This design project aims to propose a plate type heat exchanger that can meet given heat duty and find the number of plates required. Plate type heat exchanger uses metal plates to transfer heat between two fluids. Starting point of this design is to define given properties
Design Considerations for Plate Type Heat ExchangerArun Sarasan
A plate heat exchanger is a type of heat exchanger that uses metal plates to transfer heat between two fluids. This has a major advantage over a conventional heat exchanger in that the fluids are exposed to a much larger surface area because the fluids spread out over the plates. This facilitates the transfer of heat, and greatly increases the speed of the temperature change. Plate heat exchangers are now common and very small brazed versions are used in the hot-water sections of millions of combination boilers. The high heat transfer efficiency for such a small physical size has increased the domestic hot water (DHW) flowrate of combination boilers. The small plate heat exchanger has made a great impact in domestic heating and hot-water. Larger commercial versions use gaskets between the plates, whereas smaller versions tend to be brazed.
Selection and Design of Condensers
0 INTRODUCTION/PURPOSE
1 SCOPE
2 FIELD OF APPLICATION
3 DEFINITIONS
4 CHOICE OF COOLANT
5 LAYOUT CONSIDERATIONS
5.1 Distillation Column Condensers
5.2 Other Process Condensers
6 CONTROL
6.1 Distillation Columns
6.2 Water Cooled Condensers
6.3 Refrigerant Condensers
7 GENERAL DESIGN CONSIDERATIONS
7.1 Heat Transfer Resistances
7.2 Pressure Drop
7.3 Handling of Inerts
7.4 Vapor Inlet Design
7.5 Drainage of Condensate
8 SUMMARY OF TYPES AVAILABLE
8.1 Direct Contact Condensers
8.2 Shell and Tube Exchangers
8.3 Air Cooled Heat Exchangers
8.4 Spiral Plate Heat Exchangers
8.5 Internal Condensers
8.6 Plate Heat Exchangers
8.7 Plate-Fin Heat Exchangers
8.8 Other Compact Designs
9 BIBLIOGRAPHY
FIGURES
1 DIRECT CONTACT CONDENSER WITH INDIRECT COOLER FOR RECYCLED CONDENSATE
2 SPRAY CONDENSER
3 TRAY TYPE CONDENSER
4 THREE PASS TUBE SIDE CONDENSER WITH INTERPASS LUTING FOR CONDENSATE DRAINAGE
5 CROSS FLOW CONDENSER WITH SINGLE PASS COOLANT
Design Considerations for Plate Type Heat ExchangerArun Sarasan
A plate heat exchanger is a type of heat exchanger that uses metal plates to transfer heat between two fluids. This has a major advantage over a conventional heat exchanger in that the fluids are exposed to a much larger surface area because the fluids spread out over the plates. This facilitates the transfer of heat, and greatly increases the speed of the temperature change. Plate heat exchangers are now common and very small brazed versions are used in the hot-water sections of millions of combination boilers. The high heat transfer efficiency for such a small physical size has increased the domestic hot water (DHW) flowrate of combination boilers. The small plate heat exchanger has made a great impact in domestic heating and hot-water. Larger commercial versions use gaskets between the plates, whereas smaller versions tend to be brazed.
Selection and Design of Condensers
0 INTRODUCTION/PURPOSE
1 SCOPE
2 FIELD OF APPLICATION
3 DEFINITIONS
4 CHOICE OF COOLANT
5 LAYOUT CONSIDERATIONS
5.1 Distillation Column Condensers
5.2 Other Process Condensers
6 CONTROL
6.1 Distillation Columns
6.2 Water Cooled Condensers
6.3 Refrigerant Condensers
7 GENERAL DESIGN CONSIDERATIONS
7.1 Heat Transfer Resistances
7.2 Pressure Drop
7.3 Handling of Inerts
7.4 Vapor Inlet Design
7.5 Drainage of Condensate
8 SUMMARY OF TYPES AVAILABLE
8.1 Direct Contact Condensers
8.2 Shell and Tube Exchangers
8.3 Air Cooled Heat Exchangers
8.4 Spiral Plate Heat Exchangers
8.5 Internal Condensers
8.6 Plate Heat Exchangers
8.7 Plate-Fin Heat Exchangers
8.8 Other Compact Designs
9 BIBLIOGRAPHY
FIGURES
1 DIRECT CONTACT CONDENSER WITH INDIRECT COOLER FOR RECYCLED CONDENSATE
2 SPRAY CONDENSER
3 TRAY TYPE CONDENSER
4 THREE PASS TUBE SIDE CONDENSER WITH INTERPASS LUTING FOR CONDENSATE DRAINAGE
5 CROSS FLOW CONDENSER WITH SINGLE PASS COOLANT
Heat/light/electrical energy is out today’s necessity and has scarcity also. Energy conservation is key requirement of any industry at all times.
In general, industries use heat energy for conservation of raw material to finished product. The source of heat energy is generally saturated or super heated steam. The steam generation is common use one boiler with carity of fuels. Whatever may be the fuel the generation should be as economy as possible which adds to the product cost. Further the usage of steam and recycling steam condensate back to boiler is an art depending on plant layouts.
In this project the steam generator is water tube boiler fired with rice husk. The steam is transferred to the tyre/tube moulds where tyres/tubes are cured while the heat is rejected to the tyres the condensate forms and this condensate is put back to the boiler. While doing so the steam is also stopped back to boiler without rejecting complete heat to the product. This gets flashed into atmosphere at feed water tank. The science of separation of condensate from steam saves energy. Better the separation more the fuel conservation.
