In the present work an attempt has been made to investigate the performance of a corrugated plate heat exchanger by the first law and the second law of thermodynamics. Experiments were conducted to determine the laminar convective heat transfer characteristics for fully developed flow of hot and cold fluid in alternate ducts. Experiments were conducted on a three channel 1-1 pass corrugated plate heat exchanger. Hot fluid was made to flow in the central channel to get cooled by cold fluid in the top and bottom channels in parallel and counter flow arrangements.

1. International Journal of Mechanical Engineering and Technology (IJMET), ISSN 0976 – 6340(Print),
ISSN 0976 – 6359(Online), Volume 5, Issue 9, September (2014), pp. 286-292 © IAEME
286
AN EXPERIMENTAL STUDY OF HEAT TRANSFER IN A CORRUGATED
PLATE HEAT EXCHANGER
Ashish Kumar, Dr. Ajeet Kumar Rai, Vivek sachan
Department of Mechanical Engineering, SSET, SHIATS-DU, Allahabad (U.P) INDIA-211007
ABSTRACT
In the present work an attempt has been made to investigate the performance of a corrugated
plate heat exchanger by the first law and the second law of thermodynamics. Experiments were
conducted to determine the laminar convective heat transfer characteristics for fully developed flow
of hot and cold fluid in alternate ducts. Experiments were conducted on a three channel 1-1 pass
corrugated plate heat exchanger. Hot fluid was made to flow in the central channel to get cooled by
cold fluid in the top and bottom channels in parallel and counter flow arrangements. The average
effectiveness of the system is 48% higher in counter flow arrangement than in the parallel flow
arrangement. The average non-dimensional exergy loss (E/Qmax) of the system is also calculated and
found 33% less in counter flow arrangement than in the parallel flow arrangement.
Keywords: Corrugated Plate Heat Exchanger, Effectiveness, Exergy Loss.
Nomenclature
A Cross sectional area, (m2
)
c Specific heat at constant pressure, (J kg-1
K-1
)
C Heat capacity rate, (W K-1
)
Dh Hydraulic diameter, (m)
E Exergy loss, (W)
f Friction factor
h heat transfer coefficient, (W m-2
K-1
)
L length, (m)
m Mass flow rate, (kg s-1
)
Q Heat transfer rate, (W)
R Capacity ratio
Re Reynolds number
INTERNATIONAL JOURNAL OF MECHANICAL ENGINEERING
AND TECHNOLOGY (IJMET)
ISSN 0976 – 6340 (Print)
ISSN 0976 – 6359 (Online)
Volume 5, Issue 9, September (2014), pp. 286-292
© 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. International Journal of Mechanical Engineering and Technology (IJMET), ISSN 0976 – 6340(Print),
ISSN 0976 – 6359(Online), Volume 5, Issue 9, September (2014), pp. 286-292 © IAEME
287
T Temperature, (K)
V Average velocity of fluid, (m s-1
)
R Density of air, (kg m-3
)
m Viscosity of air, (N s m-2
)
Suffixes
c Cold
e Environment, ambient
h Hot
i Inlet
m Mean
min Minimum
max Maximum
o Outlet
w Wall
INTRODUCTION
Heat exchangers are the devices which are used to transfer the heat between two flowing
fluids. In the 1930s plate heat exchangers were introduced to meet the hygienic demand of the dairy
industry. These days plate heat exchangers are widely used in many fields like automobile industry,
power industry, dairy, food processing, chemical and petrochemical industries. In heat exchangers,
there is usually no external heat and work interactions, typical applications involve heating or
cooling of a fluid stream of concern and evaporation or condensation of single or multi component
fluid streams. The objective may be to recover or reject heat, or sterilize, pasteurize, fractionate,
distill, concentrate, crystallize, or control process fluid. In a few heat exchangers, the fluid
exchanging heat is in indirect or direct contact. In most of the heat exchangers, heat transfer between
fluids takes place through a separating wall or into and out of a wall in a transient manner. In many
heat exchangers, the fluids are separated by a heat transfer surface and ideally they do not mix or
