The pipe support consists of a pipe transition member welded into a vertical piping run to provide support. The transition member has the same inside diameter as the piping but its outside diameter increases along its length to form a triangular cross-section, with a ledge at the widest point. Load-bearing insulation, clamps, and hanger rods connect to this ledge to transfer the piping load to constant support hangers while preventing thermal stresses on the piping.
This document provides an introduction to heat exchangers, including their classification, types, components, and design considerations. Heat exchangers transfer thermal energy between fluids or between fluids and solids. Common types include shell and tube, plate and frame, air cooled, and spiral designs. Key components of shell and tube heat exchangers are the shell, tubes, tubesheet, baffles, and nozzles. Tube layout, pitch, pass arrangements, and baffle design impact heat transfer and pressure drop. Bypass and leakage streams must be minimized for optimal performance.
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.
This document discusses heat exchangers, which allow the transfer of heat between two fluids without direct contact. It describes several types of heat exchangers including double pipe heat exchangers, which involve two concentric pipes, and shell and tube heat exchangers, which involve tubes inside a cylindrical shell. Shell and tube heat exchangers are widely used and involve tubes, tube sheets, baffles, and multiple passes to increase heat transfer. The document also discusses applications and advantages and disadvantages of different heat exchanger designs.
CFD Analysis of Heat Transfer Enhancement in Shell and Tube Type Heat Exchang...ijtsrd
Shell and Tube heat exchangers are having special importance in boilers, oil coolers, condensers, pre-heaters. Shell and Tube heat exchanger is one such heat exchanger, provides more area for heat transfer between two fluids in comparison with other type of heat exchanger. To intensify heat transfer with minimum pumping power innovative heat transfer fluids called Nano fluids have become the major area of research now a days. The primary aim is to evaluate the effect of different weight concentration and temperatures on convective heat transfer. Increasing the weight concentration and temperatures leads to enhancement of convective heat transfer coefficient. In the present, work attempts are made to enhance the heat transfer rate in shell and tube heat exchangers. A multi pass shell and tube heat exchanger with 3 tubes with fins modelling is done using ANSYS. Nanofluid such as Al2O3-H2O is used. The CFD simulated results achieved from the use of the creating fin in tube side in shell and tube type heat exchanger are compared with without fin. Based on the results, providing fins on tube causes the increment of overall heat transfer coefficient which results in the enhancement of heat transfer rate of heat exchanger. Sudhanshu Pathak | H. S. Sahu"CFD Analysis of Heat Transfer Enhancement in Shell and Tube Type Heat Exchanger creating Triangular Fin on the Tubes" Published in International Journal of Trend in Scientific Research and Development (ijtsrd), ISSN: 2456-6470, Volume-2 | Issue-4 , June 2018, URL: http://www.ijtsrd.com/papers/ijtsrd14259.pdf http://www.ijtsrd.com/engineering/mechanical-engineering/14259/cfd-analysis-of-heat-transfer-enhancement-in-shell-and-tube-type-heat-exchanger-creating-triangular-fin-on-the-tubes/sudhanshu-pathak
This document discusses various types of heat exchangers including shell-and-tube, double-pipe, plate-and-frame, fired heaters, and aerial coolers. It provides details on shell-and-tube exchangers including baffles, tube layout, and TEMA classifications. Examples are given for sizing problems including determining heat duty, selecting the exchanger type, and calculating the number of tubes needed. Common software for heat exchanger design is also listed.
A shell and tube heat exchanger consists of a shell with tubes inside it. One fluid runs through the tubes while another flows over the tubes on the shell side to transfer heat between the fluids. Common configurations include U-tubes and straight tubes arranged in single or multiple passes. Key factors that impact performance include the number of tube passes, baffle spacing, and fluid velocities, which influence heat transfer coefficients and pressure drops. Shell and tube exchangers are widely used in applications like engine cooling, boiler systems, and oil refineries due to their ability to handle higher pressures and temperatures.
This document provides information about heat exchangers, including:
- Heat exchangers transfer energy between fluids at different temperatures through conduction, convection and radiation.
- They have advantages like being economical, having high efficiency and being easy to modify.
- Heat exchangers can be classified by their flow configuration, transfer process, construction and heat transfer mechanism.
- Common types include shell and tube, plate, double pipe, and condensers, evaporators and boilers.
- Maintenance includes hydrotesting to detect leaks and plugging leaking tubes temporarily or permanently.
The document discusses heat exchangers and fouling factors. It describes how fouling decreases heat transfer over time by creating additional thermal resistance. Fouling depends on operating conditions like temperature and fluid velocities. The types of fouling include precipitation of solids, corrosion, chemicals, and biological growth. The document also summarizes methods for analyzing heat exchangers and factors to consider when selecting a heat exchanger, such as heat transfer rate, size, cost, pumping power requirements, and materials.
This document provides an introduction to heat exchangers, including their classification, types, components, and design considerations. Heat exchangers transfer thermal energy between fluids or between fluids and solids. Common types include shell and tube, plate and frame, air cooled, and spiral designs. Key components of shell and tube heat exchangers are the shell, tubes, tubesheet, baffles, and nozzles. Tube layout, pitch, pass arrangements, and baffle design impact heat transfer and pressure drop. Bypass and leakage streams must be minimized for optimal performance.
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.
This document discusses heat exchangers, which allow the transfer of heat between two fluids without direct contact. It describes several types of heat exchangers including double pipe heat exchangers, which involve two concentric pipes, and shell and tube heat exchangers, which involve tubes inside a cylindrical shell. Shell and tube heat exchangers are widely used and involve tubes, tube sheets, baffles, and multiple passes to increase heat transfer. The document also discusses applications and advantages and disadvantages of different heat exchanger designs.
CFD Analysis of Heat Transfer Enhancement in Shell and Tube Type Heat Exchang...ijtsrd
Shell and Tube heat exchangers are having special importance in boilers, oil coolers, condensers, pre-heaters. Shell and Tube heat exchanger is one such heat exchanger, provides more area for heat transfer between two fluids in comparison with other type of heat exchanger. To intensify heat transfer with minimum pumping power innovative heat transfer fluids called Nano fluids have become the major area of research now a days. The primary aim is to evaluate the effect of different weight concentration and temperatures on convective heat transfer. Increasing the weight concentration and temperatures leads to enhancement of convective heat transfer coefficient. In the present, work attempts are made to enhance the heat transfer rate in shell and tube heat exchangers. A multi pass shell and tube heat exchanger with 3 tubes with fins modelling is done using ANSYS. Nanofluid such as Al2O3-H2O is used. The CFD simulated results achieved from the use of the creating fin in tube side in shell and tube type heat exchanger are compared with without fin. Based on the results, providing fins on tube causes the increment of overall heat transfer coefficient which results in the enhancement of heat transfer rate of heat exchanger. Sudhanshu Pathak | H. S. Sahu"CFD Analysis of Heat Transfer Enhancement in Shell and Tube Type Heat Exchanger creating Triangular Fin on the Tubes" Published in International Journal of Trend in Scientific Research and Development (ijtsrd), ISSN: 2456-6470, Volume-2 | Issue-4 , June 2018, URL: http://www.ijtsrd.com/papers/ijtsrd14259.pdf http://www.ijtsrd.com/engineering/mechanical-engineering/14259/cfd-analysis-of-heat-transfer-enhancement-in-shell-and-tube-type-heat-exchanger-creating-triangular-fin-on-the-tubes/sudhanshu-pathak
This document discusses various types of heat exchangers including shell-and-tube, double-pipe, plate-and-frame, fired heaters, and aerial coolers. It provides details on shell-and-tube exchangers including baffles, tube layout, and TEMA classifications. Examples are given for sizing problems including determining heat duty, selecting the exchanger type, and calculating the number of tubes needed. Common software for heat exchanger design is also listed.
A shell and tube heat exchanger consists of a shell with tubes inside it. One fluid runs through the tubes while another flows over the tubes on the shell side to transfer heat between the fluids. Common configurations include U-tubes and straight tubes arranged in single or multiple passes. Key factors that impact performance include the number of tube passes, baffle spacing, and fluid velocities, which influence heat transfer coefficients and pressure drops. Shell and tube exchangers are widely used in applications like engine cooling, boiler systems, and oil refineries due to their ability to handle higher pressures and temperatures.
This document provides information about heat exchangers, including:
- Heat exchangers transfer energy between fluids at different temperatures through conduction, convection and radiation.
- They have advantages like being economical, having high efficiency and being easy to modify.
- Heat exchangers can be classified by their flow configuration, transfer process, construction and heat transfer mechanism.
- Common types include shell and tube, plate, double pipe, and condensers, evaporators and boilers.
- Maintenance includes hydrotesting to detect leaks and plugging leaking tubes temporarily or permanently.
