NUMERICAL INVESTIGATION OF AUTOMOTIVE RADIATOR LOUVERED FIN COMPACT HEAT EXCHANGER

International Journal of Mechanical Engineering and Technology (IJMET), ISSN 0976 – 6340(Print),
ISSN 0976 – 6359(Online), Volume 5, Issue 7, July (2014), pp. 01-14 © IAEME
1
NUMERICAL INVESTIGATION OFAUTOMOTIVE RADIATOR
LOUVERED FIN COMPACT HEAT EXCHANGER
Manjunath S N1
, S.S.Mahesh Reddy2
, Saravana Kumar3
1
(M.Tech Student, Thermal Power Engineering,
East Point College of Engineering and Technology Bangalore)
2
(Assistant Professor, East Point College of Engineering and Technology, Bangalore)
3
(Finite Flow Technology Solutions Pvt Ltd)
ABSTRACT
In compact heat exchangers, thermal resistance is generally dominant on the air-side and may
account for 80% or more of the total thermal resistance. The air-side heat transfer surface area is 8 to
10 times larger than the water-side. Any improvement in the heat transfer on air-side therefore
improves the overall performance of the heat exchanger. Due to the high thermal resistance on the
air-side, the optimization of such fins is essential to increase the performance of the heat exchangers
which results in thermal systems enhancement. This helps to reduce CO2 emissions through a
reduction of mass and fuel consumption.
Optimization of louvered fin geometry in such heat exchangers is essential to increase the
heat transfer performance and reduce weight, packaging, and cost requirements. In this study deals
with Computational Fluid Dynamics (CFD) studies of the interactions between the air flow and
louvered fins which equipped the automotive heat exchangers is carried out. 3D numerical
simulation results is obtained by using the ANSYS Fluent 14.0 code and compared with
experimental data. Finally the effect of louver angle and louver pitch geometrical parameters, on
overall thermal hydraulic performances of louvered fins is studied.
Keywords: CFD, Heat Transfer, Louver Fin, Radiator.
I. INTRODUCTION
A heat exchanger is a complex device that provides the transfer of thermal energy between
two or more fluids, which are at different temperatures and are in thermal contact with each other.
INTERNATIONAL JOURNAL OF MECHANICAL ENGINEERING
AND TECHNOLOGY (IJMET)
ISSN 0976 – 6340 (Print)
ISSN 0976 – 6359 (Online)
Volume 5, Issue 7, July (2014), pp. 01-14
© IAEME: www.iaeme.com/IJMET.asp
Journal Impact Factor (2014): 7.5377 (Calculated by GISI)
www.jifactor.com
IJMET
© I A E M E

2
Heat exchangers are used either individually or as components of a large thermal system, in a wide
variety of commercial, industrial and household applications, e.g. power generation, refrigeration,
ventilating and air-conditioning systems, process, manufacturing, aerospace industries, electronic
chip cooling as well as in environmental engineering. The improvements in the performance of the
heat exchangers have attracted many researchers for a long time as they are of great technical,
economical, and not the least, ecological importance. Performance improvement becomes essential
particularly in heat exchangers with gases because the thermal resistance of gases can be 10 to 50
times as large as that of liquids, which requires large heat transfer surface area per unit volume on
gas side.
The traditional methods of reducing the air-side thermal resistance are by increasing the
surface area of the heat exchanger, or by reducing the thermal boundary layer thickness on the
surface of the heat exchanger. Increasing the surface area is effective but it results in the increase in
material cost and increase in mass of the heat exchanger. One of the methods to reduce boundary
layer thickness is by the generation of passive vortices. In this technique the flow field is altered by
an obstacle to generate a vortex oriented in the direction of the flow. The resulting change in the flow
due to an obstacle alters the local thermal boundary layer. The net effect of this manipulation is an
average increase in the heat transfer for the affected area.
Fig.1: 1. Water filling hole, 2. Cold water to engine, 3. Recycling water to engine,
4. Elliptical tube, 5. Fin, 6. Bottom header plate, 7. Bottom header, 8. Hot water from radiator,
9. Drain cock, 10. Core bracket
Borrajo-Pelaez et al. [1] carried out 3D numerical simulations to compare both an air side and
air/water side model of a plain fin and tube heat exchanger. In their experiment, the influence of the
Reynolds number, fin pitch, tube diameter, fin length and fin thickness were studied. Haci Mehmet
Sahin et al. [2] studied the heat transfer and pressure drop characteristics of seven different fin angles

