IJRET : International Journal of Research in Engineering and Technology is an international peer reviewed, online journal published by eSAT Publishing House for the enhancement of research in various disciplines of Engineering and Technology. The aim and scope of the journal is to provide an academic medium and an important reference for the advancement and dissemination of research results that support high-level learning, teaching and research in the fields of Engineering and Technology. We bring together Scientists, Academician, Field Engineers, Scholars and Students of related fields of Engineering and Technology
Thermal rating of Shell & Tube Heat ExchangerVikram Sharma
This presentation file was created with the objective to provide a refresher course on the thermal rating of Shell and Tube heat exchanger for single-phase heat transfer
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.
Design method for shell tube heat exchangerKarnav Rana
Design method for shell tube heat exchanger
Selection of Cooling Medium or Heating Medium
shell tube heat exchanger
Heating mediums
Cooling mediums
Energy Balance and Heat Transfer Calculations
Mean Temperature Difference
Estimation of Overall Heat Transfer Coefficient
Finding Shell Diameter
applications of the principles of heat transfer to design of heat exchangersKathiresan Nadar
This file contain a very good description for the processes design of heat ex changer. the file courtesy is Prof. Anand Patwardhan ICT Mumbai (Deemed University)
Thermal rating of Shell & Tube Heat ExchangerVikram Sharma
This presentation file was created with the objective to provide a refresher course on the thermal rating of Shell and Tube heat exchanger for single-phase heat transfer
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.
Design method for shell tube heat exchangerKarnav Rana
Design method for shell tube heat exchanger
Selection of Cooling Medium or Heating Medium
shell tube heat exchanger
Heating mediums
Cooling mediums
Energy Balance and Heat Transfer Calculations
Mean Temperature Difference
Estimation of Overall Heat Transfer Coefficient
Finding Shell Diameter
applications of the principles of heat transfer to design of heat exchangersKathiresan Nadar
This file contain a very good description for the processes design of heat ex changer. the file courtesy is Prof. Anand Patwardhan ICT Mumbai (Deemed University)
Parts of shell and tube heat exchanger
Shell
Shell Side Pass Partition Plate
Baffles
Tube
Tube Side Pass Partition Plate
Tie Rods
Spacers
Tube Sheet
Expansion Joint
Design and Cost Optimization of Plate Heat Exchangerinventy
Research Inventy : International Journal of Engineering and Science is published by the group of young academic and industrial researchers with 12 Issues per year. It is an online as well as print version open access journal that provides rapid publication (monthly) of articles in all areas of the subject such as: civil, mechanical, chemical, electronic and computer engineering as well as production and information technology. The Journal welcomes the submission of manuscripts that meet the general criteria of significance and scientific excellence. Papers will be published by rapid process within 20 days after acceptance and peer review process takes only 7 days. All articles published in Research Inventy will be peer-reviewed.
design of shell and tube heat exchanger by using chemcad simulation software v.7, this ppt helps to provide the basic knowledge of design with TEMA type heat exchanger. The heat exchanger is widely used in industries, this exchanger exchanges heat to get the desired temperature of output and efficient way to exchange heat between to liquids. This is based on NRTL MODEL
This presentation is on shell and tube heat exchanger in which its design parameters and its troubleshooting conditions designed for better understanding and learning of all
Shell and Tube Heat Exchanger in heat TransferUsman Shah
This slide will explain you the chemical engineering terms .Al about the basics of this slide are explain in it. The basics of fluid mechanics, heat transfer, chemical engineering thermodynamics, fluid motions, newtonian fluids, are explain in this process.
What is heat exchanger & its Functions
Types of Heat Exchangers
Compact Heat Exchangers
Part of Fin Plate Heat Exchangers
Advantages & Disadvantages of Fin Plate Exchangers
Materials & Manufacturing
Overall Heat transfer Coefficient & Fouling Factor
LMTD Method
Effectiveness - NTU Method
NUMERICAL ENHANCEMENT OF HEAT TRANSFER OF FIN AND TUBE COMPACT HEAT EXCHANGER...anuragchoubey9
Heat exchangers are used in aero space engines have large heat transfer coefficient, large surface area per unit volume and low weight. The large surface area in compact heat exchangers is obtained by attaching closely spaced thin plate fins to the walls separating the two fluid. This study presents the airside performance of fin and tube compact heat exchangers with plain fin configuration. The effect of fin thickness, fin and tube material and fin spacing on the thermal-hydraulic characteristics is examined. Three-dimensional CFD simulations are carried out to investigate heat transfer and fluid flow characteristics of a plain fin and tube heat exchanger using the Commercial Computational Fluid Dynamics Code ANSYS fluent 16.0. Heat transfer and fluid flow characteristics with consideration of air property variability which is caused by the air temperature change of the heat exchanger are investigated for Reynolds numbers ranging from 2622 to 10498. Temperature drop and heat transfer rate is simulated using standard k-epsilon model with air flow is taken as steady and turbulent. Results are compared for two different material GH3044,S66280 and find out optimum heat transfer rate. After selecting best material GH3044 , we investigate the temperature variation and heat transfer characteristics of three different fin thickness 0.08 mm,0.1mm and 0.2 mm and three different fin spacing 0.8mm,1.1mm and 1.6 mm. domain having 0.8 mm fin spacing shows 5 % increase in heat transfer as compared to 1.1 mm fin spacing. Fin thickness 0.2 mm is better as compared to the other fin thickness and shows 8 % increment in heat transfer as compared to 0.1 mm fin thickness.
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!!!
Computational Model for Steady State Simulation of A Plate-Fin Heat Exchangerajit desai
High performance heat transfer devices are critical components in hybrid power generation systems. The design of a Recuperator for ‘waste heat recovery’ is crucial for reducing the operating cost of a hybrid system. Plate-fin heat exchangers occupy a special position among high performance heat exchangers because of the compactness, efficiency and flexibility they offer. The performance of these heat exchange devices is typically very sensitive to fluid property variations, axial conduction and heat losses to environment.
This thesis presents a numerical model of a plate fin heat exchanger in which fluid property variations including temperature driven changes in specific heat capacity, viscosity and heat transfer coefficients, and axial conduction effects are explicitly modeled. The objective is to predict fluid properties at outlet of the heat exchanger as accurately as possible, using a computationally less expensive procedure. Finite Volume Method is used for discretization of the domain. Momentum equation is modelled using flow admittance concept and energy transport across flow field is modeled using the Advection-Diffusion equation. The model solves for mass flow rate and temperatures of fluid streams and for temperatures of solid structure. The numerical model is validated against analytical solutions in the appropriate limits and then used to analyze performance of an example heat exchanger core under specific set of operating conditions prescribed by a Solid Oxide Fuel Cell-Gas Turbine hybrid system cycle, in order to demonstrate its utility.
The resulting numerical model is simple to implement and computationally efficient, therefore it can be easily integrated into complex system models as a sub-routine and also can be used as a stand-alone solver for parallel-flow or counter-flow heat exchanger simulation.
Parts of shell and tube heat exchanger
Shell
Shell Side Pass Partition Plate
Baffles
Tube
Tube Side Pass Partition Plate
Tie Rods
Spacers
Tube Sheet
Expansion Joint
Design and Cost Optimization of Plate Heat Exchangerinventy
Research Inventy : International Journal of Engineering and Science is published by the group of young academic and industrial researchers with 12 Issues per year. It is an online as well as print version open access journal that provides rapid publication (monthly) of articles in all areas of the subject such as: civil, mechanical, chemical, electronic and computer engineering as well as production and information technology. The Journal welcomes the submission of manuscripts that meet the general criteria of significance and scientific excellence. Papers will be published by rapid process within 20 days after acceptance and peer review process takes only 7 days. All articles published in Research Inventy will be peer-reviewed.
design of shell and tube heat exchanger by using chemcad simulation software v.7, this ppt helps to provide the basic knowledge of design with TEMA type heat exchanger. The heat exchanger is widely used in industries, this exchanger exchanges heat to get the desired temperature of output and efficient way to exchange heat between to liquids. This is based on NRTL MODEL
This presentation is on shell and tube heat exchanger in which its design parameters and its troubleshooting conditions designed for better understanding and learning of all
Shell and Tube Heat Exchanger in heat TransferUsman Shah
This slide will explain you the chemical engineering terms .Al about the basics of this slide are explain in it. The basics of fluid mechanics, heat transfer, chemical engineering thermodynamics, fluid motions, newtonian fluids, are explain in this process.