In the steam generator the fuel is burnt to heat the water and form steam. This fuel burnt flue gas carries lot of energy, out through chimney. Prior to exhausting through the heat left in flue need to be recovered, through heat recovery mechanisms’. In this project an air-preheater condensate heat recovery unit is the major energy consuming station.
• Types of heat exchangers
• Classification of heat exchangers
• components of heat exchanger
• Materials of heat exchanger
• troubleshooting of heat exchanger
An overview of distillation column design concepts and major design considerations. Explains distillation column design concepts, what you would provide to a professional distillation column designer, and what you can expect back from a distillation system design firm. To speak with an engineer about your distillation column project, call EPIC at 314-207-4250.
Parallel flow heat exchanger is analysed with CFD tool. A comparative study of the analytical and experimental data is carried out to better understand the temperature profile, surface heat flux and heat transfer co-efficient parameters of the heat exchanger
ABSTRACT
Heat/light/electrical energy is out today’s necessity and has scarcity also. Energy conservation is key requirement of any industry at all times.
In general, industries use heat energy for conservation of raw material to finished product. The source of heat energy is generally saturated or super heated steam. The steam generation is common use one boiler with carity of fuels. Whatever may be the fuel the generation should be as economy as possible which adds to the product cost. Further the usage of steam and recycling steam condensate back to boiler is an art depending on plant layouts.
In this project the steam generator is water tube boiler fired with rice husk. The steam is transferred to the tyre/tube moulds where tyres/tubes are cured while the heat is rejected to the tyres the condensate forms and this condensate is put back to the boiler. While doing so the steam is also stopped back to boiler without rejecting complete heat to the product. This gets flashed into atmosphere at feed water tank. The science of separation of condensate from steam saves energy. Better the separation more the fuel conservation.
In the steam generator the fuel is burnt to heat the water and form steam. This fuel burnt flue gas carries lot of energy, out through chimney. Prior to exhausting through the heat left in flue need to be recovered, through heat recovery mechanisms’. In this project an air-preheater condensate heat recovery unit is the major energy consuming station.
this ppt is made with the reference of heat exchangers that have been used in NHFI, it almost covers their every aspect that is their working, maintenance, and safety !!
so please suit yourself!!!
Heat/light/electrical energy is out today’s necessity and has scarcity also. Energy conservation is key requirement of any industry at all times.
In general, industries use heat energy for conservation of raw material to finished product. The source of heat energy is generally saturated or super heated steam. The steam generation is common use one boiler with carity of fuels. Whatever may be the fuel the generation should be as economy as possible which adds to the product cost. Further the usage of steam and recycling steam condensate back to boiler is an art depending on plant layouts.
In this project the steam generator is water tube boiler fired with rice husk. The steam is transferred to the tyre/tube moulds where tyres/tubes are cured while the heat is rejected to the tyres the condensate forms and this condensate is put back to the boiler. While doing so the steam is also stopped back to boiler without rejecting complete heat to the product. This gets flashed into atmosphere at feed water tank. The science of separation of condensate from steam saves energy. Better the separation more the fuel conservation.
In the steam generator the fuel is burnt to heat the water and form steam. This fuel burnt flue gas carries lot of energy, out through chimney. Prior to exhausting through the heat left in flue need to be recovered, through heat recovery mechanisms’. In this project an air-preheater condensate heat recovery unit is the major energy consuming station.
• Types of heat exchangers
• Classification of heat exchangers
• components of heat exchanger
• Materials of heat exchanger
• troubleshooting of heat exchanger
An overview of distillation column design concepts and major design considerations. Explains distillation column design concepts, what you would provide to a professional distillation column designer, and what you can expect back from a distillation system design firm. To speak with an engineer about your distillation column project, call EPIC at 314-207-4250.
Parallel flow heat exchanger is analysed with CFD tool. A comparative study of the analytical and experimental data is carried out to better understand the temperature profile, surface heat flux and heat transfer co-efficient parameters of the heat exchanger
ABSTRACT
Heat/light/electrical energy is out today’s necessity and has scarcity also. Energy conservation is key requirement of any industry at all times.
In general, industries use heat energy for conservation of raw material to finished product. The source of heat energy is generally saturated or super heated steam. The steam generation is common use one boiler with carity of fuels. Whatever may be the fuel the generation should be as economy as possible which adds to the product cost. Further the usage of steam and recycling steam condensate back to boiler is an art depending on plant layouts.
In this project the steam generator is water tube boiler fired with rice husk. The steam is transferred to the tyre/tube moulds where tyres/tubes are cured while the heat is rejected to the tyres the condensate forms and this condensate is put back to the boiler. While doing so the steam is also stopped back to boiler without rejecting complete heat to the product. This gets flashed into atmosphere at feed water tank. The science of separation of condensate from steam saves energy. Better the separation more the fuel conservation.
In the steam generator the fuel is burnt to heat the water and form steam. This fuel burnt flue gas carries lot of energy, out through chimney. Prior to exhausting through the heat left in flue need to be recovered, through heat recovery mechanisms’. In this project an air-preheater condensate heat recovery unit is the major energy consuming station.
this ppt is made with the reference of heat exchangers that have been used in NHFI, it almost covers their every aspect that is their working, maintenance, and safety !!
so please suit yourself!!!