The document discusses heat exchangers and fouling factors. It describes how fouling decreases heat transfer over time by creating additional thermal resistance. Fouling depends on operating conditions like temperature and fluid velocities. The types of fouling include precipitation of solids, corrosion, chemicals, and biological growth. The document also summarizes methods for analyzing heat exchangers and factors to consider when selecting a heat exchanger, such as heat transfer rate, size, cost, pumping power requirements, and materials.
Heat exchangers transfer heat from one medium to another. They are classified by flow configuration and construction. Key flow configurations are parallel, counter, and cross flow. Main construction types are shell and tube, and plate heat exchangers. Heat transfer is calculated using methods like log mean temperature difference (LMTD) and number of transfer units (NTU). Standards like TEMA provide guidelines for shell and tube heat exchanger design and components.
The document discusses different types of heat exchangers. It begins by defining a heat exchanger as a device that transfers heat between fluids, which may flow separately with a dividing wall or mix directly. Heat exchangers are widely used in applications like heating, cooling and industrial processes. The document then classifies heat exchangers based on the heat exchange process, relative fluid flow directions, mechanical design of the heat exchange surface, and physical states of the fluids. Specific heat exchanger types discussed include direct contact, regenerative, recuperative, parallel flow, counter flow, shell and tube, evaporator and condenser.
Heat exchangers transfer heat from one fluid to another. There are two main types: tube-and-shell and plate. Tube-and-shell consists of tubes in a shell where fluids flow inside and outside the tubes. Plate heat exchangers use plates to separate fluids which flow between plates in alternating channels. Heat exchangers can operate in parallel, counter, or cross flow configurations. Performance tests determine the overall heat transfer coefficient and identify any fouling issues.
This document provides an overview of heat transfer principles and their application to the design of heat exchangers. It discusses the three main modes of heat transfer (conduction, convection, and radiation) and introduces concepts like heat transfer coefficients. Design considerations for shell and tube heat exchangers are covered, including sizing standards, tube/shell geometry, baffling, and hydraulic performance. Methods for designing single-phase and multiphase exchangers are presented, such as Kern's method and Bell's method. The document concludes with brief discussions on condenser, reboiler, and air cooler design.
• Types of heat exchangers
• Classification of heat exchangers
• components of heat exchanger
• Materials of heat exchanger
• troubleshooting of heat exchanger
This presentation contains basic principles of heat exchangers, Flow pattern, types of heat exchangers, selection criteria for heat exchangers, TEMA standars for heat exchangers design
A heat exchanger transfers heat between two fluids or a fluid and a surface. It can be classified based on transfer processes, number of fluids, construction, heat transfer mechanisms, compactness, flow arrangement, number of passes, and surface type. Recuperators and regenerators are types of surface heat exchangers that transfer heat via convection between fluids separated by a thin wall. Direct contact heat exchangers transfer heat by partially or completely mixing hot and cold fluid streams. Standards from the Tubular Exchanger Manufacturers Association classify heat exchangers by size, denoted by shell diameter and tube length, and type, denoted by stationary head, shell, and rear head configuration.
This document provides an overview of a gasketed plate heat exchanger. It describes the construction of a plate heat exchanger using metal plates and gaskets to transfer heat between two fluids without mixing. It discusses key design considerations like flow pattern, plate materials, mean flow gap, heat transfer coefficient, pressure drop, and heat transfer area. The document highlights advantages of plate heat exchangers like minimizing leakage risk, flexibility in design, efficient heat transfer due to turbulence, compact size, and low fouling characteristics.
Liquid Piping Systems, Minor Losses: Fittings and Valves in Liquid Piping Systems, Sizing Liquid Piping Systems; Fluid Machines (Pumps) and Pump–Pipe Matching, Design of Piping Systems complete with In-Line or Base-Mounted Pumps
REDESIGN OF SHELL AND TUBE HEAT EXCHANGER 1Sanju Jacob
The document discusses redesigning a shell and tube heat exchanger to increase its effectiveness. It analyzes increasing the number of tubes from 184 to 234. This results in the effectiveness increasing from 5.77 to 8.80, an improvement of 34.4%. Key components of shell and tube heat exchangers like shells, tubes, and baffles are also outlined. The redesign aims to accommodate a 65% increase in thermal load for a chemical process.
This presentation will gave an Basic idea about Pipe stress analysis, why pipe stress analysis need to perform and Having small introduction to CAESAR II Software.
This document provides an overview and classification of different types of heat exchangers. It begins by defining heat exchangers and their basic functions. It then describes various classification schemes for heat exchangers, including by transfer process (direct vs indirect contact), number of fluids, construction features, flow arrangements, and heat transfer mechanisms. The document focuses on describing indirect-contact heat exchangers, and classifies them as direct-transfer, storage, or fluidized-bed types. It provides examples of different heat exchanger configurations.
Heat exchangers transfer heat from one fluid to another without direct contact between the fluids. The most common type is the shell-and-tube heat exchanger, which consists of tubes in a shell container. Fluids flow inside the tubes and outside in the shell. Other key types include double-pipe exchangers, plate-and-frame exchangers, air-cooled exchangers, and spiral exchangers. Spiral exchangers have two fluids spiraling in opposite directions to enhance heat transfer.
A heat exchanger transfers heat between two fluids through conduction. It can transfer heat between fluids that never mix by using a solid wall, or between directly contacted fluids. Heat exchangers are widely used in applications like HVAC, power plants, refineries, and manufacturing. They are classified based on construction and flow configuration, with shell-and-tube and plate heat exchangers being most common. Proper design considers factors like heat transfer rate, pressure drop, fouling, and effectiveness.
The document discusses different types of heat exchangers including regenerative heat exchangers, plate heat exchangers, and shell and tube heat exchangers. Heat exchangers can be classified based on connecting technique, number of fluids, degree of surface compactness, construction, and flow arrangements such as counter flow, parallel flow, and cross flow. Shell and tube heat exchangers are commonly used in oil refineries and large chemical processes due to their ability to handle higher pressures. They consist of tubes, a shell, baffles, and may vary based on tube characteristics like shape, number, length, diameter, and thickness or the material used for the shell.
This document discusses the process design of shell and tube heat exchangers. It begins by classifying heat exchangers and describing different types of shell and tube heat exchangers such as fixed tube sheet, removable tube bundle, floating head, and U-tube designs. The document then discusses various thermal design considerations for shell and tube heat exchangers, including selections for the shell, tube materials and dimensions, tube layout and count, baffles, and fouling factors. It provides process design procedures and an example problem for designing shell and tube heat exchangers.
This document discusses shell and tube heat exchangers, including their components, types, and how they work. It also covers LMTD correction factors for multiple pass exchangers, extended surface heat exchangers using fins, and definitions of fin efficiency and effectiveness. Specifically, it defines a shell and tube heat exchanger as consisting of tubes inside a shell to transfer heat between two fluids without mixing. It also describes common types like U-tube, straight single-pass, and straight double-pass designs.
This document describes a heat exchanger design project. It provides theory on heat exchanger design including heat transfer rate calculations. It then details the CFD simulation process used to model and analyze different heat exchanger designs. This included an initial 2D model, mesh refinement studies to determine optimal mesh size, and modeling variations in pipe spacing, flow direction, and a 3D design. Results were analyzed using temperature, turbulence, and velocity contours to evaluate design performance.
The drainage plan shows the layout of pipes and manholes (FMs) for draining a science building addition. Soil pipes from the building drop down into a new manhole (FM3). A 110mm cast iron soil pipe runs along the underside of the first floor and into FM3. Rainwater pipes also drain into FM3. From FM3, foul water is drained through existing pipes. New manholes will be dug to connect to the existing drainage system and match the depths of existing falls. The surrounding area will be tarmaced.
This document provides details of a latrine and bathroom block project for a village in Panvel, including a schematic diagram, location information, bill of materials, estimated costs, and specifications. The project involves constructing two 4' x 4' x 8' latrine blocks and two 4' x 4' x 8' bathroom blocks with materials like FRP doors and frames, bison board walls, water tanks, toilets, taps, pipes, tiles, and other bathroom accessories. The total estimated cost for the project is Rs. 1,02,625.
Heat exchangers transfer heat from one medium to another. They are classified by flow configuration and construction. Key flow configurations are parallel, counter, and cross flow. Main construction types are shell and tube, and plate heat exchangers. Heat transfer is calculated using methods like log mean temperature difference (LMTD) and number of transfer units (NTU). Standards like TEMA provide guidelines for shell and tube heat exchanger design and components.
The document discusses different types of heat exchangers. It begins by defining a heat exchanger as a device that transfers heat between fluids, which may flow separately with a dividing wall or mix directly. Heat exchangers are widely used in applications like heating, cooling and industrial processes. The document then classifies heat exchangers based on the heat exchange process, relative fluid flow directions, mechanical design of the heat exchange surface, and physical states of the fluids. Specific heat exchanger types discussed include direct contact, regenerative, recuperative, parallel flow, counter flow, shell and tube, evaporator and condenser.