What is heat exchanger & its Functions
Types of Heat Exchangers
Compact Heat Exchangers
Part of Fin Plate Heat Exchangers
Advantages & Disadvantages of Fin Plate Exchangers
Materials & Manufacturing
Overall Heat transfer Coefficient & Fouling Factor
LMTD Method
Effectiveness - NTU Method
NUMERICAL ENHANCEMENT OF HEAT TRANSFER OF FIN AND TUBE COMPACT HEAT EXCHANGER...anuragchoubey9
Heat exchangers are used in aero space engines have large heat transfer coefficient, large surface area per unit volume and low weight. The large surface area in compact heat exchangers is obtained by attaching closely spaced thin plate fins to the walls separating the two fluid. This study presents the airside performance of fin and tube compact heat exchangers with plain fin configuration. The effect of fin thickness, fin and tube material and fin spacing on the thermal-hydraulic characteristics is examined. Three-dimensional CFD simulations are carried out to investigate heat transfer and fluid flow characteristics of a plain fin and tube heat exchanger using the Commercial Computational Fluid Dynamics Code ANSYS fluent 16.0. Heat transfer and fluid flow characteristics with consideration of air property variability which is caused by the air temperature change of the heat exchanger are investigated for Reynolds numbers ranging from 2622 to 10498. Temperature drop and heat transfer rate is simulated using standard k-epsilon model with air flow is taken as steady and turbulent. Results are compared for two different material GH3044,S66280 and find out optimum heat transfer rate. After selecting best material GH3044 , we investigate the temperature variation and heat transfer characteristics of three different fin thickness 0.08 mm,0.1mm and 0.2 mm and three different fin spacing 0.8mm,1.1mm and 1.6 mm. domain having 0.8 mm fin spacing shows 5 % increase in heat transfer as compared to 1.1 mm fin spacing. Fin thickness 0.2 mm is better as compared to the other fin thickness and shows 8 % increment in heat transfer as compared to 0.1 mm fin thickness.
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!!!
Computational Model for Steady State Simulation of A Plate-Fin Heat Exchangerajit desai
High performance heat transfer devices are critical components in hybrid power generation systems. The design of a Recuperator for ‘waste heat recovery’ is crucial for reducing the operating cost of a hybrid system. Plate-fin heat exchangers occupy a special position among high performance heat exchangers because of the compactness, efficiency and flexibility they offer. The performance of these heat exchange devices is typically very sensitive to fluid property variations, axial conduction and heat losses to environment.
This thesis presents a numerical model of a plate fin heat exchanger in which fluid property variations including temperature driven changes in specific heat capacity, viscosity and heat transfer coefficients, and axial conduction effects are explicitly modeled. The objective is to predict fluid properties at outlet of the heat exchanger as accurately as possible, using a computationally less expensive procedure. Finite Volume Method is used for discretization of the domain. Momentum equation is modelled using flow admittance concept and energy transport across flow field is modeled using the Advection-Diffusion equation. The model solves for mass flow rate and temperatures of fluid streams and for temperatures of solid structure. The numerical model is validated against analytical solutions in the appropriate limits and then used to analyze performance of an example heat exchanger core under specific set of operating conditions prescribed by a Solid Oxide Fuel Cell-Gas Turbine hybrid system cycle, in order to demonstrate its utility.
The resulting numerical model is simple to implement and computationally efficient, therefore it can be easily integrated into complex system models as a sub-routine and also can be used as a stand-alone solver for parallel-flow or counter-flow heat exchanger simulation.
EXPERIMENTAL AND THEORTICAL STUDY OF THE THERMAL PERFORMANCE OF HEAT PIPE HEA...IAEME Publication
Heat pipe heat exchanger (HPHE) considers one of the most useful devices for the recovery of waste heat energy. An Experimental study has been carried out on air to –air HPHE constructed of thermosyphon heat pipes with distilled water as the working fluid and a fill ratio of 75% from the evaporator length. Its model was composed of 4 rows, each row contains 12 copper tubes, each tube have ID= 9.5 mm, OD=10mm and length =950 mm and the rows of tubes were arranged in a staggered manner. Aluminum wavy plate fins of 0.1mm thickness were fixed among the tubes to increase the heat transfer area. Tests were conducted at various flow rates (air flow rate through evaporator and condenser sections) ranged between 0.12 and 0.37 kg/s and at different temperatures of air entering evaporator section (90, 100,110) ℃ to indicate discontinuity in the effectiveness when the flow rate ratio equal to one .
Thermal Design And Performance Of Two Phase Meso Scale Heat Exchangermartyp01
Dramatically increased power dissipation in electronic and electro-optic devices has prompted the development of advanced thermal management approaches to replace
conventional air cooling using extended surfaces. One such approach is Pumped Liquid Refrigerant Cooling (PLRC), in
which a refrigerant is evaporated in a cold plate in contact with the devices to be cooled. Heat is then rejected in an air or
water-cooled condenser and the working fluid is returned to the cold plate.
Design and verification of pipelined parallel architecture implementation in ...eSAT Publishing House
IJRET : International Journal of Research in Engineering and Technology is an international peer reviewed, online journal published by eSAT Publishing House for the enhancement of research in various disciplines of Engineering and Technology. The aim and scope of the journal is to provide an academic medium and an important reference for the advancement and dissemination of research results that support high-level learning, teaching and research in the fields of Engineering and Technology. We bring together Scientists, Academician, Field Engineers, Scholars and Students of related fields of Engineering and Technology
Fabrication and mechanical properties of stir cast al si12 cub4c compositeseSAT Publishing House
IJRET : International Journal of Research in Engineering and Technology is an international peer reviewed, online journal published by eSAT Publishing House for the enhancement of research in various disciplines of Engineering and Technology. The aim and scope of the journal is to provide an academic medium and an important reference for the advancement and dissemination of research results that support high-level learning, teaching and research in the fields of Engineering and Technology. We bring together Scientists, Academician, Field Engineers, Scholars and Students of related fields of Engineering and Technology
IJRET : International Journal of Research in Engineering and Technology is an international peer reviewed, online journal published by eSAT Publishing House for the enhancement of research in various disciplines of Engineering and Technology. The aim and scope of the journal is to provide an academic medium and an important reference for the advancement and dissemination of research results that support high-level learning, teaching and research in the fields of Engineering and Technology. We bring together Scientists, Academician, Field Engineers, Scholars and Students of related fields of Engineering and Technology.
IJRET : International Journal of Research in Engineering and Technology is an international peer reviewed, online journal published by eSAT Publishing House for the enhancement of research in various disciplines of Engineering and Technology. The aim and scope of the journal is to provide an academic medium and an important reference for the advancement and dissemination of research results that support high-level learning, teaching and research in the fields of Engineering and Technology. We bring together Scientists, Academician, Field Engineers, Scholars and Students of related fields of Engineering and Technology.
Experimental investigation on halloysite nano tubes & clay an infilled compos...eSAT Publishing House
IJRET : International Journal of Research in Engineering and Technology is an international peer reviewed, online journal published by eSAT Publishing House for the enhancement of research in various disciplines of Engineering and Technology. The aim and scope of the journal is to provide an academic medium and an important reference for the advancement and dissemination of research results that support high-level learning, teaching and research in the fields of Engineering and Technology. We bring together Scientists, Academician, Field Engineers, Scholars and Students of related fields of Engineering and Technology.