Summary of lmtd and e ntu. The Log Mean Temperature Difference Method (LMTD) The Logarithmic Mean Temperature Difference(LMTD) is valid only for heat exchanger with one shell pass and one tube pass. For multiple number of shell and tube passes the flow pattern in a heat exchanger is neither purely co-current nor purely counter-current. The temperature difference between the hot and cold fluids varies along the heat exchanger. It is convenient to have a mean temperature difference Tm for use in the relation. s mQ UA T
3. The mean temperature difference in a heat transfer process depends on the direction of fluid flows involved in the process. The primary and secondary fluid in an heat exchanger process may flow in the same direction - parallel flow or cocurrent flow in the opposite direction - countercurrent flow or perpendicular to each other - cross flow
Optimization of a Shell and Tube Condenser using Numerical MethodIJERA Editor
The purpose of this study was to investigate the effect of installation of the tube external surfaces, their parameter and variable in a shell-and-tube condenser. Variation of heat transfer coefficient with each variable of shell and tube condenser was measured each test. The optimization tube outside diameter size was analyzed and use extended surface area attached tube with tube material and tube layout and arrangement (Number of tube a triangular or hexagonal arrangement) on shell-and tube condenser. The computer programming was used to get faster output in less time. Results suggest that mean heat transfer coefficient in variable condition were mainly at velocity is fixed. And also average additional surfaces and tube layout and the arrangement comparison with the quantity of the heat transfer.
To demonstrate the effect of cross sectional area on the heat rate.
To measure the temperature distribution for unsteady state conduction of heat through the uniform plane wall and the wall of the thick cylinder.
The experiment demonstrates heat conduction in radial conduction models It
allows us to obtain experimentally the coefficient of thermal conductivity of some unknown materials and in this way, to understand the factors and parameters that affect the rates of heat transfer.
To understand the use of the Fourier Rate Equation in determining the rate of heat flow for of energy through the wall of a cylinder (radial energy flow).
To use the equation to determine the constant of proportionality (the thermal conductivity, k) of the disk material.
To observe unsteady conduction of heat
Shell & tube heat exchanger single fluid flow heat transferVikram Sharma
This article was produced to highlight the fundamentals of single-phase heat exchanger rating using Kern's method. The content is strictly academic with no reference to industrial best practices.
Layer-Type Power Transformer Thermal Analysis Considering Effective Parameter...AEIJjournal2
Since large power transformers belong to the most valuable assets in electrical power networks it is
suitable to pay higher attention to these operating resources. Thermal impact leads not only to long-term
oil/paper-insulation degradation; it is also a limiting factor for the transformer operation. Therefore, the
knowledge of the temperature, especially the hottest spot (HST) temperature, is of high interest. This paper
presents steady state temperature distribution of a power transformer layer-type winding using conjugated
heat transfer analysis, therefore energy and Navier-Stokes equations are solved using finite difference
method. Meanwhile, the effects of load conditions and type of oil on HST are investigated using the model.
Oil in the transformer is assumed nearly incompressible and oil parameters such as thermal conductivity,
special heat, viscosity, and density vary with temperature. Comparing the results with those obtained from
finite integral transform checks the validity and accuracy of the proposed method
heat exchanger is a device that transfers heat between two or more fluids. The fluids may be separated by a solid wall to prevent mixing or they may be in direct contact. Heat exchangers are widely used in a variety of applications, including:
Heating and cooling systems
Power plants
Chemical processing
Food processing
Refrigeration
Air conditioning
Numerical Modeling and Simulation of a Double Tube Heat Exchanger Adopting a ...IJERA Editor
The double tube heat exchangers are commonly used in industry due to their simplicity in design and also their
operation at high temperatures and pressures. As the inlet parameters like temperatures and mass flow rates
change during operation, the outlet temperatures will also change. In the present paper, a simple approximate
linear model has been proposed to predict the outlet temperatures of a double tube heat exchanger, considering it
as a black box. The simulation of the heat exchanger has been carried out first using the commercial CFD
software FLUENT. Next the linear model of the double tube heat exchanger based on lumped parameters has
been developed using the basic governing equations, considering it as a black box. Results have been generated
for outlet temperatures for different inlet temperatures and mass flow rates of the cold and hot fluids. The results
obtained using the above two methods have then been discussed and compared with the numerical results
available in the literature to justify the basis for the assumption of a linear approximation. Comparisons of the
predicted results from the present model show a good agreement with the experimental results published in the
literature. The assumptions of linear variation of outlet temperatures with the inlet temperature of one fluid
(keeping other inlet parameters fixed) is very well justified and hence the model can be employed for the
analysis of double tube heat exchangers.
EXPERIMENTAL STUDY OF HEAT TRANSFER FROM PLATE FIN ARRAY IN MIXED CONVECTION ...ijiert bestjournal
The work summarized in this paper presents an exper imental study of heat transfer from plate fin in mixed convection mode enhancement by the us e of plate fins is presented. After a brief review of the basic methods used to enhance the hea t transfer by simultaneous increase of heat transfer surface area as well as the heat tran sfer coefficient,a simple experimental method to assess the heat transfer enhancement is p resented. The method is demonstrated on plate fins as elements for the heat transfer enhanc ement,but it can in principle be applied also to other fin forms. That is varying various paramet ers (height,spacing). The order of the magnitude of heat transfer enhancement obtained exp erimentally,it was found that by a direct comparison of Nu and Re no conclusion regarding the relative performances could be made. This is because the dimensionless variables are int roduced for the scaling of heat transfer and pressure drop results from laboratory to large scal e but not for the performance comparison. Therefore a literature survey of the performance co mparison methods used in the past was also performed. Experiments will carried out on mix ed convection heat transfer from plate fin heat sinks subject to the influence of its geometry and heat flux. A total of 9 plate fins were pasted into the upper surface of the base plate. Th e area of the base plate is 150mm by 150mm. The base plate and the fins were made of alu minum. For all tested plate fin heat sinks,however,the heat transfer performance for h eat sinks with plate fins was better than that of solid pins.