Heat exchangers transfer heat from one fluid to another. There are two main types: tube-and-shell and plate. Tube-and-shell consists of tubes in a shell where fluids flow inside and outside the tubes. Plate heat exchangers use plates to separate fluids which flow between plates in alternating channels. Heat exchangers can operate in parallel, counter, or cross flow configurations. Performance tests determine the overall heat transfer coefficient and identify any fouling issues.
This document provides an overview of heat transfer principles and their application to the design of heat exchangers. It discusses the three main modes of heat transfer (conduction, convection, and radiation) and introduces concepts like heat transfer coefficients. Design considerations for shell and tube heat exchangers are covered, including sizing standards, tube/shell geometry, baffling, and hydraulic performance. Methods for designing single-phase and multiphase exchangers are presented, such as Kern's method and Bell's method. The document concludes with brief discussions on condenser, reboiler, and air cooler design.
• Types of heat exchangers
• Classification of heat exchangers
• components of heat exchanger
• Materials of heat exchanger
• troubleshooting of heat exchanger
This presentation contains basic principles of heat exchangers, Flow pattern, types of heat exchangers, selection criteria for heat exchangers, TEMA standars for heat exchangers design
A heat exchanger transfers heat between two fluids or a fluid and a surface. It can be classified based on transfer processes, number of fluids, construction, heat transfer mechanisms, compactness, flow arrangement, number of passes, and surface type. Recuperators and regenerators are types of surface heat exchangers that transfer heat via convection between fluids separated by a thin wall. Direct contact heat exchangers transfer heat by partially or completely mixing hot and cold fluid streams. Standards from the Tubular Exchanger Manufacturers Association classify heat exchangers by size, denoted by shell diameter and tube length, and type, denoted by stationary head, shell, and rear head configuration.
This document provides an overview of a gasketed plate heat exchanger. It describes the construction of a plate heat exchanger using metal plates and gaskets to transfer heat between two fluids without mixing. It discusses key design considerations like flow pattern, plate materials, mean flow gap, heat transfer coefficient, pressure drop, and heat transfer area. The document highlights advantages of plate heat exchangers like minimizing leakage risk, flexibility in design, efficient heat transfer due to turbulence, compact size, and low fouling characteristics.
Liquid Piping Systems, Minor Losses: Fittings and Valves in Liquid Piping Systems, Sizing Liquid Piping Systems; Fluid Machines (Pumps) and Pump–Pipe Matching, Design of Piping Systems complete with In-Line or Base-Mounted Pumps
REDESIGN OF SHELL AND TUBE HEAT EXCHANGER 1Sanju Jacob
The document discusses redesigning a shell and tube heat exchanger to increase its effectiveness. It analyzes increasing the number of tubes from 184 to 234. This results in the effectiveness increasing from 5.77 to 8.80, an improvement of 34.4%. Key components of shell and tube heat exchangers like shells, tubes, and baffles are also outlined. The redesign aims to accommodate a 65% increase in thermal load for a chemical process.
This presentation will gave an Basic idea about Pipe stress analysis, why pipe stress analysis need to perform and Having small introduction to CAESAR II Software.
This document provides an overview and classification of different types of heat exchangers. It begins by defining heat exchangers and their basic functions. It then describes various classification schemes for heat exchangers, including by transfer process (direct vs indirect contact), number of fluids, construction features, flow arrangements, and heat transfer mechanisms. The document focuses on describing indirect-contact heat exchangers, and classifies them as direct-transfer, storage, or fluidized-bed types. It provides examples of different heat exchanger configurations.
Heat exchangers transfer heat from one fluid to another without direct contact between the fluids. The most common type is the shell-and-tube heat exchanger, which consists of tubes in a shell container. Fluids flow inside the tubes and outside in the shell. Other key types include double-pipe exchangers, plate-and-frame exchangers, air-cooled exchangers, and spiral exchangers. Spiral exchangers have two fluids spiraling in opposite directions to enhance heat transfer.
A heat exchanger transfers heat between two fluids through conduction. It can transfer heat between fluids that never mix by using a solid wall, or between directly contacted fluids. Heat exchangers are widely used in applications like HVAC, power plants, refineries, and manufacturing. They are classified based on construction and flow configuration, with shell-and-tube and plate heat exchangers being most common. Proper design considers factors like heat transfer rate, pressure drop, fouling, and effectiveness.
The document discusses different types of heat exchangers including regenerative heat exchangers, plate heat exchangers, and shell and tube heat exchangers. Heat exchangers can be classified based on connecting technique, number of fluids, degree of surface compactness, construction, and flow arrangements such as counter flow, parallel flow, and cross flow. Shell and tube heat exchangers are commonly used in oil refineries and large chemical processes due to their ability to handle higher pressures. They consist of tubes, a shell, baffles, and may vary based on tube characteristics like shape, number, length, diameter, and thickness or the material used for the shell.
This document discusses the process design of shell and tube heat exchangers. It begins by classifying heat exchangers and describing different types of shell and tube heat exchangers such as fixed tube sheet, removable tube bundle, floating head, and U-tube designs. The document then discusses various thermal design considerations for shell and tube heat exchangers, including selections for the shell, tube materials and dimensions, tube layout and count, baffles, and fouling factors. It provides process design procedures and an example problem for designing shell and tube heat exchangers.
This document discusses shell and tube heat exchangers, including their components, types, and how they work. It also covers LMTD correction factors for multiple pass exchangers, extended surface heat exchangers using fins, and definitions of fin efficiency and effectiveness. Specifically, it defines a shell and tube heat exchanger as consisting of tubes inside a shell to transfer heat between two fluids without mixing. It also describes common types like U-tube, straight single-pass, and straight double-pass designs.
This document describes a heat exchanger design project. It provides theory on heat exchanger design including heat transfer rate calculations. It then details the CFD simulation process used to model and analyze different heat exchanger designs. This included an initial 2D model, mesh refinement studies to determine optimal mesh size, and modeling variations in pipe spacing, flow direction, and a 3D design. Results were analyzed using temperature, turbulence, and velocity contours to evaluate design performance.
The drainage plan shows the layout of pipes and manholes (FMs) for draining a science building addition. Soil pipes from the building drop down into a new manhole (FM3). A 110mm cast iron soil pipe runs along the underside of the first floor and into FM3. Rainwater pipes also drain into FM3. From FM3, foul water is drained through existing pipes. New manholes will be dug to connect to the existing drainage system and match the depths of existing falls. The surrounding area will be tarmaced.
This document provides details of a latrine and bathroom block project for a village in Panvel, including a schematic diagram, location information, bill of materials, estimated costs, and specifications. The project involves constructing two 4' x 4' x 8' latrine blocks and two 4' x 4' x 8' bathroom blocks with materials like FRP doors and frames, bison board walls, water tanks, toilets, taps, pipes, tiles, and other bathroom accessories. The total estimated cost for the project is Rs. 1,02,625.
In-Place Pipe Support Load Testing and Hanger Surveys_Part of a Best in Class...Britt Bettell
- A best-in-class piping fitness-for-service program involves regular visual inspections of pipe supports and hangers, as well as in-situ load testing of suspect supports to determine actual load values.
- In-situ load testing uses hydraulic tools to unload pipe hangers without disconnecting them from piping, allowing testing of critical online systems. It measures the actual load a hanger is supporting.
- Proper pipe support maintenance and load testing is important for the safe and reliable operation of piping systems, as required by various codes and standards, especially for high-risk creep-exposed lines. Load test data improves the accuracy of creep stress analyses.
This document contains diagrams and drawings of a residential drainage system. It includes:
1) Multiple views showing the layout of pipes for the main water supply, distributing water throughout the home, and removing waste water.
2) A legend defining the different pipe types.
3) Details of the connections between pipes, chambers, tanks, and other system components.
This document provides information about connecting fire trucks to hydrants and the location of necessary equipment. It discusses the types of trucks that most commonly need hydrant connections, the components of a hydrant bag and their uses. Specific compartments on Engine 28, Engine 30 and Tower 3 are highlighted that contain the hydrant bags, steamer adapters and basic hand tools like halligans and axes. Members are reminded to know where all equipment is located on all trucks.
This document discusses hydrant flushing programs. It explains that flushing programs help maintain water quality by removing sediment, restoring chlorine residuals, and preventing issues like nitrification. The document outlines a four-step approach to flushing programs: determining if flushing is needed, planning the program, collecting data during flushing, and evaluating the results. It also describes different flushing methods like conventional, unidirectional, and continuous blow-off flushing and considerations for implementing an effective flushing program.