3
with plain fin and tube heat exchangers. This problem was analyzed using Fluent software, and it
was found that a fin with 30º inclination is the optimum one, which gives the maximum heat transfer
enhancement.
Mao-Yu Wen et al. [3] have investigated the heat transfer performance of a fin and tube heat
exchanger with three different fin configurations such as plate fin, wavy fin and compounded fin.
This experiment strongly suggested the use of the compound fin configuration for the heat
exchanger. Wei-Mon Yan and Pay-Jen Sheen [4] have carried out an experiment to investigate the
heat transfer and pressure drop characteristics of fin and tube heat exchangers with plate, wavy and
louvered fin surfaces. From this experiment, it is found that at the same Reynolds number, louvered
fin geometry shows larger values of f and j factors, compared with the plate fin surfaces.
Igor Wolf et al. [5] studied the heat transfer performance of a wavy fin and tube heat
exchanger by numerical and experimental methods. They presented some results of a three
dimensional numerical analysis of heat transfer on the air side of a wavy fin and tube heat exchanger.
The three dimensional local flow and thermal fields are well characterized by the numerical analysis.
The developed and presented model demonstrated good heat transfer prediction. It could provide
guidelines for the design optimization of a fin and tube heat exchanger. In this study, three rows of
circular tubes in a staggered arrangement were taken as a domain. The air-side heat transfer and
pressure drop characteristics were successfully modeled using the CFD software Fluent. The
numerical results were validated with the experimental results and the deviation was within 8%.
Tang et al. [6] carried out an experimental and numerical investigation on the air-side
performance of fin and tube heat exchangers with various fin patterns, such as crimped spiral fin,
plain fin, slit fin, fin with delta wing longitudinal vortex generator (VG), and mixed fin with front
6-row vortex generator fin and rear 6-row slit fin. It was found that the heat exchanger with the
crimped spiral fin has better performance than the other four configurations. Also it is found that the
Slit fin offers the best heat transfer performance at a higher Reynolds number. Chi-Chuan Wang et
al. [7] provided flow visualization and pressure drop results for plain fin and tube heat exchangers,
with and without the presence of vortex generators. It was found that the pressure drop of the delta
winglet is lower than that of the annular winglet. Fiebig et al. [8] investigated the local heat transfer
and flow losses in plate fin and tube heat exchangers with vortex generators, to compare the
performance of round and flat tubes. It was found that the heat exchanger with flat tubes and vortex
generators gives nearly twice as much heat transfer with a penalty of 50% pressure loss, when
compared to a heat exchanger with round tubes. Jin-Sheng Leu et al. [9] had performed a numerical
and experimental analysis to study the thermo-hydraulic performance of an inclined block shape
vortex generator embedded plate fin and tube heat exchangers. In this analysis, the effects of
different span angles (30º, 45º and 60º) were investigated for Reynolds numbers ranging from 400 to
3000. It was found that a 30º span angle provides the best heat transfer augmentation and also offers
25% lesser fin surface area.
Jin-Sheng Leu et al. [10] conducted a numerical simulation for louvered fin and tube heat
exchangers having circular and oval tube configurations. The effects of the geometrical parameters
such as louver angle, louver pitches and louver length were discussed. Joen et al. [11] worked on the
interaction between the flow behavior (flow deflection and transition to unsteady flow) and the
thermo-hydraulic performance of an inclined louvered fin design. In this experiment, the impact of
fin pitch, fin angle and Reynolds number were discussed in detail. Zhang and Tafti [12] investigated
the effect of the Reynolds number, fin pitch, louver thickness and louver angle on flow efficiency in
multi-louvered fins and found that the flow efficiency (flow efficiency (η) = Mean flow angle
(αmean) / Louver angle (θ)) is strongly dependent on geometrical parameters, especially at a low
Reynolds number. The Flow efficiency increases with the Reynolds number and louver angle, while
decreasing with the fin pitch and thickness ratio. Wei Li and Xialing Wang [13] conducted an