International Journal of Engineering Research and DevelopmentIJERD Editor
Electrical, Electronics and Computer Engineering,
Information Engineering and Technology,
Mechanical, Industrial and Manufacturing Engineering,
Automation and Mechatronics Engineering,
Material and Chemical Engineering,
Civil and Architecture Engineering,
Biotechnology and Bio Engineering,
Environmental Engineering,
Petroleum and Mining Engineering,
Marine and Agriculture engineering,
Aerospace Engineering.
Complex Engineering Problem (CEP) Descriptive Form.
Simultaneous Heat and Mass Transfer.
The concentric tube heat exchanger is replaced with a compact, plate-type heat exchanger that consists of a stack of thin metal sheets, separated by N gaps of width a. The oil and water flows are subdivided into N/2 individual flow streams, with the oil and water moving in opposite directions within alternating gaps. It is desirable for the stack to be of a cubical geometry, with a characteristic exterior dimension L.
(a) parallel flow
(b) counter flow,
A counter flow, concentric tube heat exchanger is used to cool the lubricating oil for a large industrial gas turbine engine. The flow rate of cooling water through the inner tube (Di - 25 mm) is 0.2 kg/s,.
Cosmetic shop management system project report.pdfKamal Acharya
Buying new cosmetic products is difficult. It can even be scary for those who have sensitive skin and are prone to skin trouble. The information needed to alleviate this problem is on the back of each product, but it's thought to interpret those ingredient lists unless you have a background in chemistry.
Instead of buying and hoping for the best, we can use data science to help us predict which products may be good fits for us. It includes various function programs to do the above mentioned tasks.
Data file handling has been effectively used in the program.
The automated cosmetic shop management system should deal with the automation of general workflow and administration process of the shop. The main processes of the system focus on customer's request where the system is able to search the most appropriate products and deliver it to the customers. It should help the employees to quickly identify the list of cosmetic product that have reached the minimum quantity and also keep a track of expired date for each cosmetic product. It should help the employees to find the rack number in which the product is placed.It is also Faster and more efficient way.
Forklift Classes Overview by Intella PartsIntella Parts
Discover the different forklift classes and their specific applications. Learn how to choose the right forklift for your needs to ensure safety, efficiency, and compliance in your operations.
For more technical information, visit our website https://intellaparts.com
Saudi Arabia stands as a titan in the global energy landscape, renowned for its abundant oil and gas resources. It's the largest exporter of petroleum and holds some of the world's most significant reserves. Let's delve into the top 10 oil and gas projects shaping Saudi Arabia's energy future in 2024.
Sachpazis:Terzaghi Bearing Capacity Estimation in simple terms with Calculati...Dr.Costas Sachpazis
Terzaghi's soil bearing capacity theory, developed by Karl Terzaghi, is a fundamental principle in geotechnical engineering used to determine the bearing capacity of shallow foundations. This theory provides a method to calculate the ultimate bearing capacity of soil, which is the maximum load per unit area that the soil can support without undergoing shear failure. The Calculation HTML Code included.
Explore the innovative world of trenchless pipe repair with our comprehensive guide, "The Benefits and Techniques of Trenchless Pipe Repair." This document delves into the modern methods of repairing underground pipes without the need for extensive excavation, highlighting the numerous advantages and the latest techniques used in the industry.
Learn about the cost savings, reduced environmental impact, and minimal disruption associated with trenchless technology. Discover detailed explanations of popular techniques such as pipe bursting, cured-in-place pipe (CIPP) lining, and directional drilling. Understand how these methods can be applied to various types of infrastructure, from residential plumbing to large-scale municipal systems.
Ideal for homeowners, contractors, engineers, and anyone interested in modern plumbing solutions, this guide provides valuable insights into why trenchless pipe repair is becoming the preferred choice for pipe rehabilitation. Stay informed about the latest advancements and best practices in the field.
Student information management system project report ii.pdfKamal Acharya
Our project explains about the student management. This project mainly explains the various actions related to student details. This project shows some ease in adding, editing and deleting the student details. It also provides a less time consuming process for viewing, adding, editing and deleting the marks of the students.
Automobile Management System Project Report.pdfKamal Acharya
The proposed project is developed to manage the automobile in the automobile dealer company. The main module in this project is login, automobile management, customer management, sales, complaints and reports. The first module is the login. The automobile showroom owner should login to the project for usage. The username and password are verified and if it is correct, next form opens. If the username and password are not correct, it shows the error message.
When a customer search for a automobile, if the automobile is available, they will be taken to a page that shows the details of the automobile including automobile name, automobile ID, quantity, price etc. “Automobile Management System” is useful for maintaining automobiles, customers effectively and hence helps for establishing good relation between customer and automobile organization. It contains various customized modules for effectively maintaining automobiles and stock information accurately and safely.
When the automobile is sold to the customer, stock will be reduced automatically. When a new purchase is made, stock will be increased automatically. While selecting automobiles for sale, the proposed software will automatically check for total number of available stock of that particular item, if the total stock of that particular item is less than 5, software will notify the user to purchase the particular item.
Also when the user tries to sale items which are not in stock, the system will prompt the user that the stock is not enough. Customers of this system can search for a automobile; can purchase a automobile easily by selecting fast. On the other hand the stock of automobiles can be maintained perfectly by the automobile shop manager overcoming the drawbacks of existing system.