ベトナムの展示会運営会社C.I.S Vietnam Advertising & Exhibition JSCが、ベトナム商工省傘下のIndustry Policy & Strategy Institute(工業政策戦略研究院)及びVietnam Society of Automotive Engineers(ベトナム自動車技術会)と共催して、第13回目の自動車、オートバイ、部品、アクセサリー、整備サービス、修理器具に関する展示会International Exhibition on Automobile and Supporting Industries 2016(Vietnam Auto Expo 2016、ベトナム・オート・エキスポ2016)を、2016年6月8日(水)~6月11日(土)、Hanoi(ハノイ)のHanoi International Center for Exhibition (ICE、ハノイ国際展示センター)で開催します。
2015年6月17日(水)~20日(土)の4日間開催されたVietnam Auto Expo 2015には、会場Vietnam Exhibition and Fair Centre(ベトナム・エキシビション・アンド・フェア・センター)9,000平方メートルのスペースに142社・団体以上が出展し、来場者数は72,000人でした。出展者の13%が乗用車、40%がバス・トラック・特殊車両、22%がオートバイ・スクーター、17%がパーツ・アクセサリーなど関連商品、8%が整備やメンテンナスなどサービスを展示しました。
Vietnam Automobile Manufactures Association(VAMA、ベトナム自動車工業会)によると、2014年の新車販売台数は前年比38.2%増の133,588台、2015年10月までは、前年比52.7.%増の185,811台と好調です。
一方、国内の完成車生産や自動車部品の現地生産の情勢は、2018年以降、大きく変貌しそうです。ベトナムは自動車産業保護のため、ASEAN(東南アジア諸国連合)域内からの完成車輸入の関税は60%ですが、ASEAN物品貿易協定に基づき、この高い輸入関税は2018年までに撤廃される見込みです。この結果、タイやインドネシアからの輸入車が増加し、国内の完成車生産は減少するとの観測があります。
本展示会の御出展は、ベトナム、特にハノイの自動車・オートバイ・関連商品及びアフターマーケットにご興味のある企業様にとって、貴社製品やサービスに関心のある企業経営者や輸入代理店と出会い、ネットワークを拡げる良い機会となります。
This document provides guidelines for typical hanger spacing and rod diameters for horizontal steel, PVC, and copper piping based on nominal pipe size. It lists the maximum recommended spacing for different pipe materials and sizes, ranging from 3/8-inch to 16-inch nominal pipe. Common hanger types are also illustrated, including clevis hangers for 1/2-30 inch pipe and pipe clamps for 1/2-36 inch pipe. The information is intended as a reference for proper pipe support and not as a performance guarantee, and all local codes must be followed.
Intellectual Property Rights and Access to
Essential Medicines
Thomas Pogge
Professor of Political Science, Columbia University
Centre for Applied Philosophy and Public Ethics, Australian National University
Centre for the Study of Mind in Nature, University of Oslo
This document provides details for insulating pipe systems. It specifies using mineral fiber insulation conforming to ASTM C 547 Class 1, with a factory applied FSK/kraft paper laminate jacket. The insulation will be used on cold water, hot water, and chilled water pipes as described. Half wood sections will be inserted into the insulation and taped with FSK tape to maintain the vapor barrier. 360 degree type 40 pipe protection shields 12 inches long will be used, along with U-bolt or hanger supports conforming to MSS SP 58-69 Type 24 standards.
Fire hydrants have several key components and uses. The upper section includes outlets that connect to hoses for firefighting. The lower section connects to water mains and contains a main valve. There are different types of hydrants like dry barrel for freezing climates and wet barrel that are always full of water. Proper installation is important, making sure the hydrant has good footing and drainage, is visible to crews, and can be easily accessed and operated during an emergency. Routine maintenance like inspections helps ensure hydrants remain functional.
This document discusses various aspects of designing and installing subsoil drainage systems. It provides guidance on determining pipe sizing and placement, choosing the proper filter material, and common installation mistakes to avoid. Key points covered include designing the system from the discharge point upward with uniform fall, using washed sand rather than gravel as the filter material to prevent particle migration, and ensuring proper trench grading and slope.
20100514 pipe arch presentation to iem may 2010forcepraxeum
This presentation provides information on the construction of a pipe arch tunnel project in Malaysia. It discusses the general project details including the tunnel length and location crossing a highway. It then summarizes the chronology of construction including building a triple cell drainage culvert, demolishing an existing box culvert, and constructing the twin pipe arch tunnels under the highway. The presentation describes the pipe arch tunnel concept and construction steps. It also details a catastrophe that occurred during construction where a damaged section of pipe had to be retrieved.
This presentation will give you an introduction to Pipe Shields, Inc. and its unique line of pre-insulated pipe supports, slides, guides and anchors that it developed and patented over its 40 year history. It will cover various designs, commercial applications (chilled and heated water lines, HVAC systems and low pressure steam lines), installation and maintenance procedures and the benefits of using pre-insulated pipe supports (vs. doing insulation in the field). This presentation will be delivered by Albert Dizon, General Manager of Pipe Shields, who has been working with pre-insulated pipe supports for 30+ years. Join us and receive some of his experience and wisdom!
The document is about a webinar on pipe support field inspection, installation, and maintenance presented by Jerry Godinaer. It provides information on inspecting, installing, and maintaining different types of pipe supports including variable and constant spring hangers, restraint devices, pipe shoes, slide plates, and hardware components. It discusses guidelines for on-site surveys, what to inspect for existing supports, and criteria for adjusting or replacing supports if needed.
This document provides guidelines for supporting piping systems that use flexible grooved couplings. It discusses the differences between supporting rigid versus flexible coupling systems. For flexible systems that allow movement, it recommends maximum hanger spacing distances between supports for various pipe sizes and whether full linear movement is or is not required. No pipe section should be left unsupported between any two couplings. Supports should be attached to adjoining pipes and equipment only, not directly to the couplings.
Ms for-mechanical-piping-system-installation-workthanhuce
This document provides a method statement for installing mechanical piping at the Saigon M&C Tower Project. It describes the installation of various pipe materials, including PPR, uPVC, cast iron, ductile iron, and steel pipes. For PPR pipe installation specifically, it details the adhesive bonding joint process of cutting, heating, joining, and welding pipes and fittings. It also provides guidance on installing exposed and concealed PPR pipes.
The document discusses sanitary piping systems. It describes the main components of a piping system including main pipes, feeder pipes, branch pipes, and valves. It also discusses factors that cause head loss in pipes such as differences in pipe size, changes in flow direction, friction, and differences in gradient or level. Finally, it summarizes different types of sanitary discharge pipe systems including single stack, single pipe, and dual pipe systems.
This chapter discusses water supply systems used by firefighters. It covers the different types of water sources and supply systems, including underground piping and storage tanks. It also describes the valves used to control water flow and the different types of fire hydrants, their locations, and how to inspect and operate them. Alternative water supply methods for rural areas are discussed, such as water shuttles using portable tanks and relay pumping from nearby sources. The chapter emphasizes the importance of firefighters understanding local water supply systems and how to access water for firefighting.
This document provides guidance on designing pipe hangers and supports. It discusses determining hanger locations based on pipe size and configuration. It describes calculating hanger loads based on the weight of pipe, fittings, valves, and insulation. It also addresses calculating thermal movement of piping at hanger locations. The document provides information on selecting appropriate hangers based on the loads and movements, including spring hangers. It includes sample problems demonstrating how to apply the guidance. An extensive section lists the weights of common piping materials to aid in load calculations. The document is intended as a reference for engineers involved in pipe hanger and support design.
IRJET- Analysis of Shell and Tube Heat ExchangersIRJET Journal
The document analyzes the design and performance of shell and tube heat exchangers. It discusses the components of shell and tube heat exchangers including tubes, tube sheets, baffles, and nozzles. It also describes three common types of shell and tube exchangers: fixed tube sheet, U-tube, and floating head. The document then analyzes the performance of a shell and tube heat exchanger model made of brass with and without baffles using structural and thermal simulations. The results show that heat transfer rate and stresses are lower for the model with baffles compared to without baffles. Brass is also found to have lower stresses than other materials like carbon steel and stainless steel.
CONVECTIVE HEAT TRANSFER ANALYSIS IN A HELICAL COILIRJET Journal
This document describes an experimental study of convective heat transfer in a helical coil. The study involves fabricating a setup using a copper coil submerged in a water bath inside a cylindrical tank. Thermocouples are used to measure temperatures at different positions along the coil. Experiments are conducted for different heat input levels and fluid flow rates both with and without agitation. The results are used to calculate heat transfer coefficients, Nusselt number, Reynolds number, and overall heat transfer coefficient. The aim is to better understand the heat transfer process in helical coils and determine the fluid providing maximum heat transfer.
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.