leak. Such exchangers are referred to as direct transfer type, or simply recuperate. Common
examples of heat exchangers are shell-and tube exchangers, automobile radiators, condensers,
evaporators, air pre-heaters, and cooling towers. If no phase change occurs in any of the fluids in the
exchanger, it is sometimes referred to as a sensible heat exchanger. There could be internal thermal
energy sources in the exchangers, such as in electric heaters and nuclear fuel elements. Combustion
and chemical reaction may take place within the exchanger, such as in boilers, fired heaters, and
fluidized-bed exchangers. Mechanical devices may be used in some exchangers such as in scraped
surface exchangers, agitated vessels, and stirred tank reactors. Heat exchangers are devices used to
transfer heat between two or more fluid streams at different temperatures. Heat exchangers find
widespread use in power generation, chemical processing, electronics cooling, air-conditioning,
refrigeration, and automotive applications. A corrugated plate type heat exchanger, as compared to
a similar sized tube and shell heat exchanger, is capable of transferring much more heat. This is due
to the large area that plates provide over tubes. Corrugated plate heat exchangers are used for
transferring heat for any combination of gas, liquid and two-phase streams. Fins or appendages
added to the primary heat transfer surface (tubular or plate) with the aim of increasing the heat
transfer area. The two most common types of extended surface heat exchangers are plate-fin heat
exchangers and tube-fin heat exchangers. Consist of a stack of parallel thin plates that lie between
heavy end plates. Each fluid stream passes alternately between adjoining plates in the stack,
exchanging heat through the plates. The plates are corrugated for strength and to enhance heat

3. International Journal of Mechanical Engineering and Technology (IJMET), ISSN 0976 – 6340(Print),
ISSN 0976 – 6359(Online), Volume 5, Issue 9, September (2014), pp. 286-292 © IAEME
288
transfer by directing the flow and increasing turbulence. These exchangers have high heat-transfer
coefficients and area, the pressure drop is also typically low, and they often provide very high
effectiveness. However, they have relatively low pressure capability. A corrugated plate type heat
exchanger consists of plates instead of tubes to separate the hot and cold fluids. It would be
misleading to consider only capital cost aspect of the design of a heat exchanger, since high
maintenance cost increase the total cost during the service life of the heat exchanger. Therefore,
exergy analysis and energy saving are very important parameters in the heat exchanger design.
EXPERIMENTAL SETUP AND PROCEDURE
The experimental setup established, to investigate the heat transfer characteristics in the
corrugated channel for different flow conditions is shown in the basic components as numbered in
the schematic and their names given along with the caption, of the experimental apparatus include a
water loop and a measurement system. The water loop comprises a water tank containing a heater, a
pump and a temperature controller; the flow rate is measured by noting time for collection of fixed
volume. Importantly, the components in the water system are thermally insulated such that the wall
temperature of the corrugated channel can be maintained at a nearly constant temperature . The test
section of the corrugated plate heat exchanger has three ducts. The geometrical characteristics are
given in the table1.
Two different cases of parallel and counter flow arrangements have been made. Hot fluid was
made to flow through the central channel and cold fluid through the two outer channels. Copper-
Constantan thermocouples are used to measure the temperature of the fluids at the inlet and outlet of
the heat exchanger.