COLLEGE BUS MANAGEMENT SYSTEM PROJECT REPORT.pdfKamal Acharya
The College Bus Management system is completely developed by Visual Basic .NET Version. The application is connect with most secured database language MS SQL Server. The application is develop by using best combination of front-end and back-end languages. The application is totally design like flat user interface. This flat user interface is more attractive user interface in 2017. The application is gives more important to the system functionality. The application is to manage the student’s details, driver’s details, bus details, bus route details, bus fees details and more. The application has only one unit for admin. The admin can manage the entire application. The admin can login into the application by using username and password of the admin. The application is develop for big and small colleges. It is more user friendly for non-computer person. Even they can easily learn how to manage the application within hours. The application is more secure by the admin. The system will give an effective output for the VB.Net and SQL Server given as input to the system. The compiled java program given as input to the system, after scanning the program will generate different reports. The application generates the report for users. The admin can view and download the report of the data. The application deliver the excel format reports. Because, excel formatted reports is very easy to understand the income and expense of the college bus. This application is mainly develop for windows operating system users. In 2017, 73% of people enterprises are using windows operating system. So the application will easily install for all the windows operating system users. The application-developed size is very low. The application consumes very low space in disk. Therefore, the user can allocate very minimum local disk space for this application.
1. 1
REPORT TO DEPARTMENT OF CHEMICAL ENGINEERING
MIDDLE EAST TECHNICAL UNIVERSITY
FOR COURSE: CHE-327 HEAT AND MASS TRANSFER
OPERATIONS
PLATE TYPE HEAT EXCHANGER DESIGN
GROUP MEMBERS:
ALARA MELISA AYDIN
COŞKU MOLER
RESKY SAPUTRA
METU
(25.05.2016)
Ankara, TURKEY
2. 2
ABSTRACT
This design project aims to propose a plate type heat exchanger that can meet given heat
duty and find the number of plates required. Plate type heat exchanger uses metal plates to transfer
heat between two fluids. Starting point of this design is to define given properties. It is asked us to
cool the inlet fluid which is waste stream from 65 oCto 40 oCusing cooling water at 15 oC.Several
information of the inlet and outlet streams are given such as the inlet and outlet temperature of
waste stream, mass flow rate of inlet stream, physical properties of waste and other constructional
data for the similar heat exchanger; vertical, horizontal distances, plate thickness, length, effective
channel width, enlargement factor, chevron angle etc. Several calculations are done in 2 parts. The
first one is geometry analysis used in order to find the required number of plates. The second one
is heat transfer analysis in order to find the required heat duty for both streams and actual heat
duties for clean and fouled involving trial-error solution. Some correlations is needed such as heat
transfer coefficient calculation, correlation of Nusselt number and Reynold number in which the
empirical equation needed. Assumptions are regarded at the beginning of the design. Finally, the
required heat duty for cold and hot streams are found 1.47 x 107 W and the actual heat duties for
clean and fouled are 2.62 x 107 W and 2.32 x 107 W, respectively. The total required number of
plates are also found as 105 plates.
3. 3
TABLE OF CONTENT
TABLE OF CONTENTS
NOMENCLATURE…………………………………………………………………………1
1. INTRODUCTION …………………………………………………………………..3
1.1. Problem Statement……………………………………………………………...4
1.2. The Calculation Method………………………………………………………..5
1.3. Assumptions……………………………………………………………………..8
2. SAMPLE CALCULATIONS…………………………………………………………10
2.1. Geometry Analysis………………………………………………………………10
2.2. Heat Transfer Analysis………………………………………………………….11
3. RESULT AND DISCUSSIONS……………………………………………………….14
4. CONCLUSIONS……………………………………………………………………….16
5. REFERENCES…………………………………………………………………………17
4. 4
NOMENCLATURE
Thi : inlet hot stream temperature 0c
Tho : outlet hot stream temperature 0c
Tci : inlet cold stream temperature 0c
Tco : outlet cold stream temperature 0c
mc : cold stream mass flow rate kg/s
mh : hot stream mass flow rate kg/s
Gc : The cold channel mass velocity kg/m2s
Gh : The hot channel mass velocity kg/m2s
Ch : steam heat capacity J/kg.K
Cc : ipa-water mixture heat capacity J/kg.K
Qc : Amount of heat transfer under clean condition W
Qf : Amount of heat transfer under fouled condition W
Uf : Fouled overall heat transfer coefficient W/m2K
Uc : overall heat transfer coefficient W/m2K
Ae : Actual effective area m2
A1 : Single plate efective area m2
A1p : Single plate projected area m2
Nt : total number of plates
Ne : The effective number of plates
Np : Number of passes
Ncp : the total number of channels per pass
Lv : Vertical distance m
5. 5
Lh : Horizontal distance m
t : Plate thickness m
Lc : Plate pack length m
Lw : Effective channel width m
p : The plate pitch m
b : the mean channel spacing m
Dh : The hydraulic diameter of the channel m
∅ : The enlargement factor
𝛽 : Chevron angle o
µh : viscocity of hot fluid N.s/m2
µc : viscocity of cold fluid N.s/m2
Pr : prandalt number
Re : reynolds number
Nu : nusselt number
hc : convective heat transfer coefficient on clod fluid W.m2/K
hh : convective heat transfer coefficient on hot fluid W.m2/K
𝑅𝑓ℎ : fouling factor for hot fluid m2.K/W
𝑅𝑓𝑐 : fouling factor for cold fluid m2.K/W
kw : thermal conductivity of the plate material W/m.K
6. 6
1. INTRODUCTION
Plate heat exchanger is a type of Heat Exchanger which consists of many corrugated
stainless-steel sheets separated by polymer gaskets and clamped into a steel frame. It transfers heat
by placing thin, corrugated metal sheets side by side and connecting them by gaskets. Flow of the
substances to be heated and cooled takes place between alternating sheets allowing heat to transfer
through the metal sheets.