Nanoparticle based charge trapping memory device applying mos technology a co...eSAT Publishing House
IJRET : International Journal of Research in Engineering and Technology is an international peer reviewed, online journal published by eSAT Publishing House for the enhancement of research in various disciplines of Engineering and Technology. The aim and scope of the journal is to provide an academic medium and an important reference for the advancement and dissemination of research results that support high-level learning, teaching and research in the fields of Engineering and Technology. We bring together Scientists, Academician, Field Engineers, Scholars and Students of related fields of Engineering and Technology.
An extended database reverse engineering – a key for database forensic invest...eSAT Publishing House
IJRET : International Journal of Research in Engineering and Technology is an international peer reviewed, online journal published by eSAT Publishing House for the enhancement of research in various disciplines of Engineering and Technology. The aim and scope of the journal is to provide an academic medium and an important reference for the advancement and dissemination of research results that support high-level learning, teaching and research in the fields of Engineering and Technology. We bring together Scientists, Academician, Field Engineers, Scholars and Students of related fields of Engineering and Technology.
Analysis of Heat Transfer in Spiral Plate Heat Exchanger Using Experimental a...ijsrd.com
Heat transfer is the key to several processes in industrial application. In a present days maximum efficient heat transfer equipment are in demand due to increasing energy cost. For achieving maximum heat transfer, the engineers are continuously upgrading their knowledge and skills by their past experience. Present work is a skip in the direction of demonstrating the use of the computational technique as a tool to substitute experimental techniques. For this purpose an experimental set up has been designed and developed. Analysis of heat transfer in spiral plate heat exchanger is performed and same Analysis of heat transfer in spiral plate heat exchanger can be done by commercially procurable computational fluid dynamic (CFD) using ANSYS CFX and validated based on this forecasting. Analysis has been carried out in parallel and counter flow with inward and outward direction for achieving maximum possible heat transfer. In this problem of heat transfer involved the condition where Reynolds number again and again varies as the fluid traverses inside the section of flow from inlet to exit, mass flow rate of working fluid is been modified with time. By more and more analysis and experimentation and systematic data degradation leads to the conclusion that the maximum heat transfer rates is obtained in case of the inward parallel flow configuration compared to all other counterparts, which observed to vary with small difference in each section. Furthermore, for the increase heat transfer rate in spiral plate heat exchanger is obtain by cascading system.
Comparison of Shell and Tube Heat Exchanger using Theoretical Methods, HTRI, ...IJERA Editor
The aim of this article is to compare the design of Shell and Tube Heat Exchanger with baffles. Baffles used in
shell and tube heat exchanger improve heat transfer and also result in increased pressure drop. Shell and tube
heat exchanger with single segmental baffles was designed with same input parameters using 1) Kern’s
theoretical method; 2) ASPEN simulation software and 3) HTRI simulation software 4) SOLIDWORKS
simulation software. Shell side pressure drop and heat transfer coefficient are predicted. The results of all the
three methods indicated the results in a close range. The proven theoretical methods are in good agreement with
the simulation results
International Journal of Engineering Research and Applications (IJERA) aims to cover the latest outstanding developments in the field of all Engineering Technologies & science.
International Journal of Engineering Research and Applications (IJERA) is a team of researchers not publication services or private publications running the journals for monetary benefits, we are association of scientists and academia who focus only on supporting authors who want to publish their work. The articles published in our journal can be accessed online, all the articles will be archived for real time access.
Our journal system primarily aims to bring out the research talent and the works done by sciaentists, academia, engineers, practitioners, scholars, post graduate students of engineering and science. This journal aims to cover the scientific research in a broader sense and not publishing a niche area of research facilitating researchers from various verticals to publish their papers. It is also aimed to provide a platform for the researchers to publish in a shorter of time, enabling them to continue further All articles published are freely available to scientific researchers in the Government agencies,educators and the general public. We are taking serious efforts to promote our journal across the globe in various ways, we are sure that our journal will act as a scientific platform for all researchers to publish their works online.
A Review on Comparison between Shell And Tube Heat Exchanger And Helical Coil...ijiert bestjournal
The curved shape of the tube causes the flowing fluid to experience centrifugal force. The
extent of centrifugal force experienced depends on the local axial velocity of the fluid particle
and radius of curvature of the coil. The fluid particles flowing at the core of the pipe have
higher velocities than those flowing near to the pipe wall. Thus the fluid particles flowing
close to the tube wall experience a lower centrifugal force than the fluid particles flowing in
the tube core. This causes the fluid from the core region to be pushed towards the outer wall.
This stream bifurcates at the wall and drives the fluid towards the inner wall along the tube
periphery, causing generation of counter-rotating vortices called secondary flows which
produce additional transport of the fluid over the cross section of the pipe. This additional
convective transport increases heat transfer and the pressure drop when compared to that in a
straight tube.
Numerical Analysis of Header Configuration of the Plate-Fin Heat ExchangerIJMER
Numerical analysis of a plate fin heat exchanger accounting for the effect of fluid flow
maldistribution onthe inlet header configuration of the heat exchanger is investigated. In this analysis , it
was found that flow maldistribution has effect on the flow perpendicular to its velocity direction. The peak
velocity occurs in the central zone of the header while the velocityalong the perpendicular direction of the
inlet flow diminishes more and more. By this investigation,the results of the flow maldistribution are
presented for a plate fin heat exchangerwhich is reduced as compare to theexisting configuration of the
plate fin heat exchanger.
Study of Flow and Heat Transfer Analysis in Shell and Tube Heat Exchanger usi...SuginElankaviR
Heat exchangers are used to transfer heat from fluid at high temperature to fluid at lower temperature. Heat exchangers are used in industrial purposes in chemical industries, nuclear power plants, refineries, food processing, etc. Sizing of heat exchangers plays very significant role for cost optimization. Also, efficiency and effectiveness of heat exchangers is an important parameter while selection of industrial heat exchangers. Methods for improvement on heat transfer have been worked upon for many years in order to obtain high efficiency with optimum cost. In this research work, design of shell & tube heat exchanger with single segmented baffles and analyze the flow and temperature field inside the shell using Autodesk Simulation CFD 2015. When comparing the CFD analysis with experimental results, it was well correlation with negligible percentage of error. Thus, the series of baffles results in a significant increase in heat transfer coefficient per unit pressure drop in the heat exchanger.
IJRET : International Journal of Research in Engineering and Technology is an international peer reviewed, online journal published by eSAT Publishing House for the enhancement of research in various disciplines of Engineering and Technology. The aim and scope of the journal is to provide an academic medium and an important reference for the advancement and dissemination of research results that support high-level learning, teaching and research in the fields of Engineering and Technology. We bring together Scientists, Academician, Field Engineers, Scholars and Students of related fields of Engineering and Technology.
Heat Transfer Enhancement of Shell and Tube Heat Exchanger Using Conical Tapes.IJERA Editor
This paper provides heat transfer and friction factor data for single -phase flow in a shell and tube heat exchanger fitted with a helical tape insert. In the double concentric tube heat exchanger, hot air was passed through the inner tube while the cold water was flowed through the annulus. The influences of the helical insert on heat transfer rate and friction factor were studied for counter flow, and Nusselt numbers and friction factor obtained were compared with previous data (Dittus 1930, Petukhov 1970, Moody 1944) for axial flows in the plain tube. The flow considered is in a low Reynolds number range between 2300 and 8800. A maximum percentage gain of 165% in heat transfer rate is obtained for using the helical insert in comparison with the plain tube.
