effect of fouling factor
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ISSN 2249-6343
International Journal of Computer Technology and Electronics Engineering (IJCTEE)
Volume 2, Issue 3, June 2012
33
Optimization In Thermal Design Of Surface
Condenser By Changing Fouling Factor
Vijay K. Mehta,
Abstract: One of the most common operational challenges
encountered with heat exchangers is fouling. Fouling is the
build-up of sediments and debris on the surface area of a
heat exchanger that inhibits heat transfer. Fouling will
reduce heat transfer, impede fluid flow, and increase the
pressure drop across the heat exchanger. As with many
operational concerns, proper planning at the design stage
can minimize the effects of fouling down the road. Designers
use fouling factors to maximize the lifespan, runtime and
efficiency of a heat exchanger by accounting for the amount
of fouling an exchange will sustain over a period of time.
This often results in increasing the surface area of a heat
exchanger, so that fouling will not have as much of an
effect.. This means that the heat exchanger must be able to
function efficiently for long periods of time. Compensating
for fouling by enlarging surface area allows heat exchangers
to function with years of fouling.
Owing to the wide utilization of heat exchangers in
industrial processes, their cost minimization is an important
target for both designers and users.[1]
Keywords: Tube Materials, Fouling factor, Heat transfer
rate, Aspen plus condenser design software, Effect of
fouling factor & Heat transfer rate on surface Area.
1. INTRODUCTION:
Condenser is a type of heat exchanger in which hot fluid
becomes cold fluid. surface condenser is a commonly
used term for a water-cooled shell and tube heat
exchanger installed on the exhaust steam from a steam
turbine in thermal power stations. These
condensers are heat exchangers which convert steam
from its gaseous to its liquid state at a pressure
below atmospheric pressure where cooling water is in
short Supply; an air-cooled condenser is often used. An
air-cooled condenser is however significantly more
expensive and cannot achieve as low a steam turbine
exhaust pressure as a water-cooled surface condenser.
One of the most common operational challenges
encountered with heat exchangers is fouling. Fouling is
the build-up of sediments and debris on the surface area
of a heat exchanger that inhibits heat transfer. Fouling
will reduce heat transfer, impede fluid flow, and increase
the pressure drop across the heat exchanger [2]
Fouling depends on the type of heat exchanger, and the
kind of fluids being transferred. Due to different designs,
composition, and transfer fluid, each type of heat
exchanger will suffer fouling in unique ways. The tube
side of a shell and tube heat exchanger is usually easy to
clean but the shell side can be more difficult to access.
Plate heat exchangers can be taken apart for cleaning on
both sides. Some heat exchangers can be cleaned every
night when the equipment is not in use, while others can
only be cleaned every few months or years. In order to
reduce the amount of fouling in a heat exchanger,
equipment should be cleaned as often as possible. If a
plate heat exchanger were to suffer from the effects of
fouling, extra plates can be added to re-gain performance
if the space permits in the frame.
2. TYPES OF FOULING
There are several types of fouling, each forming
depending on the type of fluid and conditions. The
following are some of the more common fouling
mechanisms;
2.1 Crystallization
Crystallization is one of the most common types of
fouling. Certain salts commonly present in natural waters
have a lower solubility in warm water than cold.
Therefore, when cooling water is heated during the
cooling process (particularly at the tube wall) these
dissolved salts will crystallize on the surface in the form
of scale. [Common Solution: reducing the temperature of
the heat transfer surface often softens the deposits]
2.2 Sedimentation
Sedimentation, the depositing of dirt, sand, rust, and
other small matter is also common when fresh water is
used. This can be controlled to a degree by the heat
exchanger design. [Common Solution: velocity control]
2.3 Biological
Biological Organic growth material occurs from chemical
reactions, and can cause considerable damage when built
up. [Common Solution: material selection]
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ISSN 2249-6343
International Journal of Computer Technology and Electronics Engineering (IJCTEE)
Volume 2, Issue 3, June 2012
34
2.4 Chemical Reaction
Chemical Reaction Coking appears where hydrocarbon
deposits in a high temperature application. [Common
Solution: reducing the temperature between the fluid and
the heat transfer surface]
2.5 Corrosion
Corrosion can destroy surface areas of the heat
exchangers, creating costly damage. Fouling will slow
down heat transfer and damage equipment unless it is
dealt with accordingly. [Common Solution: material
selection]
2.6 Freezing Fouling
Freezing Fouling results from overcooling at the heat
transfer surface causing solidification of some of the fluid
stream components. [Common Solution: reducing the
temperature gradient between the fluid and the heat
transfer surface.[3]
3. FOULING FACTOR
The most common way to account for the effects of
fouling in a tubular heat exchanger is the application of a
fouling factor. The fouling factor is a predetermined
number that represents the amount of fouling a particular
heat exchanger transferring a particular fluid will sustain.