Evaluation of Convective Heat Transfer Coefficient of Air Flowing Through an ...Bishal Bhandari
The document evaluates the convective heat transfer coefficient of air flowing through an inclined circular duct. It describes an experimental setup used to study the effect of inclination angle and air velocity on the convective heat transfer coefficient. Tests were conducted by forcing air through a copper duct at various angles (0°, 30°, 60°, 90°, 120°, 150°) and velocities while keeping heat input constant. Temperature readings were used to calculate parameters like Reynolds number, Nusselt number, and the convective heat transfer coefficient. Results showed that the heat transfer coefficient peaks at a 90° inclination for an air velocity of 12 m/s, and is lowest at a 30° inclination for a velocity of 8.38 m/s
Ijri te-03-011 performance testing of vortex tubes with variable parametersIjripublishers Ijri
Conventional refrigeration system is a type of refrigeration systems which are costly; noisy, harmful gases released from a machine based on application of this type of system and it is required more maintenance. So, we need to go for unconventional refrigeration systems like vortex tube refrigeration system, which produce less vibrations and which require less maintenance and which are noiseless. It is required for our mechanical engineers to look for enhancing the performance of such vortex tubes. So as a part of my project work, I have chosen various sizes of vortex tubes and test their performances for finding out optimum performance. We will be testing the performance of vortex tubes with different ‘l/d’ ratios and different cold fractions, with different pressures and different nozzle sizes.
Experimental Study and Investigation of Helical Pipe Heat Exchanger with Vary...IRJET Journal
The document describes an experimental study of a helical pipe heat exchanger with varying pitch. The study investigated how changing the pitch of the helical coil affected the heat exchanger's effectiveness. An experimental setup was designed and built with a helical copper coil inside a vessel to simulate the shell side. Experiments were conducted by varying the hot and cold water flow rates through the coil and shell, and effectiveness was calculated for different pitch values. Results showed that effectiveness decreased with increasing flow rates but remained over 30% even when flow rates doubled.
Analysis The Performance of Parallel Flow and Heat Transfer in Concentric Tub...IRJET Journal
This document summarizes a research project analyzing heat transfer performance in concentric tube heat exchangers using computational fluid dynamics (CFD). The research models a double tube parallel flow heat exchanger in SolidWorks and runs CFD simulations to analyze fluid flow and heat transfer under varying parameters. The research aims to better understand heat transfer processes when fluids flow in a double concentric tube heat exchanger. Key findings of previous studies on heat transfer enhancement techniques for heat exchangers are also reviewed.
IRJET- An Experimental Study of Pool Boiling Heat Transfer Enhancement in...IRJET Journal
This document summarizes an experimental study on enhancing pool boiling heat transfer in deionized water using additives. The study used an experimental apparatus consisting of a glass cylinder, heating elements, and instruments to measure temperature and power. Experiments were conducted by boiling various types of water (deionized, battery, borewell) in the cylinder and measuring their critical heat flux (CHF). CHF is the highest heat flux before a vapor film forms, isolating the heating surface from the liquid. The document reviews previous studies on subcooled flow boiling and CHF models. It was found that CHF increased with the use of additives in deionized water, allowing for more efficient heat transfer and operation at higher heat fluxes
This document provides an overview of a project to install an air cooler on an existing well head facility. It discusses the project scope, aims, and objectives which are to reduce costs by allowing gas transfer through carbon steel piping using an air cooler. It then describes research conducted on air coolers, the different types including shell and tube, plate, regenerative, and adiabatic wheel heat exchangers. Finally, it discusses wellheads, their main components such as the casing head, tubing head, and Christmas tree, and their functions in regulating extraction of hydrocarbons from underground formations.
Helically Coiled Tube with Different Geometry and Curvature Ratio on Convecti...AM Publications
A helically coil-tube heat exchanger is generally applied in industry applications due to its compact structure, larger heat transfer area and higher heat transfer capability. Several studies from literature have also indicated that heat transfer rate in helically coiled tube are superior to straight tube due to complex flow pattern exist inside helical pipe. The concept behind compact heat exchanger is to decrease size and increase heat load which is the typical feature of modern helical tube heat exchanger. While the heat transfer characteristics of helical coil heat exchangers are available in the literature, This paper elaborates a brief review on different curvature ratio and geometry of tubes in heat transfer through heat exchangers.
A report on Fast Breeder Test Reactor: Fast breeder reactors are the second stage of three-stage power program of India formulated by Homi Bhabha in 1950s. IGCAR is working with the mission of development of the technology of Sodium cooled fast reactors. Fast Breeder Test Reactor (FBTR) is a 40MW thermal, loop type, sodium cooled fast reactor.
IRJET- Heat Transfer Enhancement Analysis of Solar Parabolic Trough Collector...IRJET Journal
This document summarizes a study on enhancing heat transfer in the receiver tubes of parabolic trough solar collectors. The receiver tubes experience non-uniform heat flux around the periphery from the concentrated solar radiation, resulting in large temperature gradients. The study numerically simulates turbulent flow and heat transfer in receiver tubes with staggered pin fins on the inside surface. It is found that pin fins improve performance over a plain tube by increasing surface area and turbulence. Higher pin fins result in greater heat transfer but also higher pressure drop. The best performing design has pin fins 12mm in height, balancing increased heat transfer with pressure penalties.
This document describes an experiment on heat conduction using different specimen materials and shapes. Temperature data was collected as specimens cooled in air after being heated to an initial temperature in a water bath. The results were used to calculate dimensionless temperature, Fourier number, and Biot number to determine if the lumped capacitance method could be applied. For a stainless steel sphere specimen, the method yielded a heat transfer coefficient of 32.58 W/m2K, consistent with expected values. The experiment allowed students to analyze unsteady state heat transfer and compare heat transfer coefficients for different materials.
The document summarizes the fabrication and testing of a heat exchanger test rig. Key points:
- The test rig was designed and built to study a counter-flow tube heat exchanger using aluminum sheets and tubes.
- Finite element analysis was performed on the rig design to analyze stresses. Water was heated to 40°C and pumped through one side while tap water entered the other side.
- Effectiveness-NTU method was used to calculate theoretical outlet temperatures which were compared to experimental readings to determine error percentages.
A Review of Vortex Tube Refrigeration SystemIRJET Journal
The document discusses the vortex tube refrigeration system. It begins with an abstract that outlines how vortex tubes produce hot and cold air streams from compressed air without affecting the environment. It then reviews the literature on vortex tube design and operation. The key components of the vortex tube are described, including the nozzle, diaphragm, valve, hot and cold sides, and chamber. The document explains how compressed air is tangentially injected into the vortex chamber, creating swirling flows that split into hot and cold streams. It evaluates the advantages and disadvantages of vortex tube systems and their applications in areas requiring compact, reliable cooling like aircraft, spacesuits, and industrial processes.
International Journal of Engineering Research and Applications (IJERA) is an open access online peer reviewed international journal that publishes research and review articles in the fields of Computer Science, Neural Networks, Electrical Engineering, Software Engineering, Information Technology, Mechanical Engineering, Chemical Engineering, Plastic Engineering, Food Technology, Textile Engineering, Nano Technology & science, Power Electronics, Electronics & Communication Engineering, Computational mathematics, Image processing, Civil Engineering, Structural Engineering, Environmental Engineering, VLSI Testing & Low Power VLSI Design etc.
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.
Performance Analysis of Flat Plate Solar Water Collector using Different Shap...IRJET Journal
This document reviews research on improving the thermal efficiency of flat plate solar collectors by modifying design factors like the shape of riser tubes. It summarizes several studies that analyzed different riser tube shapes, including semicircular, triangular, accelerated, and dimpled tubes. The studies found that designs with better contact between the tubes and absorber plate, like triangular tubes, increased heat absorption and collector efficiency compared to traditional circular tubes. One study found an accelerated design with converging riser tubes improved absorbed heat by around 60% compared to a conventional collector. Overall, modifying the riser tube shape is a promising way to enhance flat plate collector performance.
IRJET-Experimental Study on Helical Tube Heat Exchanger by Varying Cross Sect...IRJET Journal
This document presents an experimental study on a helical tube heat exchanger. The study varies the cross-section of the tubes by adding nano particles like TiO2 and SiO2 to the working fluid. The performance of a helical coil heat exchanger is analyzed and compared to a straight tube heat exchanger based on parameters like log mean temperature difference (LMTD), heat transfer coefficient, and Reynolds number. The results show that a helical coil heat exchanger with nano particles added to the working fluid is more efficient, with its overall heat transfer coefficient increasing with mass flow rate.
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2 louis p. pollono - 4046169- pipe support for use in a nuclear system
1. United States Patent [19J
Pollono et al.
[54] PIPE SUPPORT FOR USE IN A NUCLEAR
SYSTEM
[75] Inventors: Louis P. Pollono; Raymond M. Mello,
both of Greensburg, Pa.
[73] Assignee: The United States of America as
represented by the United States
Energy Research and Development
Administration, Washington, D.C.
