

The maximum value of enhancement.

Volume concentration

%

Enhancement %with

B=0.0Tesla

Enhancement %with

B=0.1Tesla

Heat flux Kw/m2 Heat flux Kw/m2

12.7 15.9 19.8 12.7 15.9 19.8

0.3 11.6 6.4 6.9 13 10 8.2

0.6 14.98 9.5 8.6 16.7 11.5 9.9

0.9 18.3 13.1 12.7 20.1 14.1 13.9



6. Conclusions

This article discussed the impacts of heat flux and magnetic

nanofluid with a magnetic field on heat transfer in a

horizontal pipe, thus the following points were derived.

The nanofluid employed, Fe3O4– distilled water with a

particle size of 80 nm resulted in an enhancement in the

heat transfer as well as in the Nusselt Number. The

nanoparticles displayed characteristics of heat transfer

greater than the base fluid (distilled water). The average

enhancement is (20.1 percent) for the magnetic nanofluid

at a concentration of 0.9 percent and a magnetic field of 0.1

Tesla with the heat flux of 12.7 kW/m2 while the minimum

enhancement is (1.5 percent) for the magnetic nanofluid at

a concentration of 0.3 percent with the heat flux of 19.8

kW/m2 without the magnetic field. Applying a magnetic

field often promotes heat transfer enhancement, as the

magnetic field produces higher numbers of Nusselt as

compared to water-distilled and magnetic nanofluid.

Conclusively, with higher inlet temperature, the heat

transfer decreases.

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