4
experimental study on the air side heat transfer and pressure drop characteristics of brazed aluminum
heat exchangers, with multi-region louver fins and flat tubes. They found that the heat transfer
coefficients and pressure drop tend to decrease with increasing Reynolds numbers, and increase with
the number of louvers.
Wang et al. [14] presented generalized heat transfer and friction correlations for louver fin
geometry having a round tube configuration. They considered different geometrical parameters, such
as louver pitch, louver height, longitudinal tube pitch, transverse tube pitch, tube diameter and fin
pitch for the generation of correlations. Yu-Juei Chang and Chi-Chuan Wang [16] developed a
similar generalized heat transfer correlation for louver fin geometry, using a large data bank. In this
study, different geometrical parameters such as louver angle, tube width, louver length, louver pitch,
fin length and fin pitch were used. For corrugated louver fin geometry, it is shown that 89.3% of the
corrugated louver fin data are correlated within ±15% with a mean deviation of 7.55%. The inclusion
of the plate and tube louver fin data in the heat transfer correlation results in a mean deviation of
8.21%.
It is found from the literature that most of the research works carried out in the field of
compact heat exchangers are presenting j and f factors corresponding to the air side only. However,
the heat transfer performance of the compact heat exchanger under varying conditions of the tube
side fluid is not reported. In the present paper, in addition to the CFD studies carried out for the
louvered fin and elliptical tube compact heat exchanger which is validated with the experimental
results, the heat transferred to the air under different mass flow rate of the water is also reported,
which provides lot of significance.
II. MATHEMATICAL MODELS OF FLUENT
All the fluids investigated in this research are Newtonian. This means that there exists a linear
relationship between the shear stress, σij, and the rate of shear (the velocity gradient). In CFX, this is
expressed as follows:
ߪ௜௝ ൌ െ‫ߜ݌‬௜௝ ൅ ߤ ቆ
߲‫ݑ‬௜
߲‫ݔ‬௝
൅
߲‫ݑ‬௝
߲‫ݔ‬௜
ቇ … … … … … … . .1
In FLUENT, these laws are expressed in the following form:
Law of Conservation of Mass: Fluid mass is always conserved.
ࣔ࣋
࢚ࣔ
൅
ࣔ
ࣔ࢞࢐
൫࢛࣋࢐൯ ൌ ૙ … … … … … . . . ૛
Newton’s 2nd
Law: The sum of the forces on a fluid particle is equal to the rate of change of
momentum.
ࣔ
࢚ࣔ
ሺ࢛࣋࢏ሻ ൅
ࣔ
ࣔ࢞࢐
൫࢛࣋࢏࢛࢐൯ ൌ
ࣔ
ࣔ࢞࢐
ቈെ࢖ࢾ࢏࢐ ൅ ቆ
࢛ࣔ࢏
ࣔ࢞࢐
൅
࢛ࣔ࢐
ࣔ࢞࢏
ቇ቉ ൅ ࡮࢏ … … … … … . . . ૜
First Law of Thermodynamics: The rate of head added to a system plus the rate of work done on a
fluid particle equals the total rate of change in energy.

5
ࣔ
࢚ࣔ
ሺ࣋ࡴࢋሻ ൅
ࣔ
ࣔ࢞࢐
൫࢛࣋࢐ࡴࢋ൯ െ
ࣔ
ࣔ࢞࢐
ቆࣅ
ࣔࢀ
ࣔ࢞࢐
ቇ ൌ
ࣔ࣋
࢚ࣔ
… … … … … . . . ૝
The fluid behaviour can be characterised in terms of the fluid properties velocity vector u
(with components u, v, and w in the x, y, and z directions), pressure p, density ρ, viscosity µ, thermal
conductivity λ, and temperature T. The changes in these fluid properties can occur over space and
time. H is the total enthalpy, given in terms of the static (thermodynamic) enthalpy, h:
III. GEOMETRIC MODEL
Fig.2 shows 3-D CFD model computational domain, which is a complete louver fin
geometric configuration. The tube and fin with the unlouvered zone have been modeled. To reduce
the computational period, only half of the fin and half of the tube are represented. The symmetry
conditions are assumed on both sides of the computational domain and the periodic boundary
conditions are applied to at the top and bottom of the computational domain as depicted of fig.4.1 In
order to avoid the effect of air circumfluence, computational domain has been extended some
distance downward and upward along the flow direction.
Fig.2: Dimension details of louver plate-fin geometry
The objective of this project is to introduce a method associated with simulation technique as
an alternative for cost reduction of new product design and development cycle. The numerical
technique called finite volume method is used in this study to investigate the effects of geometric
parameters on heat transfer and fiction factor of louvered fin radiator.
The geometrical parameter for a plate-fin in this study is shown in Figure 2. All samples in
this analysis have the tube width 16 mm, depth 2 mm and the copper louver fin thickness is 0.05 mm.