Cfd and conjugate heat transfer analysis of heat sinks with different fin geo...eSAT Journals
Abstract Heat sinks are commonly used for cooling of electronic devices. Heat sinks, an array of heat fins, remove the heat from the surfaces of the chips by enhancing the heat Transfer rate through heat conduction process. Heat can also be removed from the chip surfaces through forced convection heat transfer. In this project work, CFD and conjugate heat transfer analysis is carried out for various fin geometries with Zigzag, Fluted, Slanted mirror, Custom pin fin and staggered array configurations for low thermal resistance and minimum pressure drop. Numerical simulations are carried out for each of the above mentioned fin geometries with common base plate thickness of 2 mm, fin height of 28 mm and fin thickness of 1 mm for three different heat loads namely 50 W, 75 W and 100 W with air flow of 3.933 m/s (15 ft3/min or 15 CFM) and air inlet temperature of 25oC. The results are compared for thermal performance of a heat sink for each of above geometries and it is observe that the fin with Slanted Mirror geometry gives the best performance among all the other geometries for minimum Pressure drop. The average heat transfer coefficients for fins with slanted mirror geometry, zig zag configuration, fluted type, custom pin fin and staggered array are found to be 215 W/m2K, 164 W/m2K, 164 W/m2K, 157 W/m2K and 145 W/m2K respectively Keywords: Fin geometries of Heat sinks, Computational Fluid Dynamics, Conjugate heat transfer.
EXPERIMENTAL STUDY ON THE ANALYSIS OF HEAT ENHANCEMENT IN CORRUGATED TWISTED ...P singh
In heat exchanger, the enthalpy is transferred between two or more fluids, at different temperatures. The major challenge in designing a heat exchanger is to make the equipment more compact and achieve a high heat transfer rate using minimum pumping power. In recent years, the high cost of energy and material has resulted in an increased effort aimed at producing more efficient heat exchange equipment. Furthermore, as a heat exchanger becomes older, the resistance to heat transfer increases owing to fouling or scaling. The heat transfer rate can be improved by introducing a disturbance in the fluid flow thereby breaking the viscous and thermal boundary layer. However, in the process pumping power may increase significantly and ultimately the pumping cost becomes high. Therefore, to achieve a desired heat transfer rate in an existing heat exchanger at an economic pumping power, several techniques have been proposed in recent years and are discussed under the classification section.
In this work, a study of transient heat transfer in double tube heat exchanger has enhanced. The inner tube of the setup was made with corrugation on both inner and outer walls by twisting the pipe from one end, which gives the more swirling motion to the fluid particles flowing over it. The flow inside the pipe was considered as turbulent, and the analysis was done experimentally and theoretically by using the ANSYS workbench. The experimental results were compared with the experimental values taken in the setup done by considering the inner tube as normal pipe. In both heat exchangers the values were taken and compared with the theoretical analysis. Temperature distribution and heat transfer rate were calculated and the details of the study have been discussed in this paper.
Welcome to WIPAC Monthly the magazine brought to you by the LinkedIn Group Water Industry Process Automation & Control.
In this month's edition, along with this month's industry news to celebrate the 13 years since the group was created we have articles including
A case study of the used of Advanced Process Control at the Wastewater Treatment works at Lleida in Spain
A look back on an article on smart wastewater networks in order to see how the industry has measured up in the interim around the adoption of Digital Transformation in the Water Industry.
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.
Overview of the fundamental roles in Hydropower generation and the components involved in wider Electrical Engineering.
This paper presents the design and construction of hydroelectric dams from the hydrologist’s survey of the valley before construction, all aspects and involved disciplines, fluid dynamics, structural engineering, generation and mains frequency regulation to the very transmission of power through the network in the United Kingdom.
Author: Robbie Edward Sayers
Collaborators and co editors: Charlie Sims and Connor Healey.
(C) 2024 Robbie E. Sayers
Industrial Training at Shahjalal Fertilizer Company Limited (SFCL)MdTanvirMahtab2
This presentation is about the working procedure of Shahjalal Fertilizer Company Limited (SFCL). A Govt. owned Company of Bangladesh Chemical Industries Corporation under Ministry of Industries.
Water scarcity is the lack of fresh water resources to meet the standard water demand. There are two type of water scarcity. One is physical. The other is economic water scarcity.
Final project report on grocery store management system..pdfKamal Acharya
In today’s fast-changing business environment, it’s extremely important to be able to respond to client needs in the most effective and timely manner. If your customers wish to see your business online and have instant access to your products or services.
Online Grocery Store is an e-commerce website, which retails various grocery products. This project allows viewing various products available enables registered users to purchase desired products instantly using Paytm, UPI payment processor (Instant Pay) and also can place order by using Cash on Delivery (Pay Later) option. This project provides an easy access to Administrators and Managers to view orders placed using Pay Later and Instant Pay options.
In order to develop an e-commerce website, a number of Technologies must be studied and understood. These include multi-tiered architecture, server and client-side scripting techniques, implementation technologies, programming language (such as PHP, HTML, CSS, JavaScript) and MySQL relational databases. This is a project with the objective to develop a basic website where a consumer is provided with a shopping cart website and also to know about the technologies used to develop such a website.
This document will discuss each of the underlying technologies to create and implement an e- commerce website.
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.
Analysis comparing performance of a conventional shell and tube heat exchanger using kern, bell and bell delaware method
1. IJRET: International Journal of Research in Engineering and Technology eISSN: 2319-1163 | pISSN: 2321-7308
__________________________________________________________________________________________
Volume: 03 Special Issue: 03 | May-2014 | NCRIET-2014, Available @ http://www.ijret.org 486
ANALYSIS COMPARING PERFORMANCE OF A CONVENTIONAL
SHELL AND TUBE HEAT EXCHANGER USING KERN, BELL AND BELL
DELAWARE METHOD
Shweta Y Kulkarni 1
, Jagadish S B 2
, Manjunath M B3
1
Thermal Power Engg, Dept. of Mechanical Engg. VTURC Gulbarga
2
Thermal Power Engg, Dept. of Mechanical Engg. VTURC Gulbarga
3
Thermal Power Engg, Dept. of Mechanical Engg. VTURC Gulbarga
Abstract
The transfer of heat to and from process fluids is an essential part of most of the chemical processes. Therefore, heat exchangers
(HEs) are used extensively and regularly in process and allied industries and are very important during design and operation. The
most commonly used type of HE is the shell and tube heat exchanger. In the present study, a comparative analysis of a water to water
STHE wherein, hot water flows inside the tubes and cold water inside the shell is made, to study and analyze the heat transfer
coefficient and pressure drops for different mass flow rates and inlet and outlet temperatures, using Kern, Bell and Bell Delaware
methods. This paper purely aims at studying and comparing different methods of STHE and bringing out which method is better for
adopting in shell side calculations.
Keywords: STHE, Heat transfer coefficient, shell &Tube heat exchanger, Pressure Drop, TEMA, Bell Delaware method,
Kern Method & Bell method.
---------------------------------------------------------------------***---------------------------------------------------------------------
1. INTRODUCTION
Shell-and-tube heat exchangers _STHXs_ are widely used in
many industrial areas, and more than 35–40% of heat
exchangers are of this type due to their robust geometry
construction, easy maintenance, and possible upgrades. Besides
supporting the tube bundles, the baffles in shell-and-tube heat
exchangers form flow passage for the shell-side fluid in
conjunction with the shell. The most-commonly used baffle is
the segmental baffle, which forces the shell-side fluid going
through in a zigzag manner, hence, improves the heat transfer
with a large pressure drop penalty. This type of heat exchanger
has been well-developed and probably is still the most-
commonly used type of the shell and tube heat exchangers [1].
Heat exchangers are one of the most important devices of
mechanical systems in modern society. Most industrial
processes involve the transfer of heat and more often, it is
required that the heat transfer process be controlled. According
to Oko (2008), a heat exchanger is a device of finite volume in
which heat is exchanged between two media, one being cold and
the other being hot. There are different types of heat exchangers;
but the type widely used in industrial application is the shell and
tube [2]. Mass velocity strongly influences the heat-transfer
coefficient. Thus, with increasing mass velocity, pressure drop
increases more rapidly than does the heat-transfer coefficient.