[21] Appl. No.: 594,477
[22] Filed: July 9, 1975
[51] Int. CJ.2 .......................... F16L 3/00; F21 L 17/02
[52] U.S. Cl. ...................................... 138/106; 248/58;
248/DIG. I; 248/54 R
[58] Field of Search ................. 138/106, 107, 99, 155,
138/177, 178; 248/54 CS, 54 R, 62, 59, 73,74
A, 74 B, DIG. I, 26, 58, 62, 71; 52/27, 32, 39;
165/67, 68; 122/510; 285/61, 62; 403/41;
211/29, 605, 69, 182, 107, 117
[56]
1,833,187
2,447,830
3,008,735
3,625,658
References Cited
U.S. PATENT DOCUMENTS
11/1931
8/1948
11/1961
12/1971
Stringer ............................. 285/61 X
Wood ................................. 248/54 R
Wijngaaren ....................... 248/58 X
Closon ....................... 248/DIG. I X
(II]
[45]
4,046,169
Sept. 6, 1977
Primary Examiner-Richard E. Aegerter
Assistant Examiner-John W. Shepperd
Attorney, Agent, or Firm-M. S. Yatsko
[57] ABSTRACT
A pipe support for high temperature, thin-walled verti-
cal piping runs used in a nuclear system. A cylindrical
pipe transition member, having the same inside diameter
as the thin-walled piping, replaces a portion of the pip-
ing where support is desired. The outside diameter of
the pipe transition member varies axially along its verti-
cal dimension. For a section of the axial length adjacent
the upper and lower terminations of the pipe transition
member, the outside diameter is the same as the outside
diameter of the thin-walled piping to which it is affixed.
Intermediate of the termination sections, the outside
diameter increases from the top of the member to the
bottom. Adjacent the lower termination section, the
diameter abruptly becomes the same as the piping.
Thus, the cylindrical transition member is formed to
have a generally triangular shaped cross-section along
the axial dimension. Load-bearing insulation is installed
next to the periphery of the member and is kept in place
by an outer ring clamp. The outer ring clamp is con-
nected to pipe hangers, which provide the desired sup-
port for the vertical thin-walled piping runs.
6 Claims, 4 Drawing Figures
n-J~------------------------------------------~•
I~~====~?
:,J 0II c======J/II
6. 4,046,169
1
PIPE SUPPORT FOR USE IN A NUCLEAR
SYSTEM
2
constructed from thin-walled tubing having a wall
thickness generally less than 0.5 inches.
Thin-walled piping has the ability to withstand severe
thermal transients, but in large diameter sizes, support
BACKGROUND OF THE INVENTION
5 problems arise due to the heavy weight of the contents
(liquid sodium) as compared with that of the piping
itself. Thin-walled piping is not able to provide any
significant self-support for long runs since the full-to-
This invention was made in the course of, or under, a
contract with the U.S. Energy Research And Develop-
ment Administration, the successor in interest to the
United States Atomic Energy Commission; and relates
generally to pipe supports and particularly to pipe sup- 10
ports for high temperature, thin-walled vertical piping
runs of the type found in liquid metal cooled nuclear
reactors.
A nuclear reactor produces heat by fissioning of nu-
clear materials which are fabricated into fuel elements 15
and assembled within a nuclear core situated in a pres-
sure vessel. In commercial nuclear reactors, the heat
produced thereby is used to generate electricity. Such
nuclear reactors typically comprise one or more pri-
mary flow heat transfer loops, and a corresponding 20
number of secondary flow heat transfer loops to which
conventional steam turbines and electrical generators
are coupled. A typical energy conversion process for a
commercial nuclear reactor, therefore, involves transfer
of heat from a nuclear core to the primary coolant flow 25
system, to a secondary system, where it is connected
into steam from which electricity is generated.
In liquid cooled nuclear reactors, such as liquid metal
cooled breeder reactors, a reactor coolant, such as liq-
uid sodium, is circulated through the primary coolant 30
flow system. A typical loop ofthe primary system com-
prises a nuclear core within a reactor vessel, a heat
exchanger, and a circulating pump with flow conducts
such as piping coupling the various components. In
nuclear reactors having more than one primary coolant 35
flow loop the nuclear core and reactor pressure vessel
are common to each of the primary loops. The heat
generated by the nuclear core is removed by the reactor
coolant which flows into the reactor vessel and through
the core. The heated reactor coolant then exits from the 40
reactor vessel and flows to heat exchangers which
transfer the heat through intermediate heat transfer
systems to corresponding secondary flow loops. The
cooled reactor coolant exits from respective the heat
exchangers, then flows to corresponding pumps which 45
again circulates the coolant to the pressure vessel, re-
peating the described flow cycle.
Piping is used throughout both the primary and sec-
ondary flow and heat transfer systems to provide a
means for containing the liquid sodium as it flows be- 50
tween the various components such as the pressure
vessel, heat exchangers and pumps. The piping between
the reactor pressure vessel and the heat exchangers,
commonly referred to as the hot legs of the primary
system, experiences liquid sodium temperatures of ap- 55
proximately 1000• F. The piping between the heat ex-
changer outlets and the reactor inlets, commonly re-
ferred to as the cold leg of the primary system is in
contact with liquid sodium at temperatures of approxi-
mately 100• F. This results in a large sodium tempera- 60
ture differential of approximately Joo• F between the
hot and cold leg sections of the loop. In the event of a
rapid reactor core shutdown, or similar event, the liquid
sodium temperature in the hot and cold legs of the loop
are rapidly equalized. This equalization can cause se- 65
vere through-the-wall thermal gradients making the
piping susceptible to cracking and deformation. To
avoid this problem, the liquid sodium piping is generally
empty weight ratio for a large sodium piping system
may be as high as 3:1, whereas for the more conven-
tional high temperature fluid systems the ratio is close
to unity.
System operation at high temperature produces sig-
nificant linear expansion of the piping network, and
constant support hangers are normally prescribed. For
high temperature sodium piping systems, the real diffi-
culty that arises in the design ofthe support is the design
of the attachment of the constant load hanger to the
piping. In providing attachment, it is essential to care-
fully control the magnitude and distribution of stresses
that can be attributed to structural bending and thermal
gradients which occur during system operation.
Selection of attachment location involves consider-
ation of the individual piping system, the support struc-
ture to which the piping loads are transmitted, and
space limitations. Preferred points of attachments are:
on pipe rather than on piping components such as el-
bows; and as close as possible to heavy concentrations
of loads such as vertical runs, branch lines, and valves.
Pipe attachments fall into two basic categories; at-
tachments integral with the pipe wall; and attachments
non-integral with the pipe wall. In non-integral attach-
ments, the reaction between pipe and support structure
is distributed by contact. Integral pipe attachments are
those attachments directly attached to the pipe such as
by welding.
For high temperature sodium piping, integral pipe
attachments are generally not feasible. The attachment
to the pipe wall would cause severe thermal transients
and introduce localized stress concentrations at the
place of support. Likewise, non-integral attachments
should not be in direct contact with the piping because
of the severe thermal stresses they would cause. There-
fore, in the prior art, load-bearing insulation was used
between the non-integral attachment and the pipe wall.
The prior art has generally only employed such sup-
ports for horizontal runs. For large diameter sodium
piping, the exclusive use of horizontal supports intro-
duces large primary bending stresses in the elbows im-
mediately following vertical runs of piping. It is impor-
tant to support these vertical runs to reduce the stresses
in the elbows, and to counteract the gravity loads.
Of the non-integral attachments, only clamps are
suitable for vertical runs. Direct attachment of clamps
to the piping is not feasible, both because of the severe
thermal stresses which would be introduced, and be-
cause the high temperature will relax the initial preload
and the clamp will creep and thus slip. The use of load-
bearing insulation between the clamp and the pipe wall
will not function satisfactorily, because the clamping
force will not be strong enough to prevent slippage
along the pipe. The welding of shear lugs to the piping
to prevent slippage is unsatisfactory because these lugs
will introduce thermal stresses at the welds. Addition-
ally, the support forces placed on these lugs at the same
place where the thermal transient stresses occur could
cause these lugs to act as hinges.
7. 3
4,046,169
SUMMARY OF THE INVENTION
The aforementioned disadvantages of the prior art are
eliminated by this invention by providing a pipe support
structure for high temperature, thin-walled vertical 5
piping runs. A pipe transition member, having the same
inside diameter as the piping to be supported, is installed
integral with the piping where support is desired. The
outside diameter of the pipe transition member con-
forms to the outside diameter of the pipe at the pipe to
transition member interface axial sections and progres-
sively increases along a central section from one inter-
face section to the other reverting relatively abruptly to
the pipe outside diameter at the second interface sec-
tion. This increasing outside diameter forms a generally 15
triangularly shaped, axial cross-sectional extension of
the cylindrical transition member, with a circumferen-
tial ledge being formed at the apex of the triangle. The
vertical load of the thin-walled piping is concentrated
on this ledge, and is transferred through loadbearing 20
insulation, clamps, and hanger rods to constant support
hangers. The thermal stresses caused by the structural
discontinuity of the pipe transition member are located
far enough away from the transition member/pipe inter-
face that the stresses which occur during system opera- 25
tion will dampen out well before the transition mem-
ber/pipe interface welds, alleviating any attachment
problems.