6
The length of the fins in the airflow direction is 41.6 mm associating with double row tubes.
Simulations are performed for different geometries with various fin pitch (Fp), louver pitch (Lp),
tube pitch (Tp) and louver angle (α). The values of these parameters are listed in Table 1. The scope
of this paper is limited to 3 from 15 configurations of T.A. Cowell and A. Achaichia [15].
Fig.3: Computational domain
The air flow over the louvers is assumed to be laminar and steady. The model is governed by
the conservation equations of mass, momentum and energy. To form a closed set of equations, ideal

7
gas state equation can be used to relate pressure, density and temperature of air. The viscosity and
thermal conductivity of the air are a function only of the temperature, the change of which is small in
flow over the fin and can be assumed constant and evaluated at the mean air temperature of inlet and
outlet. The viscosity is obtained from Sutherland’s law and the thermal conductivity can be fitted as
linear form of mean temperature.
The boundary conditions for the velocity and thermal fields need to be specified on the
interface of the fin surface and fluid due to take into account conjugate heat transfer. At the upstream
boundary, the flow direction velocity and temperature are assumed to be constant, with the other two
direction velocities being set to zero and flow direction velocity being set to the inlet air velocity and
the temperature being set to the ambient atmospheric temperature. The downstream boundary is
assumed to be pressure-outlet condition. The symmetry conditions are assumed on both sides of the
computational domain and the periodic boundary condition are applied to at the top and bottom of
the computational domain. All solid surfaces including the louver surface and the tube surface are
assumed as no-slip boundary conditions and constant wall temperature are specified.
IV. CFD MESHING
In this model tetrahedral with prism boundary layer grid in the flow region. Especially
complex shapes are difficult to model with a structured grid. Therefore an unstructured grid with
triangular cells is used at the r outer region.
Fig.4: CFD Meshing of Louver Fin
The three-dimensional computational domain and boundary condition is shown in Figure 4.
3. One-half of the tube pitch is considered with symmetry plane at one side and constant wall
temperature at the other. The top and bottom surfaces of the domain are defined as periodic

8
boundaries. Previous literature suggests that the three-dimensional model is to be constructed with
the smallest fluid cell size next to the wall being smaller than or equal to the fin’s thickness. For
simplicity of the computational mesh and modeling reason of heat transfer between solid and fluid
interface, however, its thickness next to fin is assigned to be equal to the fin height with symmetrical
geometry at upper and lower surface of the fin. The numerical simulations are performed for
different Reynolds number with range of 100 to 1000. From Experiment of T.A cowel and
A.Achaichia the temperature variation of the tube is small, this can be assumed constant at 358K.
The inlet air temperature of the louver fin is at 288K.
V. RESULTS AND DISCUSSIONS
A. Smooth tube Results
Fig.5: Pressure contours Ɵ=20o and Re=100
Fig.5 shows the Pressure contours at Re=100. In these contours shows pressure drop 0.8Pa

9
Fig.6: Temperature contours ƟƟƟƟ=20o
and Re=100
Figure 6 shows the contours of temperature on the radiator water tubes, fins and louvers. The
tube walls are at a higher temperature, as hot water flows through them. The fins transfer the heat
from the hot water tube to the air through the louvers. Accordingly, the temperature variation is seen.
Similar to the increase in temperature of air seen along the stream-wise direction, the fin and louver

10
temperature also increases along this direction. The contour of temperature on the same plane is
plotted in Fig. 7. Heat is dissipated from the tube wall through the fin by convection heat transfer in a
conjugate fashion. Along the stream-wise direction, a gradual increase in temperatures is seen which
ensures the heating of air, while cooling the water in the tubes. At the outlet region, a large increase
in the air temperature is seen near the fin surface, which is due to the absence of louvers at this
region.
Fig.7: Velocity contours ƟƟƟƟ=20o
and Re=100

11
Fig.8: Stanton Number Vs Reynolds Number for Fin angle 25.5 Degree
Figures 8. show the result from this study compared with empirical results of Stanton number
as functions of Reynolds number. The values from the experiment and from the formulation of A.
Achaichia and T.A. Cowell [15] and those computed from Stanton number. The predictive quality of
the selected model is good in general with the minimum and maximum deviation in heat transfer of
4% and 12% respectively
Fig.9: Stanton Number Vs Reynolds Number for different Fin angle
0.01
0.1
1
0 200 400 600 800 1000 1200
StantonNumber
Reynolds Number
CFD-Angle25.5 Deg
Experimental
0.01
0.1
1
0 200 400 600 800 1000 1200
StantonNumber
Reynolds Number
Angle20 Deg
Angle25.5 Deg
Angle30 Deg
Angle35 Deg

