This document provides information about the design of shafts, keys, and couplings. It discusses transmission shafts, stresses induced in shafts, and shaft design based on strength and rigidity. It presents formulas for shaft design using maximum shear stress theory, distortion energy theory, and the ASME code. Several examples are provided to demonstrate how to calculate the diameter of a shaft given the power transmitted, loads on the shaft, material properties, and other parameters using these theories and codes. Assignments involving similar calculations of shaft diameters are presented.
- The document discusses different types of springs including helical compression springs, helical extension springs, helical torsion springs, and multileaf springs.
- It describes the functions and applications of springs which include absorbing shocks and vibrations, storing energy, and measuring forces.
- Key terms related to helical spring design are defined such as wire diameter, mean coil diameter, spring index, solid length, compressed length, free length, and pitch. Stress and deflection equations for helical spring design are also presented.
Springs - DESIGN OF MACHINE ELEMENTS-IIDr. L K Bhagi
Introduction to springs, Types and terminology of springs, Stress and deflection equations, Series and parallel connection, Design of helical springs, Design against fluctuating load, Concentric springs, Helical torsion springs, Spiral springs, Multi-leaf springs, Optimum design of helical spring
The various forces acts on the reciprocating parts of an engine.
The resultant of all the forces acting on the body of the engine due to inertia forces only is known as unbalanced force or shaking force.
Unit 6- spur gears, Kinematics of machines of VTU Syllabus prepared by Hareesha N Gowda, Asst. Prof, Dayananda Sagar College of Engg, Blore. Please write to hareeshang@gmail.com for suggestions and criticisms.
Shaft & keys (machine design & industrial drafting )Digvijaysinh Gohil
This document discusses different types of shafts, keys, and their design considerations. It contains the following key points:
1. Shafts can be classified based on their shape (solid or hollow), application (transmitting, machine, spindle), and construction (rigid or flexible).
2. Keys are used to connect rotating machine elements to shafts and prevent relative motion. Common types include rectangular, square, parallel, gib-head, feather, and woodruff keys.
3. Shaft design considers factors like bending moment, shear stress, and material properties. Hollow shafts have higher strength-to-weight ratio than solid shafts of the same size.
Design against fluctuating loads, stress concentration, Goodman and Modified Goodman Diagrams, Factors affecting stress concentration, Use of charts for finding stress concentration facotrs
- Clutches are used to connect or disconnect a driving shaft from a driven shaft. They allow transmission of power from one shaft to another that needs to be started or stopped frequently.
- There are two main types of clutches: positive clutches and friction clutches. Cone clutches are a type of friction clutch with conical working surfaces.
- Torque transmission in clutches is calculated using either a uniform pressure theory or uniform wear theory. These theories make assumptions about the pressure distribution across the clutch plates or cones.
Unit 7-gear trains, Kinematics of machines of VTU Syllabus prepared by Hareesha N Gowda, Asst. Prof, Dayananda Sagar College of Engg, Blore. Please write to hareeshang@gmail.com for suggestions and criticisms.
- The document discusses different types of springs including helical compression springs, helical extension springs, helical torsion springs, and multileaf springs.
- It describes the functions and applications of springs which include absorbing shocks and vibrations, storing energy, and measuring forces.
- Key terms related to helical spring design are defined such as wire diameter, mean coil diameter, spring index, solid length, compressed length, free length, and pitch. Stress and deflection equations for helical spring design are also presented.
Springs - DESIGN OF MACHINE ELEMENTS-IIDr. L K Bhagi
Introduction to springs, Types and terminology of springs, Stress and deflection equations, Series and parallel connection, Design of helical springs, Design against fluctuating load, Concentric springs, Helical torsion springs, Spiral springs, Multi-leaf springs, Optimum design of helical spring
The various forces acts on the reciprocating parts of an engine.
The resultant of all the forces acting on the body of the engine due to inertia forces only is known as unbalanced force or shaking force.
Unit 6- spur gears, Kinematics of machines of VTU Syllabus prepared by Hareesha N Gowda, Asst. Prof, Dayananda Sagar College of Engg, Blore. Please write to hareeshang@gmail.com for suggestions and criticisms.
Shaft & keys (machine design & industrial drafting )Digvijaysinh Gohil
This document discusses different types of shafts, keys, and their design considerations. It contains the following key points:
1. Shafts can be classified based on their shape (solid or hollow), application (transmitting, machine, spindle), and construction (rigid or flexible).
2. Keys are used to connect rotating machine elements to shafts and prevent relative motion. Common types include rectangular, square, parallel, gib-head, feather, and woodruff keys.
3. Shaft design considers factors like bending moment, shear stress, and material properties. Hollow shafts have higher strength-to-weight ratio than solid shafts of the same size.
Design against fluctuating loads, stress concentration, Goodman and Modified Goodman Diagrams, Factors affecting stress concentration, Use of charts for finding stress concentration facotrs
- Clutches are used to connect or disconnect a driving shaft from a driven shaft. They allow transmission of power from one shaft to another that needs to be started or stopped frequently.
- There are two main types of clutches: positive clutches and friction clutches. Cone clutches are a type of friction clutch with conical working surfaces.
- Torque transmission in clutches is calculated using either a uniform pressure theory or uniform wear theory. These theories make assumptions about the pressure distribution across the clutch plates or cones.
Unit 7-gear trains, Kinematics of machines of VTU Syllabus prepared by Hareesha N Gowda, Asst. Prof, Dayananda Sagar College of Engg, Blore. Please write to hareeshang@gmail.com for suggestions and criticisms.