Figure 1: Plate type heat exchanger
Some advantages using plate heat exchanger are high heat transfer area, high heat transfer
coefficient, having lower floor space requirements, multiple duties can be performed by a single
unit, most suitable type heat exchanger for lower flow rates and heat sensitive substances.
Moreover, area of heat transfer of plate heat exchanger can be increased by increasing the number
of the plates.
7. 7
1.1. Problem Statement
In this problem, a plate heat exchanger is needed to be designed for a specific purpose. This heat
exchanger should be able to cool a waste from 65°C to 40°C using cooling water which enters the
heat exchanger at 15°C. The mass flow rate of the waste stream is 140 kg/s and its properties may
be approximated as follows:
ρ = 985 kg/m3
μ = 510 x 10-6 kg/m.s
k = 0.650 W/m.K
Pr = 3.3
Cp = 4200 J/kg.K
Fouling resistance ≡ Fouling resistance of water= 0.0000069 m2.K/W (taken from Heat
Exchanger: Selection, Rating and Thermal Design, table 10.4)
Moreover, we are going to propose a plate type heat exchanger that can meet this heat duty and
find the number of plats required for the heat exchanger.
Some constructional data for a similar heat exchanger are given as follows:
Total effective area (Ae)= 110 m2
Vertical distance (Lv) = 1.55 m
Horizontal distance (Lh)= 0.43 m
Plate thickness (t)= 0.6 mm
Plate pack length (Lc)= 0.38 m
Effective channel width (Lw)= 0.63 m
Enlargement factor (∅)= 1.25
Chevron angle (𝛽 )= 45°
8. 8
Plates are stainless steel (kw = 16.5 W/m.K, taken from heat exchangers selection, Rating and
thermal design, table 10.1)
Figure 2: Main dimensions of a chevron plate and and developed and projected dimensions of a
chevron plate cross section normal to to the direction troughs.
1.2. The Calculation Method;
Calculation of this problem design are separated by 2 analysis.
The first one is geometry analysis. The channels increase the surface area of the plate as
compared to the original flat area. To express the increase of the developed length in relation to
the projected length, a surface enlargement factor,∅, is the defined as the ratio of the developed
length to the flat or projected length
∅ =
𝐷𝑒𝑣𝑒𝑙𝑜𝑝𝑒𝑑 𝑙𝑒𝑛𝑔𝑡ℎ
𝑃𝑟𝑜𝑗𝑒𝑐𝑡𝑒𝑑 𝑙𝑒𝑛𝑔𝑡ℎ
=
𝐴𝑐𝑡𝑢𝑎𝑙 𝑒𝑓𝑓𝑒𝑐𝑡𝑖𝑣𝑒 𝑎𝑟𝑒𝑎
𝑝𝑟𝑜𝑗𝑒𝑐𝑡𝑒𝑑 𝑝𝑙𝑎𝑡𝑒 𝑎𝑟𝑒𝑎
=A1/A1p
(1.1)
9. 9
Where Actual effective area can be calculated as (1.2)
Actual effective area (Ae) = Lp * Lw (1.2)
Or actual effective area can be calculated as Ae = A1 * Ne
Where the effective number of plates. Ne,can be estimated as Ne = Nt – 2
Also Lp and Lw can be estimated from the port distance Lv and Lh and port diameter Dp as
Lp ≈ Lv - Dp (1.3)
Lw ≈ Lh + Dp (1.4)
The value of enlargement factor is calculated the effective flow path.
From (1.3 and 1.4) we can make a new equation to find Lp.
Lp = Lv – Lw + Lh (1.5)
Flow channel is the conduit formed by two adjacent plates between the gaskets. The cross section
of a corrugated surface being very complex, the mean channel spacing, b, is defined as (1.6)
b = p –t (1.6)
The plate pitch (p) can be determined from the compressed plate pack length (Lc), which usually
specified.
p = Lc / Nt (1.7)
Where Nt is the total number of plates.
The hydraulic diameter of the channel (Dh) can be estimated as (1.8)
Dh ≈ 2b / ∅ (1.8)
Finding the total number of channels per pass (Ncp) is obtained from (1.9)
Ncp = (Nt – 1) / 2 *Np (1.9)
Where Nt is total number of plates and Np is the number of passes.
10. 10
From those correlations we can find total number of plates required. With plate type heat
exchangers, heat transfer is enhanced. The heat transfer enhancement will strongly depend on the
chevron inclination angle (𝛽) relative to flow direction. Moreover, the performance of a chevron
plate will also depend upon the surface enlargement factor (∅), the channel profile, the mean
channel spacing (b), the temperature dependent physical properties, and especially the variable
viscosity effects.
The second one is heat transfer analysis. In order to find heat transfer coefficient (h),
correlation of Nusselt number (Nu) and Reynold number (Re) is needed. The Reynolds number
based on channel mass velocity and the hydraulic diameter of the channel is defined as (1.10)
Re = Gc * Dh / 𝜇 (1.10)
Where the channel mass velocity is given by (1.11)
Gc = mch / Ncp * b * Lw (1.11)
Correlation empirical equation is needed. The correlation in the form of (1.12) are proposed by
Kumar and the values of constants Ch and n are given in table 1.1 (Heat exchangers:Selection,
Rating and Thermal design 2nded, p. 395)
Nu = Ch * Ren * Pr * (
𝜇
𝜇 𝑤
)0.17 (1.12)
Table 1.1. Constants for single-phase heat transfer and pressure loss calculation in gasketed-plate
heat exchanger (Heat exchangers:Selection, Rating and Thermal design 2nded, p. 394).