12
Fig.10: HTC Vs Reynolds Number for different Fin angle
Fig.11: Pressure Drop Vs Reynolds Number for different Fin angle
The heat transfer coefficients and the values of pressure drop are given for different values of
Reynolds numbers in above Figure. The effects of angle can be observed. Heat transfer coefficients
proportionally relate with Reynolds number. Moreover, the heat transfer coefficients and pressure
drop increase with increase in fin angle. The CFD results show that the differential pressure is almost
a quadratic function of the velocity and that flows passing through the louvers also have a resistance
characte-ristic of ordinary flows. When the angle becomes small, that is, when the angle to flows
flowing through the louvers be-comes small, the pressure differences tend to decrease. The louvers
are installed to eliminate projected gaps in front and the area occupied by the louvers increases in the
0
50
100
150
200
250
0 200 400 600 800 1000 1200
HTCW/m2
K
Reynolds Number
Angle20 Deg
Angle25.5 Deg
Angle30 Deg
Angle35 Deg
0
5
10
15
20
25
30
35
40
45
0 200 400 600 800 1000 1200
PressureDropPa
Reynolds Number
Angle20 Deg
Angle25.5 Deg
Angle30 Deg
Angle35 Deg

13
cross section when the angle becomes small, while the flow path becomes narrow. Notwithstanding
this, the pressure diffe-rential becomes significantly small. Figure 11 compares the ratios of pressure
differences of the louvers based on a pressure difference at 35° and Re=1000m/s as a reference. The
pressure difference lowers to 45% at 20°.
VI. CONCLUSION
The effects of geometric parameters have been investigated by considering heat transfer and
friction loss of louver plate fins in terms of Stanton number and friction factor. The study is
performed within the range of Reynolds number from 100 to 1000. Comparison study with empirical
equation of A. Achaichia and T.A. Cowell [15] is made to evaluate the predictive quality of the
technique within the specified range of operating conditions and geometries. Good agreement is
observed as far as Stanton number with the deviation in heat transfer of 1% up to 12%.
• It is expected that the flow efficiency increases with Reynolds number and louver angle, but
it decreases with the fin pitch and thickness ratio
• Pressure loss characteristic varies significantly relative to the louver angle. In this research,
pressure losses could be kept to less than half by varying the louver angle 20°.
• CFD allows reliable forecasting of flow behaviors in shapes of louvers as in this research and
its availability as a design tool has been verified.
• Adding more fin surface area will also result in a range increase in pressure drop and material
loss.
• A numerical simulation using a CFD code is used to determine which parameters have the
strongest impact on the heat transfer coefficent and friction factor.
REFERENCES
[1] Pelaez, R.B., Ortega, J.C., Cejudo-Lopez, J.M., A three-dimensional numerical study and
comparison between the air side model and the air/water side model of a plain fin and tube
heat exchanger, Applied Thermal Engineering, 30 (2010), pp.1608-1615.
[2] Sahin, H.M., Dal, A.R., Baysal, E., 3-D Numerical study on correlation between variable
inclined fin angles and thermal behavior in plate fin-tube heat exchanger, Applied Thermal
Engineering, 27 (2007), pp.1806-1816.
[3] Wen, M.Y. Ho, C.Y., Heat transfer enhancement in fin and tube heat exchanger with
improved fin design, Applied Thermal Engineering, 29(2009), pp.1050-1057.
[4] Yan, W.M., Sheen, P.J., Heat transfer and friction characteristics of fin and tube heat
exchangers, International Journal of Heat and Mass Transfer, 43 (2000), pp.1651-1659.
[5] Wolf, I., Frankovic, B., Vilicic, I., A numerical and experimental analysis of neat transfer in a
wavy fin and tube heat exchanger, Energy and the Environment (2006) pp.91-101.
[6] Tang, L.H., Zeng, M., Wang, Q.W., Experimental and numerical investigation on air side
performance of fin and tube heat exchangers with various fin patterns, Experimental Thermal
and Fluid science, 33(2009), pp.818-827.
[7] Wang, C.C., Lo, J, Lin, Y.T. Wei, C.S., Flow visualization of annular and delta winlet vortex
generators in fin and tube heat exchanger application, International Journal of Heat and
Mass Transfer, 45, (2002), pp.3803-3815.
[8] Fiebig, M., Valencia, A., Mitra, N.K.., Local heat transfer and flow losses in fin and tube heat
exchangers with vortex generators: A comparison of round and flat tubes, Experimental
Thermal and Fluid Science, 8(1994), pp.35-45.