4
heat to a secondary flow system. The cooled reactor
coolant exits from the heat exchanger 26 through the
heat exchanger coolant outlet means 28, flows through
a section of interconnecting piping 30 to the primary
pump coolant flow inlet means 32. The coolant is then
pumped through the pump 34 and exits through the
primary pump coolant outlet means 36, From the pump
coolant outlet means 36, the coolant flows through
interconnecting piping 38 to the pressure vessel coolant
flow inlet means 14. The described flow cycle is then
repeated.
As previously mentioned, the heat from the primary
coolant flow system is transferred to a coolant in an
intermediate flow system in the heat exchanger 26. This
intermediate coolant, typically liquid sodium, exits from
the heat exchanger 26 through the heat exchanger inter-
mediate coolant flow outlet means 40. The coolant then
flows through interconnecting piping 42 and enters a
superheater 44 through superheater coolant inlet means
46. The coolant then flows through the superheater 44,
where the heat in the coolant is transferred to a secon-
dary coolant from which electricity is generated, and
exits through the superheater coolant flow outlet means
48. From the superheater coolant flow outlet means 48,
the coolant flows through interconnecting piping 50 to
the inlet means 52 of the evaporator 54. This intermedi-
ate coolant then flows through the evaporator 54, exits
through the outlet means 56 of the evaporator 54, flows
through interconnecting piping 58 to the inlet means 60
BRIEF DESCRIPTION OF THE ORAWINGS
For a better understanding of this invention, refer-
ence is made to the description of the preferred embodi-
ment, taken in connection with accompanying draw-
ings, in which:
30 of the pump 62. This intermediate coolant is then
pumped through the pump 62, exits through the pump
outlet means 64, flows through interconnecting piping
66 and enters the heat exchanger 26 through the heat
FIG. 1 is a view in elevation of a flow system of a 35
typical nuclear reactor;
FIG. 2 is a plan view of the pipe support;
FIG. 3 is a sectional view of the pipe support taken
along line III-III of FIG. 2; and,
FIG. 4 is a detailed view of the pipe transition mem- 40
ber shown in FIG. 3,
DESCRIPTION OF THE PREFERRED
EMBODIMENT
Throughout the following description, like reference 45
characters indicate like elements in the various figures
of the drawings.
exchanger intermediate coolant flow inlet means 68.
Although only one primary and one intermediate
coolant flow loop is described, it is obvious to one
skilled in the art that numerous primary and intermedi-
ate coolant flow loops can be utilized. As can be seen,
there are numerous locations where it may be desirable
to provide support for vertical runs of piping.
FIG. 3 illustrates one location along a vertical run
where a pipe support may be desired, namely a vertical
run of the section of piping 42 between the intermediate
coolant flow outlet means 40 of the heat exchanger 26
and the coolant inlet means 46 of the superheater 44. A
pipe transition member 70 designed to replace a small
segment of the piping run is installed into the section of
piping 42 where vertical support is desired. The transi-
tion member 70 is attached to the piping 42 by conven-
tional welds 72. These welds 72 are continuous around
the circumference of the pipe 42 and the pipe transition
member 70 at their interface, and form a liquid-tight
seal. The pipe transition member 70 can be considered
as divided into three sections; a first or upper section 74,
an intermediate section 76, and a second or lower sec-
tion 78. This division is for descriptive purposes only,
and it is to be understood that the pipe transition mem-
ber 70 is formed as an integral unit.
The first or upper section 74 and the second or lower
FIG. 1 illustrates a typical liquid metal cooled nuclear
reactor coolant flow system which can utilize the prin-
ciples of this invention. A nuclear reactor pressure ves- 50
sel 10 houses a nuclear core 12 comprised mainly of a
plurality ofclad fuel elements (not shown) which gener-
ate substantial amounts of heat. The pressure vessel 10
has coolant flow inlet means 14 and coolant flow outlet
means 16 formed integral with and through its cylindri- 55
cal walls. A quantity of reactor coolant, such as liquid
sodium, fills the pressure vessel10 to the level schemati-
cally illustrated, and designated by numeral 18, A pres-
sure vessel closure head 20 seals the top of the nuclear
reactor pressure vessel 10.
The heat generated by the nuclear core 12 is trans-
ferred to the reactor coolant entering through inlet
means 14 and exiting through outlet means 16. The hot
reactor coolant exiting through pressure vessel coolant
outlet means 16 flows through a section ofinterconnect- 65
ing piping 22 to the coolant flow inlet means 24 of the
heat exchanger 26. The heat exchanger 26, generally in
combination with an intermediate flow loop, transfers
60 section 78 of the pipe transition member 70 which can
be considered as the transition members terminations
have the same inside diameter as the section ofpiping 42
in which the transition member 70 is installed, and have
the same wall thickness, and thus have the same outside
diameter as the piping 42. The intermediate section 76
also has the same inside diameter as the piping 42. The
outside diameter of the intermediate section 76 varies
through its axial length. At the top 80 ofthe intermedi-
8. 5
4,046,169
6
ate section 76, the outside diameter is the same as the 88. By the time these stresses reach the welds 72, they
connected piping 42. This outside diameter then in- have died out enough such that they are no longer a
creases until a predetermined maximum outside diame- problem.
ter is reached (as indicated by the numeral 82). In this In addition to providing vertical support, the pipe
exemplary embodiment, this maximum outside diame- 5 transition member 70 also prevents movement in the
ter, maximum being a term meaning the furtherest dis- case of a seismic disturbance. The load-bearing insula-
lance outward in actuality and not being used in a limit- tion 90 extends vertically adjacent to the triangular
ing sense, remains constant for a short section 84 until extension 88 of the pipe transition member 70. In the
the top of the lower section 85 is reached. The outside case of a seismic disturbance, the ledge 86 of the pipe
diameter then abruptly returns to the same outside di- 10 extension piece is prevented from downward move-
ameter as the piping 42. This return may be accom- ment by the support provided by the load-bearing insu-
plished either along a straight line or along a curved lation 90, the clamp 92, and the pipe support rods 96,
line. This structure forms a circumferential ledge 86 at together with the constant support hanger 98 and the
the top of the lower section 78. The entire intermediate ceiling 100. Upward vertical movements are prevented
section 76 then resembles a generally triangularly cross- 15 by the geometry of the triangular extension 88 which is
sectional radial extension 88 completely surrounding restrained against movement by the load-bearing insula-
the cylindrical transition member 70. tion 90. The section 84 having the maximum outside
Annular load-bearing insulation 90, of a material such diameter is prevented from moving vertically upward
as that made ofdiatomaceous earth and fillers, is located because the load-bearing insulation 90 above the section
adjacent to the ledge 86 of the transition member 70. 20 84 has a smaller diameter of the section 84.
For best results, this load-bearing insulation 90 should Without departing from the teachings of this inven-
extend across the entire radial length of the ledge 86 tion, the orientation of the pipe transition member 70,
except preferably for a small space 93, of about .125 and especially of the triangular extension 88, may be
inch, next to the outward side of the lower section 78. inverted. That is, instead of having the ledge 86 at the
The load-bearing insulation 90 should also extend hori- 25 top of the lower section 78, the ledge 86 be placed at the
zontally, radially outward from the ledge 86 beyond the bottom point 80 of the first or upper section 74, tapering
maximum outside diameter, and should extend verti- down to the normal outside diameter of the pipe 42 at
cally, axially, upward adjacent to the periphery of the the top of the second or lower section 78. In this orien-
triangularly shaped extension 88 of the transition mem- tation, the load would still be carried by the load-bear-
her 70. 30 ing insulation 90, but the load would be located next to
The load-bearing insulation 90 is maintained adjacent the tapered section of the triangular extension 88.
to the ledge 86 and the triangular extension 88 by Dimensioning of the pipe transition member 70 de-
clamping means 92 (see FIG. 2). This clamping means pends upon the load to be supported in the piping 42
92, typical of which is a split-ring clamp, completely and the physical properties of the load-bearing insulat-
encircles the load-bearing insulation 90 and correspond- 35 ing 90. FIG. 4 illustrates in detail the pipe transition
ingly the pipe transition member 70. To avoid the afore- member with the symbols used in dimensioning shown
mentioned problems of direct contact with hot piping, thereon.
the lower lip 94 of the clamp 92 should be kept a short From elementary mechanics, the stress, SN which will
distance 93 away from the pipe transition member 70, be placed on the load-bearing insulation 90 is equal to
mainly the lower section 78. 40 the load to be supported, P, divided by the area, A, of
The clamping means 92 should provide a constant the surface upon which this load will bear. The load to
clamping force, and still accommodate any radial ex- be supported, P, is determined from a deadweight anal-
pansion of the piping 42 and the pipe transition member ysis of the piping system. The allowable stress on the
70 due to the flow of hot coolant through the piping 42. load-bearing insulation 90, is found from the specifica-
The clamp 92 is connected to a pipe hanger rod 96. 45 tion of the load-bearing insulation, and should be a
This pipe hanger rod 96 is connected to a constant stress such that the load-bearing insulation will be mini-
support hanger 98, which in turn is secured either to the mally deformed (approximately 1% deformation or
ceiling of the containment building 100 or possibly to a less). The minimum area, A, of the bearing surface can
pipe support framework (not shown). Alternately, the then be calculated from this equation. This bearing
clamp 92 may be connected to piping (not shown) 50 surface area is the area of the ledge 86 which will be
which is secured to the floor (not shown). supported by the load-bearing insulation 90.