Table 1: Geometrical characteristics of plate heat exchanger
Sl. No Parameters Value
1 Length of the test section, L 100 cm
2 Width of the test section, a 10 cm
3 High of the test section, b 5 cm
4 Corrugation angle 30o
Fig 1: Photograph showing Experimental setup

4. International Journal of Mechanical Engineering and Technology (IJMET), ISSN 0976 – 6340(Print),
ISSN 0976 – 6359(Online), Volume 5, Issue 9, September (2014), pp. 286-292 © IAEME
289
Fig.2: Corrugated Plates of Corrugated Plate Heat Exchanger
Methodology
The experimental data was used to calculate the heat transfer rate
Q= mhCh (Thi - Tho)
Each channel has equal flow area and wetted perimeter given by,
Ao=H.W,and p=2(W+H)
Heat capacity
Ch = mhcph
Cc = mccpc
LMTD= [(Tho –Tci) – (Thi - Tco)]] / ln[(Tho – Tci)/(Thi-Tco)]
ε =[Cc(Tco –Tci)]/[Cmin ln(Thi – Tci)]
The exergy changes for the two fluids are obtained as given below:
For hot fluid (i.e. water),
Eh = Te [Ch ln (Tho/Thi)]
And for cold fluid
Ec = Te [Cc ln (Tco/Tci)
Exergy loss for steady state open system can be found as a sum of individual fluid exergy
E = Eh+Ec
RESULTS AND DISCUSSION
Fig. 1 shows the variation of effectiveness of the corrugated plate heat exchanger in parallel
and counter flow arrangement at the different hot water temperature ranging from 50 0
C to 70 0
C at
the interval of 50
C.
A maximum of 100% and a minimum of 3.3% higher effectiveness is observed in case of
counter flow at hot water temperature of 50 0
C and 65 0
C respectively.

5. International Journal of Mechanical Engineering and Technology (IJMET), ISSN 0976 – 6340(Print),
ISSN 0976 – 6359(Online), Volume 5, Issue 9, September (2014), pp. 286-292 © IAEME
290
Fig 2: Variation of effectiveness at different hot water inlet temperatures for counter and parallel
flow arrangements
Fig.3: Variation of Exergy loss at different hot water inlet temperatures for counter and parallel flow
arrangements
Fig. 3 shows the variation of exergy loss at different hot water inlet temperatures for counter
and parallel flow arrangements. It is observed that exergy loss is found more in paralle flow than in
counter flow. A maximum of 39.5% and a minimum of 35.5 % rise in exergy loss is calculated in
counter flow arrangement than in parallel flow arrangement.
Fig 4: Variation of max heat transfer at different hot water temperatures for counter and parallel flow
arrangements

6. International Journal of Mechanical Engineering and Technology (IJMET), ISSN 0976 – 6340(Print),
ISSN 0976 – 6359(Online), Volume 5, Issue 9, September (2014), pp. 286-292 © IAEME
291
Fig 4 shows that the maximum heat transfer increases with rise in hot fluid inlet
temperature.The maximum value of heat transfer is at the maximum hot water temperature of 70 0
C
in parallel and counter flow respectively. Maximum value of heat transfer is 5% greater in parallel
flow than in the counter flow arrangement.
Fig.5: Variation of E/Qmax at different hot water inlet temperatures for counter and parallel flow
arrangements
Fig. 5 shows the variation of E/Qmax at different hot water inlet temperatures for counter and
parallel flow arrangements. As the hot water inlet temperature increases, the non-dimensional exergy
loss goes on decreases. The non-dimesional exergy loss is found more in parallel flow than in the
counter flow arrangement. A maximum of 35% and minimum of 29% more exergy loss is found in
the parallel flow arrangement than in the counter flow arrangement. Further it is observed that the
rate of reduction in the exergy loss is more in the parallel flow than in the counter flow.
CONCLUSIONS
An experimental set up of heat exchanger was made of GI sheet for heat transfer study. The
test section was formed by three identical channels with hot fluid in the middle and cold fluid in the
adjacent channels. Plates had sinusoidal wavy surfaces having corrugation angle of 300
.Water-water
fluid combinations are selected in parallel and counter flow arrangements of the heat exchanger.
Bulk temperature of the hot fluid was in the range of 500
C to 700
C whereas cold fluid was in the
range of 300
C to 400
C. It is observed that the log mean temperature difference of the system is 42%
higher in parallel flow arrangement than in the counter flow arrangement. Qmax of the system is 3.5%
higher in the parallel flow arrangement than in the counter flow arrangement. Average exergy loss of
the system is also calculated and found 37% higher in parallel flow arrangement than in counter flow
arrangement.