Consequently, there will be an optimum mass velocity above
which it will be wasteful to increase mass velocity further. The
construction geometry and thermal parameters such as mass
flow rate, heat transfer coefficient etc are strongly influenced by
each other.[3]. There are design charts such as E-NTU
(Effectiveness- Number of Transfer Unit) curves and LMTD
(Logarithm Mean Temperature Difference) correction factor
curves for the analysis of simple types of exchangers. Similar
design charts do not exist for the analysis of complex heat
exchangers with multiple entries on the shell side and complex
flow arrangements (Ravikumaur et al, 1988).
In this way, the design of shell and tube heat exchangers is a
very important subject in industrial processes. Nevertheless,
some difficulties are found, especially in the shell-side design,
because of the complex characteristics of heat transfer and
pressure drop [4].
The flow in the shell side of a shell-and-tube heat exchanger
with segmental baffles is very complex. The baffles lead to a
stream inside the shell, which is partly perpendicular and partly
parallel to the tube bank. The gaps between the tubes and the
holes in the baffles and the gap between a baffle and the shell
cause leakage streams, which may modify the main stream
significantly. Since the tubes of the heat exchanger cannot be
placed very near to the shell, bypass streams S, may be formed,
which influence also the main stream. The flow direction of the
main stream relative to the tubes is different in the window
sections created by the baffle cut from that in the cross flow
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sections existing between the segmental baffles. This
necessitates the use of different equations to calculate the
pressure drop in the window sections to those used in the cross
flow sections. The spacing between the tube plates and the first
and the last baffle, which is mostly dictated by the diameter of
the inlet and oulet nozzles, differs in many cases from the
spacing between two adjacent baffles and some of the
aforementioned streams are not present in the first and in the last
heat exchanger sections. This adds to the complexity of the
problem [5].
In designing shell and tube heat exchangers, to calculate the heat
exchange area, different methods were proposed such as Kern
Method, Bell, Bell Delaware etc [6].
The present paper employs all the three methods mentioned
above to study and analyze various parameters of a shell and
tube heat exchanger and compare the results to identify which
method gives the best result.
2. KERN METHOD
The kern method was based on experimental work on
commercial exchangers with standard tolerances and will give a
reasonably satisfactory prediction of the heat-transfer coefficient
for standard designs. The prediction of pressure drop is less
satisfactory, as pressure drop is more affected by leakage and
bypassing than heat transfer. The shell-side heat transfer and
friction factors are correlated in a similar manner to those for
tube-side flow by using a hypothetical shell velocity and shell
diameter. As the cross-sectional area for flow will vary across
the shell diameter, the linear and mass velocities are based on
the maximum area for cross-flow: that at the shell equator. The
shell equivalent diameter is calculated using the flow area
between the tubes taken in the axial direction (parallel to the
tubes) and the wetted perimeter of the tubes. The method used
by D.Q. Kern is simple and more explanative. All the parameter
related to heat exchanger are obtained in well manner and brief
without any complication as compared to other method, the
calculation process is quite and simple detailed.
Among all the methods, the Kern method provided a simple
method for calculating shell side pressure drop and heat transfer
coefficient. However, this method cannot adequately account
the baffle to shell and tube to baffle leakage.
3. BELL METHOD
In Bell’s method the heat-transfer coefficient and pressure drop
are estimated from correlations for flow over ideal tube-banks,
and the effects of leakage, bypassing and flow in the window
zone are allowed for by applying correction factors. This
approach will give more satisfactory predictions of the heat-
transfer coefficient and pressure drop than Kern’s method; and,
as it takes into account the effects of leakage and bypassing, can
be used to investigate the effects of constructional tolerances
and the use of sealing strips. The procedure in a simplified and
modified form to that given byBell (1963), is outlined below.
The method is not recommended when the by-pass flow area is
greater than 30% of the cross-flow area, unless sealing strips are
used[5].
Bell (1978) has proposed a graphical method based on the
operating lines in stagewise process design, to estimate the
value of N. This procedure utilizes the inlet and outlet
temperatures of both hot and cold streams in which N is about 3.
In this work, it has been found that for N > 3, Bell’s method
frequently cannot be used to predict feasible designs of
multipass exchangers. Specifically, by following the procedure
used in the development of the Kremser equation in stagewise
process design (McCabe and Smith, 1976)[5]
4. BELL DELAWARE METHOD
Shell side flow is complex, combines crossflow and baffle
Window flow, as well as baffle-shell and bundle-shell bypass
streams and other complex flow patterns
In a baffled shell and tube heat exchanger, only a fraction of the
fluid flow through the shell side of a heat exchanger actually
flows across the tube bundle in the idealized path normal to the
axis of the tubes. The remaining fraction of the fluid flows
through bypass areas. The fluid seeks the flow path of less
resistance from the inlet to the outlet of the exchanger.
In the Bell Delaware method, the fluid flow in the shell is
divided into a number of individual streams A through F as
shown in FIG 1.
Fig- 1 cross section of shell and tube heat exchanger
Each of the streams from A to F introduces a correction factor to
the heat transfer correlation for ideal cross-flow across a bank of
tubes such as Jc, JL, Jb , Js, Jr .
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In the present study, efforts have been made to study Kern, Bell
& Bell Delaware method and apply these methods in calculating
heat transfer coeffient, Reynold’s number, pressure drops,
overall heat transfer coefficient etc for a heat exchanger which
has been designed and fabricated for our experimental
investigations and compare the results and identify which
method is more efficient in calculating the shell side parameters.
The heat transfer fluid used is water. Hot water flows inside the
tubes and cold water flows inside shell.
4.1 Fluid Properties Considered
Shell side fluid properties:
ρs = 1000 kg/m3
μs = 0.00088 N-s/ m2
Cps = 4.187kJ/kg’K
Ks = 0.00098 kJ/s-m’K.
Tube side fluid properties:
ρt = 1000 kg/m3
μt= 0.00086 N-s/ m2
Cpt = 4.187kJ/kg’K
Kt = 0.00098 kJ/s-m’K.
5. HEAT EXCHANGER SPECIFICATIONS:
In the present study, a stainless steel shell and tube heat
exchanger is used to study the various parameters of the heat
exchanger such as heat transfer coefficient, Reynolds’s number,
pressure drop, Overall heat transfer coefficient etc using water
as a heat transfer medium.
Specifications of the heat exchanger are as follows:
Shell diameter (Ds) 0.2m
Tube inside diameter (Di) 0.016m
Tube outside diameter (Do) 0.01924m
Pitch (Pt) 0.03m
Length of shell (Ls) 0.8m
Length of tube (Lt) 0.825m
Length of baffle (Lb) 0.2m
Number of baffles (Nb) 4
Number of tubes (Nt) 18
Number of shell passes (ns) 1
Number of tube passes (nt) 2
Clearance (C) 0.01076m
Bundle to shell diametrical clearance (Δb) 0.028m
Shell to baffle diametrical clearance (Δsb) 0.0254m
Tube to baffle diametrical clearance (Δtb) 0.0005m
6. NOMENCLATURES
Sm = Area of the shell side cross flow section (m2
).
Pt = Tube pitch (m).
Do = Tube outside diameter (m).
Di = Tube inside diameter (m).
Ds = Shell inside diameter (m).
Lb = Baffle spacing (m)
Ls= Length of shell (m).
Lt = Length of tube (m).
tb = Tube thickness (m).
Gs= Shell side mass velocity (kg/ m2
-s).
Gt = Tube side mass velocity (kg/ m2
-s).
Us= Shell side linear velocity (m/s).
Ut = Tube side linear velocity (m/s).
ms= Mass flow rate of the fluid on shell side (kg/s).
mt= Mass flow rate of the fluid on tube side (kg/s).
ρs = Shell side fluid density (kg/m3
).
ρt = Tube side fluid density (kg/m3
).