In the heat transfer equation the fouling factor is added to
the other thermal resistances to calculate the Total
Thermal Resistance which is the reciprocal of U clean
(Overall Heat transfer coefficient). There is no direct
calculation to determine the appropriate fouling factor to
use for a given fluid in a particular application; however
guidelines do exist to help determine an appropriate
fouling factor. The most common compilation of fouling
factors, to be used for a variety of fluid in various
applications, is supplied by Tubular Exchanger
Manufacturers Association (TEMA). The below table is a
list of general fouling factors used for shell and tube heat
exchangers and common fluids and applications [3]
Table-1 Typical Fouling Factor value for different
condition OF water [4]
Table-2 Typical Fouling Factor value for different
fluids [4]
ConditionsCooling
Water < 50°C
Cooling
Water <50°C
Cooling
Water >50°C
Cooling
Water
>50°C
Cooling Water
velocityv < 1 m/s v > 1 m/s v < 1 m/s
v > 1 m/s
Sea 0.00009 0.00009 0.00018 0.00018
Brackish 0.00035 0.00018 0.00053 0.00035
Cooling tower
with inhibitor0.00018 0.00018 0.00035 0.00035
Cooling tower
without
inhibitor
0.00053 0.00053 0.00088 0.0007
City grid 0.00018 0.00018 0.00035 0.00035
River
mimimum0.00018 0.00018 0.00035 0.00035
River average 0.00053 0.00035 0.0007 0.00035
Engine jacket 0.00018 0.00018 0.00018 0.00018
Demineralized
or distilled0.00009 0.00009 0.00009 0.00009
Treated Boiler
Feedwater0.00018 0.00009 0.00018 0.00018
Boiler
blowdown0.00035 0.00035 0.00035 0.00035
Type of Water
Typical Fouling Factors [m2K/W]
Group Fluid
Fouling Factor
Rf (m2K/W)
Gasoil 0.00009
Tansformer 0.00018
Lubrication 0.00018
Heat Transfer oil 0.00018
Hydraulic 0.00018
Quenching Oil 0.0007
Fuel Oil 0.0009
Hydrogen 0.00176
Engine exhaust 0.00176
Steam 0.00009
Steam with oiltraces 0.00018
Cooling fluid vapours with
oil traces 0.00035
Organic solvent vapours 0.00018
Compressed air 0.00035
Natural gas 0.00018
Stable top products 0.00018
Cooling Fluid 0.00018
Organic heat transfer fluids 0.00018
Salts 0.00009
LPG, LNG 0.00018
MEA and DEA (Amines) solutions 0.00035
DEG and TEG (Glycols) solutions 0.00035
Stable side products 0.00018
Stable bottom products 0.00018
Caustics 0.00035
Vegetable Oils 0.00053
Refrigerating Liquid 0.0002
Several Fluids
Liquid
Gas &
Vapour
Oil
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ISSN 2249-6343
International Journal of Computer Technology and Electronics Engineering (IJCTEE)
Volume 2, Issue 3, June 2012
35
4. DESIGN OF SURFACE CONDENSER:
There are two design of heat exchanger
4.1 Thermal Design:
It’s a primary design of any heat exchanger in which u
optimise by changing flow rate, material etc. Also you
optimise in process by design of two or three pass system
on different loading in different season like as in winter
less cooling load required as compare to summer. This is
based on HEI codes.
Turbine Condensers are designed as per HEI-standards
for steam condensers (HEI means Heat Exchange
Institute) Since 1933 - HEI is a non profit trade
association committed to the technical advancement,
promotion, understanding and education of industrial
heat exchanger, vacuum system etc. HEI has developed
and published Standard
4.2 Mechanical Design:
Design & Construction Code:
Mechanical design based on these codes.
• ASME
• Sec VIII Div I, II, III
• Sec III
• Sec I
• TEMA
• IBR
• IS 2825
5. MATERIAL FOR CONSTRUCTION:
• CS (Plain CS & Micro Alloy Steels)
• LAS
• C-Mn, C-Mo, Cr.-Mo, Cr.-Mo. Ni. - Cr. - Mo,
Ni- Steel
• Stainless Steel.
• Austenitic, Ferritic, Martensitic, Duplex, Super
Duplex
• NF Metals & Alloys
• Al, Cu, Brass, Bronze, Monel, Cupronickel,
Titanium
6. SOFTWARE USED FOR CONDENSER DESIGN:
Condenser Design on Aspen-Plus Software
Compress Software
PVElite
LMTD Calculator.
Condenser Design (Cnd)
Double Pipe Heat Exchanger Design(DHex)
Casketed plate Exchanger Design (PH 2.0.1).