11. 11
Overall heat transfer coefficient under fouling conditions is calculated as (1.13)
1
𝑈 𝑓
=
1
ℎℎ
+
1
ℎ 𝑐
+
𝑡
𝑘 𝑤
+ 𝑅𝑓ℎ + 𝑅𝑓𝑐 (1.13)
The required heat duty (Qr) for cold and hot streams is defined as (1.14)
Qr = (𝑚̇ ∗ 𝐶𝑝)c *(Tc2 – Tc1) = (𝑚̇ ∗ 𝐶𝑝)h * (Th1 – Th2) (1.14)
On the other hand, the actually obtained heat duty (Qf) for fouled conditions is defined as (1.15)
Qf = U*Ae*F*∆𝑇𝑙𝑚 (1.15)
In order to find ∆𝑇𝑙𝑚, equation (1.16) is defined as
∆𝑇𝑙𝑚 =
( 𝑇ℎ,𝑖𝑛 −𝑇𝑐,𝑜𝑢𝑡)−(𝑇ℎ ,𝑜𝑢𝑡−𝑇 𝐶,𝑖𝑛 )
ln(
( 𝑇ℎ,𝑖𝑛−𝑇 𝑐,𝑜𝑢𝑡 )
(𝑇ℎ,𝑜𝑢𝑡−𝑇 𝐶,𝑖𝑛)
(1.16)
For heat transfer analysis we are not given 𝑇𝑐,𝑜𝑢𝑡. So that physical properties of water cannot be
decided. Hereby trial-error solution is needed to find the correct 𝑇𝑐,𝑜𝑢𝑡 . To determine the correct
one we need to check both the required heat of hot and cold fluid. From energy balance analysis,
the required heat of hot and cold fluid must be same. The calculation for trial-error solution stops
until it reaches the equality of the required heat of hot and cold fluid.
1.3. Assumptions;
Physical properties are constant at 1 atm
Heat loses to or from the surrounding are negligible.
The kinetic and potential energy changes are negligible.
The heat exchanger operates at steady-state conditions.
No phase changes in the fluid streams.
Wall thermal resistances are distributed uniformly.
The velocity and temperature at the inlet of the heat exchanger on each fluid side are
uniform.
The heat transfer area (A) is distributed uniformly on each fluid side.
12. 12
The cold and hot stream mass flow rate are same
Number of passes is one pass
13. 13
2. SAMPLE CALCULATIONS
2.1 Geometry Analysis
The projected plate area
Single plate heat transfer area
The effective number of plates
Total number of plates
The plate pitch
the mean channel flow gap
The one channel flow area
The channel hydraulic
Ae 110m
2
Lv 1.55m Lh 0.43m t 0.0006m Lc 0.38m Lw 0.63m
kw 16.5
W
m K
Np 1
Lp Lv Lw Lh 1.35m
A1p Lp Lw 0.851m
2
A1 A1p 1.063m
2
Ne
Ae
A1
103.469
Nt Ne 2 105.469
p
Lc
Nt
3.603 10
3
m
b p t 3.003 10
3
m
Ach b Lw 1.892 10
3
m
2
Dh
2 b
4.805 10
3
m
14. 14
2.2 Heat Transfer Analysis
Total number pf channel per pass
(Trial-error method)
water properties at 313/288 = 300.5 K
waste properties
The mass flow rate per channel
for hot fluid for cold fluid
Ncp
Nt 1
2 Np
52.234
assume
8.410
4
Pa s k 0.611
W
m K
mc 140
kg
s
Pr
Cpc
k
5.748 Rfwater 0.0000069
m
2
K
W
Cpwaste 4200
J
kg K
kwaste 0.650
W
m K
Prwaste 3.3
waste 51010
6
Pa s
Rfwaste Rfwater 6.9 10
6
s
3
K
kg
mh mc 140
kg
s
mch
mc
Ncp
2.68
kg
s
Gch
mch
Ach
1.417 10
3
kg
s m
2
Gcc Gch 1.417 10
3
kg
s m
2
Reh
Gch Dh
waste
1.335 10
4
Rec
Gcc Dh
8.103 10
3
Cpc 4185.847
J
kg K
Tco 40 273 313K
Tci 15 273 288K Thi 65 273 338K Tho 40 273 313K
15. 15
Since Qrh and Qrc is almost same, then Tco assumption is acceptable
Table 10.6
or hhot= 3.283x104 W/m2K
or hcold=2.669x104 W/m2K
The clean overall heat transfer coefficient
or W/m2K
The fouled overall heat transfer coefficient
for counter current flow
the actual heat duties for clean and fouled surfaces
The required heat
45
0
Reh 100 Rec 100
ch 0.3 n 0.663
hhot
kwaste
Dh
ch Reh
n
Prwaste
1
3
3.283 10
4
kg
s
3
K
hcold
k
Dh
ch Rec
n
Pr
1
3
2.668 10
4
kg
s
3
K
Uc
1
1
hcold
1
hhot
t
kw
9.587 10
3
kg
s
3
K
9.587 10
3
Uf
1
1
Uc
Rfwaste Rfwater
8.467 10
3
kg
s
3
K
T2 Tho Tci 25K T1 Thi Tco 25K
LMT D 25K
Qc Uc Ae LMTD 2.636 10
7
W
Qf Uf Ae LMTD 2.328 10
7
W
Qrh mh Cpwaste Thi Tho( ) 1.47 10
7
W
Qrc mc Cpc Tco Tci( ) 1.465 10
7
W
16. 16
The safety factor
The precent over surface design
The cleanliness factor
Cs
Qf
Qrh
1.584
OS 100Uc Rfwaste Rfwater( ) 13.23
CF
Uf
Uc
0.883
17. 17
3 RESULTS AND DISCUSSONS
Objective of this project was to design a proper plate type heat exchanger. Several assumptions
were made while making the calculations. These assumptions are constant physical properties at
1 atm, negligible heat losses through the surroundings, negligible kinetic and potential energy
changes, operating at steady state, no phase changes, same mass flow rates and, uniform
temperature and velocity at the inlet of the heat exchanger. Calculation of this problem design
are separated by 2 analysis. The first one is geometry analysis and the second one is heat transfer
analysis. Geometry is analyzed by the given datas and calculations were made according to these
given datas. First of all projected length was calculated as 1.35 m and then projected area was
determined as 0.851 𝑚2