Res= Shell side Reynolds number.
Ret = Tube side Reynolds number.
Prs= Shell side Prandtl number.
Prt = Tube side Prandtl number
μs = Shell side fluid Viscosity (N-s/ m2
).
μt = Tube side fluid viscosity (N-s/ m2
).
μw = Viscosity a wall temperature (N-s/ m2
).
Cps = Shell side fluid heat capacity (kJ/kg’K).
Cpt = Tube side fluid heat capacity (kJ/kg’K).
Ks = Shell side fluid thermal conductivity (kJ/s-m’K).
Kt = Tube side fluid thermal conductivity (kJ/s-m’K).
ho= Shell side heat transfer coefficient (W/ m2
’K).
hi = Shell side ideal heat transfer coefficient (W/ m2
’K).
Nb= Number of baffles.
Nt = Number of tubes.
f = Friction factor.
ΔPs= Shell side pressure drop (Pa).
np = Number of tube passes.
C = Clearance between tubes.
Δb = Bundle to shell diametrical clearance.
Δsb=Shell to baffle diametrical clearance.
Δtb=Tube to bundle diametrical clearance.
Nss/Nc=Sealing strips per cross flow row.
Dotl=Ds - Δb
Ө = {Ds-(2*Lc)}/ Dotl
Fc=Fraction of total number of tubes in a crossflow section.
Jc=Correction factor for baffle cut and spacing.
Ssb=Shell to baffle leakage area (m2
).
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Stb=Tube to baffle leakage area (m2
).
Fbp = Fraction of the crossflow area available for bypass flow.
Sw= Window flow area (m2
).
Nc = Number of tube rows crossed in one crossflow section.
Ncw=Effective number crossflow rows in window zone.
ΔPc=Ideal cross flow pressure drop through one baffle space
(Pa).
ΔPw= Window zone pressure drop (Pa).
RL= correction factor for baffle leakage effect on pressure drop
Rb= correction factor on pressure drop for bypass flow.
Experimental study is done on the shell and tube water / water
heat exchanger and various parameters are calculated for
different mass flow rates and at varying inlet and outlet
temperatures. Calculations shown below are made using Kern,
Bell and Bell Delaware methods for a mass flow rate of
.0354Kg/s and further readings are shown for different flow
rates and comparison graphs are drawn.
6.1 Calculation of Shell Side Heat Transfer Coefficient
Using Kern Method:
As = {(Pt – Do)*D*Lb} /Pt
= {(0.03-0.01924)*0.2*.2}/(0.03)
= 0.01435 m2
Gs = ms / As
= 0.0354/0.01435
= 2.47 Kg/m2
sec
De = [4*{(Pt
2
*√3)/4} – {(π* Do
2
)/8}] / [(π*Do)/2]
=[4{(0.032
*√3/4}{(π*0.019242
)/8]/[(π*0.0924)/2]
= 0.0325m
Res = (Gs* De) / μs
= (2.47/0.0325)/0.00088
= 91.2
Prs = (Cps*μs) / Ks
= (4.187*0.00088)/0.00098
= 3.76
hs = 0.36*( Ks / De)* (Re^0.55)*( Pr^0.33)*{ (μs / μw)^0.14}
=0.35*(0.00098/0.0325)*(91.20.55
)*(3.760.33
)*1
hs = 0.201 W/m2o
K
6.2 Calculation of Shell Side Heat Transfer Coefficient
Using Bell Method:
Area of the Shell As = PT – OD/PT x Ds x PB
=[(0.03-0.01924)/(0.03)]*0.2*0.2
= 0.0143m2
Calculate the shell –side mass velocity
Gs = Ms/ As
= 0.0354/0.01432
=2.46 Kg/m2
Sec
Calculate the Reynolds number on shell side
Res = Gs do/ μ
= (2.46*0.01924)/(0.008)
=53.7645
Calculate the Prandtl number
Pr = Cp μ / K
=(4.187*0.00088)/(0.00098)
= 3.76
Ideal heat transfer co-efficient is given by
hoc* do/ K = Jh Re Pr1/3
(μ/ μw) 0.14
(hoc*0.01924)/(0.00098)=1*53.97*(3.761/3
)*1
hoc= 3.445W/m2 o
K
Now Jh is calculated, from the fig (2) at Reynolds no
Jh=1
Fn tube row correction factor
Tube vertical pitch, P't = 0.87 x PT (for triangular pitch)
= 0.87*0.03
=0.026
Baffle cut height, Hc = Ds x Bc
=0.2*0.25
=0.05
Height between Baffle tips = Ds – 2 x (Hc)
= 0.2-(2*0.05)
= 0.1
Ncv = HbT/ P't
=0.1/0.026
=3.8
Now from the figure (3) at Ncv, we get Fn, i.e, (tube row
correction factor)
Fn=1
Window Correction factor Fw:-
Height of the baffle chord to the top of the tube bundle, Hb is
given by
Hb = Db/ 2 – Ds (0.5 – Bc)
=(0.172/2)-0.2(0.5-0.25)
= 0.036
Db = Ds – ΔPbs
=(0.2-0.028)
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=0.172
Bb = Hb / Db
=0.036/0.0172
=0.209
Now from fig (4) at the cut of i.e, (Bb) we get Ra'=0.14
Now, the number of tubes in a window zone is given by
Nw = Nt x Ra'
=18*0.14
=2.54
Nc = Nt - 2Nw
=18-(2*2.52)
=12.96
Rw = 2Nw / Nt
=2*2.52/18
=0.28
From the figure (5) at Rw we get the value of Fw=1.08
Bypass correction Fb
Fb = exp [-α Ab/ As (1 – {2Ns / Ncv }1/3
)]
=exp [-1.5*(0.0344/0.0143)(1-(2*0.2/3.8)1/3
)]
=0.1496
Ab = [Ds – Db] x Bp
=[0.2-0.028]*0.2
=0.0344
Leakage correction factor FL.
FL = 1 – βL {Atb + 2 Asb / AL}
=1-0.5[0.011883+2*0.000305/0.01218]
=0.4874
AL = total leakage area = [Atb + Asb]
=[0.011883+0.000305]
=0.01218
Atb = Ct π do / 2 ( Nt – Nw)
= 0.02548*π*0.01924/2(18-2.52)
=0.011883
Asb = CsDs / 2 (2π – θb)
=0.0005*0.2/2(2π-0.18)
=0.000305
Shell – side heat transfer co-efficient is given by
hs = hco x Fn x Fw x Fb x FL .
=3.445*1*1.08*0.1496*0.4875
hs =0.271W/m2o
K
6.3 Calculation of Shell Side Heat Transfer Coefficient
Using Bell Delaware Method:
STEP 1: Calculate the shell side area at or near the centre line
for one cross flow section Sm,
Sm = Lb*[(Ds – Dotl) + {(Dotl – Do)*(Pt -Do)}/Pt ]
Sm=.2*[(.2 – .172) + {(.172 – .01924)*(.03 -.01924)}/.03 ]
Sm =0.017 m2
STEP 2: Calculate shell side mass velocity Gs and linear
velocity Us.
Gs = ms / Sm
Gs = .0354 / .017
Gs= 2.082 kg/ m2
-s
Us = Gs / ρs
Us = 2.082 / 1000
Us = .002082 m/s
STEP 3: Calculate shell side Reynolds number Res.
Res = (Gs* Do) / μs
Res = (2.082* .01924) / .00088
Res = 45.52
STEP 4: Calculate shell side Prandtl number Prs.
Prs = (Cps*μs) / Ks
Prs = (4.187*.00088) / .00098
Prs = 3.7597
STEP 5: Calculate the colburn j factor ji.
ji = a1*[{1.33 / (Pt / Do)} ^ a]* (Res^a2)
ji = 1.36*[{1.33 / (.03 / .01924)} ^ .719]* (45.52^-.657)
ji = 0.0987
STEP 6: Calculate the value of the coefficient a.
a = a3 / [1+ {0.14* (Res^a4)}]
a = 1.450 / [1+ {0.14* (45.52^.519)}]
a = 0.719
Where, a1=1.360, a2 = -.657, a3 = 1.450 and a4 = .519 for Res <
100, are the coefficients to be taken from the table given in
Kakac book for the obtained value of Reynolds number and
pitch and layout.