7. RESULTS OBTAINED FROM ASPEN PLUS SOFTWARE
Data taken from Sikalbaha 225 MW ± 10% Combined
Cycle (Dual Fuel) Power Plant Project – Bangladesh
Given Data[5]
Ambient Pressure 1.0130 bar
Ambient Temperature 35.0 ºC
Relative Humidity 98.0%
Design Conditions at different Gas Turbine Load
Steam inlet (kg/s)
Cooling Water Inlet & Condensate Outlet Temperature
(0C)
TABLE 3. Result table produced by Aspen plus
software based on given data of thermal design of
surface condenser [6]
Heat
Trasfer
Rate
(W/m2K)
596.1
Tube Materal (SS 304)
Shell & another part material
(Carbon Steel)
D
E
S
I
G
N
P
A
R
A
M
E
T
E
R
63Reading-1 When Rf=0
Surface Area=430.95m2
0.115Reading-1 When Rf=0.0001
Surface Area=549.30
Steam Inlet/Outlet
(0C)
Density of liquid
(kg/m3)993
Reading-1 When Rf=0.0005
Surface Area=757.46m2
38.5Reading-1 When Rf=0.0006
Surface Area=815.27m2
Water Inlet
(0C)
48.84Reading-1 When Rf=0.0002
Surface Area=637.09m2
5178.16Reading-1 When Rf=0.0003
Surface Area=648.5m2
Density of
vapor
(kg/m3)
0.08Reading-1 When Rf=0.0004
Surface Area=706.93m2
Water Flow Rate
(kg/s)
663.9
Code Requirement
ASME Code Sec VIII Div 1
TEMA Class
Same Design Parameter for 1 to 8
Readings. Only Fouling Factor change
as per Different condition of cooling
water
Water Outlet
(0C)
1269
995.6
858.4
850.3
773.6
722
670.8
45.5Reading-1 When Rf=0.0007
Surface Area=823.74m2
Reading-1 When Rf=0.0008
Surface Area=917.44m2
SteamFlow
(kg/s)
Pressure
(bar)
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ISSN 2249-6343
International Journal of Computer Technology and Electronics Engineering (IJCTEE)
Volume 2, Issue 3, June 2012
36
8. OVERALL SUMMARY OF RESULT IN ALL
CASES:
Table-4.0 Effect of Fouling Factor on
Surface Area.
Table-5.0 Effect of Heat Transfer Rate
On Surface Area
Fig.-1. Surface Area V/S Fouling Factor
Heat
Transfer Rate
(W/m²K)
Surface
Area(m²)
1269 430.95
995.6 549.3
858.4 637.09
850.3 622.3
773.6 706.93
722 757.46
670.8 815.27
663.9 823.74
596.1 917.44
Fig.-2.Surface Area V/S Heat Transfer Rate
Fouling
Factor
(m² K/W)
Surface
Area (m²)
0 430.95
0.0001 549.3
0.0002 637.09
0.0003 622.3
0.0004 706.93
0.0005 757.46
0.0006 815.27
0.0007 823.74
0.0008 917.44
0.0009 968.9
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ISSN 2249-6343
International Journal of Computer Technology and Electronics Engineering (IJCTEE)
Volume 2, Issue 3, June 2012
37
9. CONCLUSION:
Heat transfer (Q) is directly proportional to heat
transfer rate (U) and Area. If the value of fouling
factor increases then heat transfer rate decreases.
So, more Surface area required to transfer the heat. So, when we select that type of material which has
less effect of fouling then we reduce the surface
area. Also select the cooling media which has low
value of fouling factor at that time also reduced the
surface area for heat transfer [11]
ACKNOWLEDGEMENT:
I would like to express my deep sense of gratitude
and respect towards my faculty members of Dept.
of Mechanical, Sri satya Sai Institute of Science &
Technology,Sehore,for his valuable guidance right
from selection of the topic. His constant
encouragement and support has been the cause of
my success in completing this.
REFERENCES: [1] www.sciencedirect.com, C. Caputo , Pacifico M. Pelagagge, Paolo SaliniUniversity of L’Aquila, Heat exchanger design
based on economic optimisationAntonio
[2] www.sciencedirect.com,Applied Thermal Engineering 28
(2008) 1798–1805, Design optimization of shell-and-tube heat
exchangers, Andre´ L.H. Costa a,*, Eduardo M. Queiroz b
[3] www.deltathx.com, Industrial Heat Exchangers
[4] R.C.Sachdeva, fundamentals of Engineering Heat and Mass
Transfer. 3rd edition, NEW AGE INTERNATIONAL
PUBLISHERS, page.Num.497
[5] Design data, ABENER Project: Sikalbaha 225 MW ± 10%
Combined Cycle (Dual Fuel) Power Plant Project Bangladesh,
Condenser Design. Performance for Guaranteed Balances
Revision 17/11/2011
[6] Author: Jim Lang (©SDSM&T, 2000), Condenser Design on
Aspen-Plus Software (Heat Exchanger design with a phase
change)
[7] Lang, Jim. “Design Procedure for Heat Exchangers on
Aspen Plus Software” Design Manual. June 1999.
[8] Aspen plus Simulator 10.0-1. User Interface (1998).
[9] KEVIN M. LUNSFORD , Bryan Research and Engineering,
Inc. - Technical Papers, Increasing Heat Exchanger Performance, Bryan Research & Engineering, Inc,Bryan, Texas.
[10]WOLVERINE TUBE HEAT TRANSFER DATA BOOK, ch-1_6-Fouling in Heat Exchangers.
[11] HTRI design manual, Page D6.2.1 (Rev.1)
ABOUT THE AUTHOR
Mr. Mehta Vijay K.
M-Tech Student (Thermal Engineering)
Contact No. +919998443111
E-Mail ID:[email protected]
Address: Surag para,Khetani road, Near Police line,
Vadia Devali-365480, Dist.-Amreli, State-Gujarat