Support of the vertical piping run occurs in the fol- The bearing surface area is found from the equation
lowing manner. The load of the vertical piping run 42 is
transferred from the piping 42 to the pipe transition
member 70, mainly through the triangular extension 88 55
and the ledge 86. The load is then transferred to the
annular loadbearing insulation 90 through the ledge 86.
The load on the load-bearing insulation 90 is transferred
to the clamping means 92 which supports the load-bear-
ing insulation 90. The load is then transferred to the pipe 60
hanger rod 96 from the clamping means 92, and is then
transferred along the pipe hanger rod 96 to the constant
support hanger 98 and the ceiling 100.
The aforementioned problems associated with
welded attachments are eliminated by the tapered out- 65
side diameter of the extension 88. The thermal stresses
caused by the structural discontinuity of the ledge 86
dampen as they travel along the taper of the extension
(I)
in which D1o the maximum outside diameter of the
member, is equal to the inside diameter of the pipe (J.D.)
plus two times the wall thickness (t) of the piping 42,
plus two times the space 93 (S) left between the load-
bearing insulation and the lower section 78 plus two
times the width of the ledge (Wd where the load-bear-
ing insulation is located. Mathematically, the maximum
outside diameter can be expressed as
Dt = !.D. + 2(1) + 2(WL) + 2(S). (II)
0 2 is equal to the inside diameter of the piping 42 plus
two times the wall thickness of the transition member
9. 4,046,169
87
70, plus two times the width of the space 931eft between
the load-bearing insulation 90 and the lower section 78.
Mathematically this is expressed as
Dl = V588 + (160/3.14)
D 1 = 25.28.
D2 = I.D. + 2(1) + 2(S).
(III)
5
However, the final diameter, D~o is also equal to
The equation for the area (I) is then solved for the final
outside diameter, D~o and eventually solved for the
effective width of the ledge, WL· The total width of the
ledge, Lw is the quantity WL + S. 10
D1 = I.D. + 2(1) + 2(WJ + 2(5), or
25.28 = 23 + 2(0.5) + 2(Wu + 2(0.125)
WL = (25.28 - 23 - I - 0.25/2) = 0.515.
The total length ofthe ledge, L,xis equal to the width of
the load-bearing ledge 86, Wv plus the space 93 be-
tween the insulation 90 and the lower section 78 or S.
Substituting,
L., = WL + S = 0.515 + 0.125 = 0.64
For ease of fabrication, make this ledge width, L,xo
0.650 inches.
Once the total ledge 86 width, Lexo is known, the
minimum length of the taper, TL• of the triangular ex-
tension 88 can be determined. This determination is for
the minimum length of taper, and a longer taper length
may be used if so desired. The taper TL is equal to the 15
square root of the mean radius RMof the piping 42 times
the thickness of the heavy wall, which is the quantity;
total thickness of the ledge 86, Lexo plus the wall thick-
ness, t, of the piping 42 and the transition member 70.
Mathematically, this is expressed as 20 The minimum length of taper necessary, TL• for the
triangular extension 88 can then be calculated from the
formula:
(IV)
The length, L5, of the first or upper section 74, which
is the same as the length of the second or lower section 25
78, should be long enough that the taper of the triangu-
lar extension 88 is not in the heat-affected zone of the
weld 72; that is, the length of the sections 74, 78 should
prevent the stresses occurring at the weld 72 from being
(IV)
where mean radius RM = (I.D. -:- 2) + (t -:- 2). Solving,
RM= (23 7 2) + (0.5 7 2) = 11.5 + 0.25 = 11.75.
transmitted to the taper. In hot liquid metal sodium 30 Substituting in equation (IV)
piping systems, this length Ls has generally been found
to be approximately five to six inches.
The length Lr of the straight section of maximum
outside diameter 84 is preferably inserted so that the
taper of the triangular extension 88 does not run directly 35
into the ledge 86. If it is so desired, this straight section
84 can be eliminated from the design of the pipe transi-
tion member 70. If inclusion of this section 84 is desired,
for ease of fabrication the length, Lr. should be approxi-
mately 0.5 inches. 40
TL = ((11.75)(0.65 + 0.5)]178
TL = 3.67
For ease of calculation, the above equations have
been combined into two equations from which the criti-
cal dimensions can be calculated. The width of the
ledge 86, Lex, can be determined from
(V)
~(lD. +21+25)2+*-/.D. -21
L., = 2
The space 93, S, between the load-bearing insulation
90 and the outward side of the lower section 78 should
be just large enough that the load-bearing insulation 90
and the lip 94 of the clamp 90 does not come into
contact with the lower section 78. A width of 0.125
inches has been found to be satisfactory. 45 The length ofthe taper, Tv can then be calculated using
An example may be appropriate for a better under-
standing ofthe dimensioning. The system piping 42 was
assumed to be 24 inch by 0.500 inch wall piping. The
maximum vertical load was 20,000 pounds, and the
maximum stress for 0.5% deformation of the insulation
50
was 500 pounds per square inch. Substituting into the
stress equation, stress = PIA, and solving for A, the
load bearing surface area was found to be 40 square
(VI)
Once these calculations have been made, the pipe
transition member 70 can be fabricated. For example,inches. The non-load bearing diameter, 0 2, was
D 2 = I.D. + 2(1) + 2(5), or
D2 = 23 + 2(0.5) + 2(0.125) = 24.25
55 based on the above calculations, the pipe transition
member 70 can be machined from a piece of piping with
an outside diameter of 26 inches, an inside diameter of
21 inches, and a length of 20 inches.
Then, using the area equation, (I)
40 = (3.14/4)(D1D- 24.252)
40 = (3.14/4)(D1l - 588.06).
Solving for Dh
60
65
We claim as our invention:
1. A ptpe support system comprising:
a vertical pipe;
an integrally formed tubular pipe support structure
having the same inside diameter as said pipe, said
pipe support structure having the same wall thick-
ness as said pipe, said pipe support structure having
a generally triangularly shaped extension formed
integral with and extending circumferentially
around its outward side, the bottom side of said
10. 9
4,046,169
10
extension generally forming a ledge, said pipe sup-
port structure replacing a portion of said pipe;
S = a horizontal distance along said ledge wherein no
load will be carried;
an annular load-bearing insulation formed adjacent to
said extension, said load-bearing insulation support- 5
ing said pipe support structure substantially
through said ledge;
P = an amount of load to be supported; and
Sr = a stress which may be carried by said load-bear-
ing insulation.
3. The system according to claim 2 wherein the out-
side diameter of said extension varies from a diameter
being the same as the outside diameter of said vertical
pipe to a maximum diameter at least the same as the
means for clamping said load-bearing insulation to
said extension, said means for clamping said insula-
tion being located such that a first space is main-
tained between said means for clamping and said
pipe support structure; and
means for providing constant vertical support to said
means for clamping.
l. The system according to claim 1 wherein said ledge
at least extends horizontally outward beyond the out-
ward side of said vertical pipe a minimum distance
determined by the equation
~(LD. + 2t + 2S)l +*-J.D.- 2t
L., = 2
wherein
Lex = said minimum distance said ledge extends be-
yond the outward side of said vertical pipe;
I.D. = an inside diameter of said vertical pipe;
t = a pipe-wall thickness of said vertical pipe;
10 outside diameter of said vertical pipe plus twice the
distance said ledge extends horizontally outward, said
outside diameter of said extension increasing through at
least a miniJDum distance determined by the equation
TL = Y([I.D. + t]I2XL... + /)
15
20
wherein
Lex = the actual distance said ledge extends beyond
the outward side of said vertical pipe; and
TL = said minimum distance along which said in-
creasing outside diameter of said extension occurs.
4. The system according to claim 1 wherein said pipe
support structure and said vertical pipe are cylindrical.
S. The system according to claim 1 wherein said ex-
tension has an outside diameter which is substantially
25 constant for a vertical axial distance adjacent to said
ledge.
6. The system according to claim 1 wherein said load-
bearing insulation and said pipe support structure verti-
cally below said extension form an axial annular second
30 space therebetween.
• • • • •
35
40
45
so
55
60
65