STEP 7: Calculate the ideal heat transfer coefficient hi.
hi = ji *Cps*( ms / Sm)*{( 1/Prs)^(2/3)}*{ (μs / μw)^0.14}
hi = .0987 *4.187*( .0354/ .017)*{( 1/3.7597)^(2/3)}*{ (.00088
/ .00088)^0.14}
hi = 0.3559 W/ m2
’K
STEP 8: Calculate the fraction of total tubes in crossflow Fc.
Consider, Ө = {Ds-(2*Lc)}/ Dotl
Ө = {.2 - (2*.05}/ .172
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Ө = 0.581 rad
Fc =(1 /π)*[π +(2*Ө) *sin{cos-1
(Ө)}-{2* cos-1
(Ө)}]
Fc=(1 /π)*[π +(2*.581) *sin{cos-1
(.581)}-{2*cos-1
(.581)}]
Fc =0.695
Here Lc = 0.25* .2 = 0.05 for 25% baffle cut.
STEP 9: Calculate the correction factor for baffle cut and
spacing Jc.
The value of Jc can be obtained from the fig 2.33 of wolverine
tube heat transfer data book Page No. 107 for the corresponding
value of Fc.
Jc = 1.05
STEP 10: Calculate shell to baffle leakage area for one baffle
Ssb.
Ssb = Ds*(Δsb / 2)*[π - cos-1
(Ө)]
Ssb = .2*(.0254 / 2)*[π - cos-1
(.581)]
Ssb = 0.00556 m2
STEP 11: Calculate tube to baffle leakage area for one baffle
Stb.
Stb = (π*Do)*(Δtb / 2)*Nt*[(1 +Fc)/ 2]
Stb = (π*.01924)*(.0005 / 2)*18*[(1 +.695)/ 2]
Stb = 0.0002305 m2
STEP 12: Calculate
(Ssb + Stb) / Sm
(.00556 + 0.0002305) / .017
(Ssb + Stb) / Sm = 0.349
&
Ssb / (Ssb + Stb)
0.00556 / (0.00556+0.0002305)
Ssb / (Ssb + Stb) = 0.9601
STEP 13: Calculate the correction factor for baffle leakage
effects JL.
The value of JL can be obtained from the fig 2.34 of wolverine
tube heat transfer data book Page No. 108 for the corresponding
value obtained in step 12 above.
JL = 0.89
STEP 14: Calculate the fraction of the crossflow area available
for bypass flow Fbp.
Fbp = (Lb / Sm)*(Ds - Dotl)
Fbp = (.2 / .017)*(.2- .172)
Fbp = 0.3383
STEP 15: Calculate the correction factor for bundle bypassing
effects due to the clearance between the outermost tubes and the
shell and pass dividers Jb.
The value of Jb can be obtained from the fig 2.35 of wolverine
tube heat transfer data book Page No. 109 for the corresponding
value of Fbp.
Jb = 0.96
STEP 16: The correction factors Js and Jr are equal to 1 for
Res>=100. But for Res<100, Jr can be obtained from Fig. 2.37 of
wolverine tube heat transfer data book Page No. 111.
Jr = 0.88
STEP 17: Calculate the shell side heat transfer coefficient for
the exchanger ho.
ho = hi *Jc*JL*Jb*Js *Jr
ho = 0.3559 *1.05*0.89*0.96
ho = 0.32 W/ m2
’K
Calculation Of Shell Side Pressure Drop Using Kern
Method:
Nb = {Ls / (Lb + tb)} – 1
= {0.800/(0.2+0.00162)}-1
Nb+1= 3.96
f = exp {0.576 – (0.19*Ln Res)}
= exp {0.567-(0.19*Ln*91.2)}
= 0.754
ΔPs = [f* Gs
2
* Ds*( Nb+1)] / [2* ρs* De*{(μs / μw)^0.14}]
=[0.754*(2.472
)*0.2*3.96]/ [2*1000*0.0325*1]
ΔPs = 0.056Pa
6.4 Calculation of Shell Side Pressure Drop Using Bell
Method:
Cross flow zones
ΔPc = ΔPi F 'b F 'L
Ideal tube Pr drop (ΔPi)
(ΔPi) = 8Jf Ncv ρus2
/ 2 (μ/ μw) -0.14
=8x7.5x3.38x1000x0.0024622
/2x1
=0.6136
Res = ρus do/ μ
=1000x0.00246x0.01924/0.00088
=53.78
F 'b bypass correction factor for Pr drop.
F 'b = exp [-αAb/ As (1 – {2Ns / Ncc }1/3
)]
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=exp[(-5x0.0344/0.01434)x(1-(2x0.2)1/3
]
=0.04255
Where, α = 5.0, if Re < 100 for laminar region
α = 4.0 if Re > 100 for turbulent region.
F 'L leakage factor for Pr drop.
F 'L = 1- βL {Atb + 2 Asb/ AL}
=1-0.7(0.0118830+2x0.000305/0.1218)
=0.2820
ΔPc=ΔpiFb’Fl’
=0.6136x0.2820x0.04255
=0.00736
Window zone pressure drop.
ΔPw = F 'L (2 + 0.6 Nwv) ρuz2
/2
=0.2820(2+0.6x0.833)x(1000x0.003822
)/2
=0.005116
Where Uw = Ws / Awρ
=0.0354/0.00596x1000
=0.00593
Geometric Mean velocity Uz = √UwUs
= √0.00593x0.00246
=0.0038
Aw = (π/4 x ID2
x Ra) – (Nw x π/4 x OD2
)
=(π/4x0.22
x0.19)-(2.52xπ/4x0.019242
)
=0.0059
Nwv = Hb/ P't
=0.036/0.03
=0.833
End Zone
ΔPe = ΔPi [(Nwv + Ncv/ Ncv)] F 'b
=0.6136(0.833+3.38/3.38)x0.04255
=0.03254
Total shell –side pressure drop
ΔPs = 2ΔPe + ΔPc( Nb – 1) + Nb ΔPw
=2x0.03254+0.00736(4-1)+4x0.005116
ΔPs =0.1074
6.5 Calculation of Shell Side Pressure Drop Using Bell
Delaware Method:
STEP 1: Calculate the number of tube rows crossed in one
crossflow section Nc.
Nc = (Ds /Ptp)*[1 – {(2*Lc)/Ds}]
Nc = (.2 /.02598)*[1 – {(2*.05)/.2}]
Nc = 3.85 = 4
Where, Ptp = 0.866*Pt
Ptp = 0.866*.03
Ptp = 0.02598
STEP 2: Calculate the ideal cross flow pressure drop through
one baffle space ΔPb.
ΔPb = [(2*fs*ms
2
*Nc) / (ρs*sm
2
)]* [(μs / μw)^0.14]
ΔPb = [(2*.000125*.03542
*4) / (1000*.0172
)]* [(.00088/
.00088) ^0.14]
ΔPb = 4.33*10-6
Pa
STEP 3: Calculate the window flow area Sw.
Sw=(Ds
2
/4)*[cos-1
Ө-{Ө*√(1-Ө2
)}]-[(Nt/8)*(1-Fc)*π* Do
2
]
Sw=(.22
/4)*[cos-1
.581-{.581*√(1-.5812
)}]-[(18/8)*(1-.695)*π*
.019242
]
Sw=0.004 m2
STEP 4: Calculate the number of effective cross flow rows in
window zone Ncw.
Ncw = (0.8*Lc) / Ptp
Ncw = (0.8*.05) / .02598
Ncw = 1.54
STEP 5: Calculate the window zone pressure drop ΔPw.