, by using this value single plate heat transfer area was calculated by
enlargement factor times projected area, enlargement factor,∅, is the defined as the ratio of the
developed length to the flat or projected length and found as 1.25. Up to here effective area and
single plate heat transfer area was calculated number of effective plates was found as 103.469 by
dividing effective area by single plate heat transfer area. Then total number of plates were found
as 105.469. After that plate pitch was determined as 3.603 ∗ 10−3
𝑚 and mean flow channel gap
was found by using that one as 3.003 ∗ 10−3
𝑚. The one channel flow area was determined by
using mean flow channel gap and found as 1.892 ∗ 10−3
𝑚2
hydraulic diameter was calculated
by 2 mean flow channel gap divided by enlargement factor and found as 4.805 ∗ 10−3
𝑚. Lastly
total number pf channel per pass was found as 52.234 and the geometry calculations were done.
In the heat transfer analyses in order to find heat transfer coefficient (h), correlation of Nusselt
number (Nu) and Reynold number (Re) is needed. The Reynolds number based on channel mass
velocity and the hydraulic diameter of the channel is defined as Re for hot fluid was determined
as 1.335 ∗ 104
and 8.303 ∗ 103
for the cold fluid. Where the channel mass velocity is given by
Gc 1.417 ∗ 103 𝑘𝑔
𝑚2 ∗𝑠
for both hot and cold fluid. In calculation of Nusselt number Correlation
empirical equation is needed. The correlation in the form of (1.12) are proposed by Kumar and
the values of constants Ch and n are given in table 1.1. This correlation gave us the heat transfer
coefficients directly by using Nusselt number as 3.283 ∗ 104 𝑊
𝑚2∗𝐾
for hot 2.668 ∗ 104 𝑊
𝑚2∗𝐾
for
cold fluid. By using these heat transfer coefficients, the overall heat transfer coefficient for hot
clean and fouled heat exchangers were found 9.587 ∗ 103 𝑊
𝑚2 ∗𝐾
, 8.467 ∗ 103 𝑊
𝑚2 ∗𝐾
respectively.
18. 18
In the determination of Qr and Qf ∆𝑇𝑙𝑚 is required and for heat transfer analysis we are not
given 𝑇𝑐,𝑜𝑢𝑡 . So that physical properties of water cannot be decided. Therefore trial-error solution
is needed to find the correct 𝑇𝑐,𝑜𝑢𝑡 . To determine the correct one we need to check both the
required heat of hot and cold fluid. From energy balance analysis, the required heat of hot and
cold fluid must be same. The calculation for trial-error solution goes until it reaches the equality
of the required heat of hot and cold fluid. To be sure of the 𝑇𝑐,𝑜𝑢𝑡 value was acceptable Qrh and
Qrc was determined and found as 1.47 ∗ 107
𝑊 and 1.465 ∗ 107
𝑊 which is really close to each
other so that Tcout value that choosen is acceptable. After calculation of ∆𝑇𝑙𝑚 Qr and Qf was
calculated as 2.637 ∗ 107
𝑊, 2.328 ∗ 107
𝑊 respectively. Lastly the safety factor was calculated
by dividing Qf to Qrh and found as 1.584 and cleanless factor as 0.883. According to the
literature Process heat transfer, 1950, typical design are based on safety factor of 1.6 which is
closer to 1.58. Moreover, based on Heat Exchanger: Selection, Rating, and Thermal Design, 2nd ,
Typical designs are based upon a cleanliness factor of 0.85 which is quite closer with our value.
19. 19
4 CONCLUSION
After performing the required equations which are given in calculation part, it is seen that
each plate is corrugated to increase the surface area and maximize heat transfer. Within a plate
heat exchanger, the fluid paths alternate between plates allowing the two fluids to interact, but not
mix, several times in a small area. The data from the similar heat exchanger is used in order to
define the heat exchanger that is used in the project. The goal of the project is to understand the
characteristics and design of a plate heat exchanger. By geometry and heat transfer analysis, the
total number of plates, the actual with fouled surface and required heat duty are found as 105
plates, 2.63 x 107 W and 2.32 x 107 W, respectively. It is considered that no heat loss to
surroundings however in reality there should be heat loss, therefore, error due to this assumption
must be considered in real life applications.
20. 20
5 REFERENCES
Incropera, F. (2012). Principles of heat and mass transfer (7th ed.). Singapore: John
Wiley & Sons Singapore Pte.
Leib, T., & Pereira, C. (2008). Perry's chemical engineers' handbook (8th ed.). New York:
McGraw-Hill.
Kakaç. S. (Sadik). Heal exchangers : selection, rating. and thermal design / Sadik Kakaç,
Hongtan Liu.-. 2nd ed
Kern,“Processheattransfer”,McGraw Hill,1950