REFERENCES
[1] Han, J.C. (1984) “Heat transfer and friction in channels with two opposite rib-roughened
walls.” Transaction of the ASME, Vol. 106, pp (2384-2398).
[2] Jorge A.W. Gut, Renato Fernandes, José M. Pinto, Carmen C. Tadini (2004) Thermal
model validation of plate heat exchangers with generalized Configurations. Chemical
Engineering Science vol.59 pp.( 4591 – 4600).

7. International Journal of Mechanical Engineering and Technology (IJMET), ISSN 0976 – 6340(Print),
ISSN 0976 – 6359(Online), Volume 5, Issue 9, September (2014), pp. 286-292 © IAEME
292
[3] J.E. Hesselgreaves (2000) Rationalization of second law analysis of heat exchangers.
International Journal of Heat and Mass Transfer Vol. 43 pp (4189-4204).
[4] J. R. Maughan and F. P. Incropera, (1990). “Regions of Heat Transfer Enhancement for
Laminar Mixed Convection in a Parallel Plate Channel”, Int. J. Heat Mass Transfer, Vol. 33,
No.3, pp.555-570.
[5] Kotcfiogiu, I. Ayhon, T. Olgon, H and Ayhan, B., (1998). “Heat transfer and flow structure
in rectangular channel flows”, Tr. J. of engineering and environmental science, Vol.22,
pp185-195.
[6] L. B. Wang, Y. H. Zhang, Y. X. Su, and S. D. Gao. (2002). “Local and Average
Heat/Mass Transfer over Flat Tube Bank Fin Mounted In-Line Vortex Generators with
Small Longitudinal Spacing”, Journal of Enhanced Heat Transfer, Vol. 9, pp (77–87)
[7] Mahesh Kumar, K.S. Kasana, Sudhir Kumar and Om Prakash (2010) Evaluation of
Convective Heat Transfer Coefficient for Pool Boiling of Milk under Closed Condition,
samriddhi, Vol. 1, pp (2229-7111)
[8] Michael Looper (1994) Factors affecting milk composition of lactating cows Dairy Science.
vol.7, pp (2103-2115).
[9] Mustafa S Mahdi and Ajeet Kumar Rai (2012).A practical approach to design and
optimization of single phase liquid to liquid shell and tube heat exchanger, Mechanical
Engineering & Technology 3(3), pp.(378 – 386).
[10] Pandey S. D.and Nema V.K. (2012) Experimental analysis of heat transfer and friction
factor of nanofluid as a coolant in a corrugated plate heat exchanger. Elsevier Science Direct
Experimental Thermal and Fluid Sciencevol. 38, pp (248–256).
[11] Pandey S. D., Nema V.K (2011) An experimental investigation of exergy loss reduction in
corrugated plate heat exchanger Elsevier Science Direct Energy vol.36 pp (2997-3001)
[12] Omar Mohammed Ismael, Dr. Ajeet Kumar Rai, HasanFalah Mahdi, Vivek Sachan
(2014) an experimental study of heat transfer in plate heat exchanger, International Journal
of Advanced Research in Engineering and Technology Vol 5, pp.(31-37).
[13] Shah, R. K., 1991, Compact heat exchanger technology and applications, in Heat Exchanger
Engineering, Vol. 2, pp (1–29).
[14] Shah, R. K. and W. W. Focke, 1988, Plate heat exchangers and their design theory, in Heat
[15] Transfer Equipment Design, Hemisphere Publishing, Washington, DC, vol.21,
pp. (227–254).
[16] W. R. Pauley and J. K. Eaton, (1994). “The Effect of Embedded Longitudinal Vortex
Arrays on Turbulent Boundary Layer Heat Transfer”, Transactions of the ASME, Journal of
Heat Transfer, Vol.116, pp (871-878).
[17] Yimin Xuan, Qiang Li (2000) Heat transfer enhancement of nanofluids International Journal
of Heat and Fluid Flow vol.21 pp (58-64).