ΔPw = [{(26 μs ms) /( ρs√( Sm Sw)}*{(Ncw /( Pt - Do)) + (
Lb/Dw
2
)}]+[ ms
2
/ (2 ρs Sm Sw)]
ΔPw = [{(26* .00088* .0354) /( 1000*√( .017* .004)}*{(1.54 /(
.03- .01924)) + ( .2/.0222
)}]+[ .03542
/ (2*1000*.017* .004)]
ΔPw = 0.0638 Pa
STEP 6: Estimate the correction factor on pressure drop for
bypass flow Rb.
The value of Rb can be obtained from the fig 2.39 of wolverine
tube heat transfer data book for the corresponding value of Fbp.
Rb = 0.78
STEP 7: Estimate the correction factor for baffle leakage effect
on pressure drop RL
The value of RL can be obtained from the fig 2.38 of wolverine
tube heat transfer data book for the corresponding value
obtained in step 12 above.
RL = 0.78
STEP 8: Calculate the total pressure drop across shell ΔPs
ΔPS= [{(Nb- 1)*ΔPb*Rb} + (Nb*ΔPw)]*RL + [2*ΔPb*Rb*{1+
(Ncw/Nc)}]
ΔPS= [{(4- 1)* 4.33*10-6
*.78} + (4*0.0638)]*.78 + [2*4.33*10-
6
*.78*{1+ (1.54/4}]
ΔPS= 0.278 Pa
8. IJRET: International Journal of Research in Engineering and Technology eISSN: 2319-1163 | pISSN: 2321-7308
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Volume: 03 Special Issue: 03 | May-2014 | NCRIET-2014, Available @ http://www.ijret.org 493
6.6 Calculation of Tube Side Heat Transfer Coefficient
using Gnielinski Correlation:
At = {(π* Di
2
) / 4}*(Nt / 2)
= {(π*0.0162
)/4}*(18/2)
= 0.00180 m2
Gt = mt / At
= 0.0291/0.00180
= 16.17 Kg/m sec
Ut = Gt / ρt
= 16.17/1000
= 0.01617 m/sec
Res = (Gt* Di) / μt
= (16.17*0.016)/0.00086
=300.83
Prt = (Cpt*μt) / Kt
= (4.187*0.00086)/0.00098
= 3.67
f = {(1.58*Ln Ret) – 3.28} ^ (-2)
= {(1.58*Ln 300.83)-3.28}^(-2)
= 0.0304
Nut = {(f /2)*(Ret -1000)* Prt} / {1+(12.7*√ (f /2)*(Prt ^ (2/3))-
1)}
={(0.0304/2)*(300.83-1000)*3.67]/{1+(12.7*√
(0.0304/2)*(3.672/3
- 1)}
=-12.4
hi = (Nut * Kt) / Di
= (-12.4*0.00098)/0.016
hi = -0.78 W/m2 0
K
6.7 Calculation of Tube Side Pressure Drop:
ΔPt = [{(4* f* Lt* np) / Di} + (4* np)]*[(ρt*Ut
2
) / 2]
=[{(4*0.0304*0.825*2)/0.016}+(4*2)]*[(1000*0.016172
)/2]
= 2.685Pa
.008782
) / 2]
ΔPt =2.685Pa
7. RESULTS AND DISCUSSION
Shell side results for four sample readings are shown below
Shell side (Cold Water) R1 R2 R3 R4
1 Mass flow rate (Kg/sec) 0.0257 0.0299 0.035 0.0397
2 Temperature at inlet (o
c) 29.7 30.1 30.6 31.2
3 Temperature at outlet (o
c) 32.2 33 33.5 33.9
4 Reynolds number (Kern Method) 66.93 76.45 91.12 102.4
5 Reynolds number (Bell Method) 35.53 45.28 53.97 60.68
6 Reynolds number (Bell Delaware Method) 32.96 38.346 44.887 50.915
7 Prandtl number 3.76 3.76 3.76 3.76
8
Heat transfer coefficient (W/ m2
’K). (Kern
Method)
0.17 0.183 0.201 0.214
9
Heat transfer coefficient (W/ m2
’K).(Bell
Method)
0.162 0.231 0.271 0.296
10
Heat transfer coefficient (W/ m2
’K).(Bell
Delaware method)
0.286 0.302 0.32 0.336
11 Pressure drop (Pa) ( Kern Method)
0.032 0.041 0.056 0.069
12 Pressure drop (Pa) Bell Method) 0.065 0.084 0.1075 0.109
13 Pressure drop (Pa Bell Delaware method)) 0.169 0.215 0.278 0.343
9. IJRET: International Journal of Research in Engineering and Technology eISSN: 2319-1163 | pISSN: 2321-7308
__________________________________________________________________________________________
Volume: 03 Special Issue: 03 | May-2014 | NCRIET-2014, Available @ http://www.ijret.org 494
Tube side results for four sample readings are shown below
8. GRAPHS
Fig a. Comparison of Variation of Reynold’s number w.r.t
Flow rate on the Shell side using three methods
Fig b. Comparison of Variation of Heat Transfer Coefficient
w.r.t Flow rate on the Shell side using three methods
Fig c. Comparison of Variation of Pressuer drop w.r.t Flow rate
on the Shell side using the three methods
Fig d. Variation of Reynold’s number w.r.t Flow rate on the
Tube side
Sl.no Tube side Result 1 Result 2 Result 3 Result 4
1 Mass flow rate (Kg/sec), Mt 0.020 0.0231 0.0291 0.0364
2 Temperature at inlet (o
c), Thi 49.8 52.6 54.4 54.8
3 Temperature at outlet (o
c), Tho 34.9 34.7 34.6 34.5
4 Reynolds number, Ret 206.718 238.76 300.775 376.227
5 Prandtl number, Prt 3.674 3.674 3.674 3.674
6 Heat transfer coefficient (W/
m2
’K), hi
-1.106 -1.002 -0.842 -0.693
7 Pressure drop (Pa), ΔPa 1.456 1.836 2.684 3.91
10. IJRET: International Journal of Research in Engineering and Technology eISSN: 2319-1163 | pISSN: 2321-7308
__________________________________________________________________________________________
Volume: 03 Special Issue: 03 | May-2014 | NCRIET-2014, Available @ http://www.ijret.org 495
Fig e. Variation of Heat Transfer Coefficient w.r.t Flow rate on
the Tube side
Fig f. Variation of Pressure drop w.r.t Flow rate on the Tube
side.
9. CONCLUSIONS
The shell and tube heat exchanger is analyzed using Kern, Bell
and Bell Delaware methods and heat transfer coeffient,
Reynold’s number, pressure drops are calculated for various
mass flow rates and the results are shown in the graphs above.
We found that, shell side heat transfer coefficient increases with
increasing mass flow rate in all the three methods, but the heat
transfer given by Bell Delaware method is much more than the
other two methods. Also the shell side pressure increase rapidly
with increasing flow rate and this increase is again more in Bell
Delaware method as compared to others.
Since in a baffled heat exchanger, there is a obstruction to flow,
drop in the pressure is definitely more when compared to the
heat exchanger without baffles. Kern method does not take in to
consideration the obstructions due to baffles in calculating the
pressure drops and hence the pressure drop given by Kern
method is unrealistic. Whereas, the pressure drops given by Bell
and Bell Delaware methods, is more realistic, since these
methods consider pressure drop due to bypass and leakage
streams caused by the baffles in the heat exchanger.
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11. IJRET: International Journal of Research in Engineering and Technology eISSN: 2319-1163 | pISSN: 2321-7308
__________________________________________________________________________________________
Volume: 03 Special Issue: 03 | May-2014 | NCRIET-2014, Available @ http://www.ijret.org 496
exchangers,Department of Chemical Engineering, Birla Institute
of Technology and Science (BITS), Pilani
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