14
[9] Leu, J.S., Wu, Y.H., Jang, J.Y., Heat transfer and fluid flow analysis in plate-fin and tube
heat exchangers with a pair of block shape vortex generators, International Journal of Heat
and Mass Transfer, 47 (2004), pp. 4327-4338.
[10] Leu, J.S., Liu, M.S., A numerical investigation of louvered fin and tube heat exchangers
having circular and oval tube configurations, International Journal of Heat and Mass
Transfer, 44 (2001), pp. 4235-4243.
[11] Joen, C.T et al., Interaction between mean flow and thermo-hydraulic behaviour in inclined
louver fins, International Journal of Heat and Mass Transfer, 54, (2011), pp.826-837.
[12] Zhang, X., Tafti, D.K., Flow efficiency in multi-louvered fins, International Journal of Heat
and Mass Transfer, 46, (2003), pp.1737-1750.
[13] Li, W., Wang, X., Heat transfer and pressure drop correlations for compact heat exchangers
with multi-region louver fins, International Journal of Heat and Mass Transfer, 53 (2010),
pp.2955-2962.
[14] Wang, C.C., Lee, C.J., Chang, C.T., Lin, S.P., Heat transfer and friction correlation for
compact louvered fin and tube heat exchangers, International Journal of Heat and Mass
Transfer, 42 (1999), pp.1945-1956.
[15] T.A. Cowell and A. Achaichia, “Heat Transfer and Pressure Drop Characteristics of Flat
Tube and Louver Plate Fin Surfaces”, Experimental Thermal and Fluid Science, No.1, 1988,
p147-157.
[16] Chang, Y.J., Wang, C.C., A generalized heat transfer coefficient for louver fin geometry,
International Journal of Heat and Mass Transfer, 40, (1997), pp.533-544.
[17] Omar Mohammed Ismael, Dr. Ajeet Kumar Rai, Hasanfalah Mahdi and Vivek Sachan, “An
Experimental Study of Heat Transfer in a Plate Heat Exchanger”, International Journal of
Advanced Research in Engineering & Technology (IJARET), Volume 5, Issue 4, 2014,
pp. 31 - 37, ISSN Print: 0976-6480, ISSN Online: 0976-6499.
[18] S. Bhanuteja and D.Azad, “Thermal Performance and Flow Analysis of Nanofluids in a Shell
and Tube Heat Exchanger”, International Journal of Mechanical Engineering & Technology
(IJMET), Volume 4, Issue 5, 2013, pp. 164 - 172, ISSN Print: 0976 – 6340, ISSN Online:
0976 – 6359.
[19] Ajeet Kumar Rai and Mustafa S Mahdi, “A Practical Approach to Design and Optimization
of Single Phase Liquid to Liquid Shell and Tube Heat Exchanger”, International Journal of
Mechanical Engineering & Technology (IJMET), Volume 3, Issue 3, 2012, pp. 378 - 386,
ISSN Print: 0976 – 6340, ISSN Online: 0976 – 6359.
[20] Sunil Jamra, Pravin Kumar Singh and Pankaj Dubey, “Experimental Analysis of Heat
Transfer Enhancement in Circular Double Tube Heat Exchanger using Inserts”, International
Journal of Mechanical Engineering & Technology (IJMET), Volume 3, Issue 3, 2012,
pp. 306 - 314, ISSN Print: 0976 – 6340, ISSN Online: 0976 – 6359.

NUMERICAL INVESTIGATION OF AUTOMOTIVE RADIATOR LOUVERED FIN COMPACT HEAT EXCHANGER

Empfohlen

Empfohlen

Weitere ähnliche Inhalte

Was ist angesagt?

Was ist angesagt? (15)

Andere mochten auch

Andere mochten auch (7)

Ähnlich wie NUMERICAL INVESTIGATION OF AUTOMOTIVE RADIATOR LOUVERED FIN COMPACT HEAT EXCHANGER

Ähnlich wie NUMERICAL INVESTIGATION OF AUTOMOTIVE RADIATOR LOUVERED FIN COMPACT HEAT EXCHANGER (20)

Mehr von IAEME Publication

Mehr von IAEME Publication (20)

Kürzlich hochgeladen

Kürzlich hochgeladen (20)

NUMERICAL INVESTIGATION OF AUTOMOTIVE RADIATOR LOUVERED FIN COMPACT HEAT EXCHANGER