,
diploma mechanical engineering
,
mechanical engineering
,
machine design
,
design of machine elements
,
knuckle joint
,
failures of knuckle joint under different streses
,
fork end
,
single eye end
,
knuckle pin
Unit 5- balancing of reciprocating masses, Dynamics of machines of VTU Syllabus prepared by Hareesha N Gowda, Asst. Prof, Dayananda Sagar College of Engg, Blore. Please write to hareeshang@gmail.com for suggestions and criticisms.
The document discusses transmission shafts and their design. It defines a transmission shaft as a rotating element that supports transmission elements like gears and transmits power. Stepped shafts are commonly used, with maximum diameter in the middle and minimum at the ends. Shaft material is typically carbon steel. Design considers strength based on stresses from loads, torsional rigidity based on permissible twist, and ASME code factors for shock/fatigue. Equivalent moment concepts are introduced for combined loading conditions.
This document discusses the design of connecting rods for internal combustion engines. It describes the functions of connecting rods as transmitting force between the piston and crankshaft. Key aspects covered include common connecting rod designs, considerations for determining connecting rod length, materials used, forces acting on connecting rods, and design parameters such as cross-sectional dimensions and crankpin/piston pin sizes. Formulas are provided for calculating cross-sectional moments of inertia to ensure equal resistance to buckling in both planes.
1. The document discusses different types of clutches including positive clutches and friction clutches. It describes the key components and operation of a single plate clutch commonly used in automotive applications.
2. Formulas are presented for calculating the torque capacity of clutches under uniform pressure and uniform wear conditions based on geometric parameters, pressure, and coefficient of friction.
3. The document provides an example problem demonstrating the use of the formulas to design a multi-plate clutch meeting specific torque and speed requirements.
Design of Flat belt, V belt and chain drivesDr. L K Bhagi
Geometrical relationships, Analysis of belt tensions, Condition for maximum power transmission, Characteristics of belt drives, Selection of flat belt, V- belt, Selection of V belt, Roller chains, Geometrical relationship, Polygonal effect, Power rating of roller chains, Design of chain drive, Introduction to belt drives and belt construction, Introduction to chain drives
Rolling contact bearings and design procedureJashavant singh
this slide will give you idea about the rolling contact bearing , its types application areas and also you will learn how to design rolling contact bearing ,
comparison between the rolling contact and sliding contact bearing , advantage and disadvantages.
The document discusses different types of gears including spur gears, helical gears, herringbone gears, rack and pinion gears, bevel gears, and worm gears. It provides details on each type, such as how they transmit power at different angles, speeds, and ratios. Spur gears have parallel teeth and are used in devices like electric screwdrivers. Helical gears operate more smoothly than spur gears. Herringbone gears are a type of double helical gear. Rack and pinion gears convert rotational motion to linear motion. Bevel gears transmit power at intersecting shafts. Worm gears provide large gear reductions and can easily turn in one direction.
The document discusses various types of shafts and shaft couplings. It provides information on shaft materials, sizing, layout and design considerations. Regarding couplings, it describes rigid couplings like sleeve, flange and marine couplings. It also discusses flexible bush pin couplings. Key points covered include shaft material selection, stress analysis for sizing, deflection requirements, coupling design for strength, rigidity and alignment between connected shafts. Common shaft and coupling types, their designs and applications are explained.
This document discusses different types of keys used to connect rotating machine elements to shafts. It describes sunk keys like rectangular, square, parallel, gib-head, and feather keys. It also discusses saddle keys, tangent keys, round keys, and splines. The main types of keys covered are sunk keys like rectangular, square, parallel, gib-head, and feather keys which are partially inserted in the shaft and hub keyways. It provides details on the purpose and design of each key type.
A key connects a shaft to a pulley to prevent relative motion. Common key types include sunk, saddle, tangent, round, and splined keys. A rectangular sunk key is usually d/4 wide and d/6 thick, with a 1 in 100 taper on top. It transmits torque from the shaft to the pulley, withstanding both shearing and crushing stresses. The key length to transmit full shaft power is calculated as 1.571 times the shaft diameter.
Definition, Use, Types of beariings, Types of Journal bearing, Materials for journal bearing, Failures of journal bearing, Design terms for journal bearing, Types of roller contact bearing, applications of roller contact bearing, Designation of roller contact bearing, Design terms for roller contact bearing, comparison between journal and roller bearings, characteristics of bearings, selection procedure of bearings
This presentation provides an overview of worm gears, including their two types (cylindrical and cone), three types of worm gears, common materials used, key terms, how they work to reduce speed and increase torque via a high velocity ratio, common applications, advantages of being self-locking and occupying less space, disadvantages of higher costs and lower efficiency, and areas for further research such as improved lubrication. Worm gears are widely used gear systems for transmitting power between non-intersecting shafts, especially at high velocity ratios.
Design of clutch theory Prof. Sagar a DhotareSagar Dhotare
This covers following points,
Introduction to clutch
Classification
Requirement of good friction clutch
Requirements of material used for friction clutch
Material used for friction clutch
Considerations in Designing a Friction Clutch
Design of Single Disc or Plate Clutch
Design of Multi Disc or Plate Clutch
Design of Cone Clutch
Comparison between Single and Multi Plate Clutch
Comparison between Plate and Cone Clutch
1. A shaft transmits power and rotational motion and has machine elements like gears and pulleys mounted on it.
2. Press fits, keys, dowel pins, and splines are used to attach machine elements to the shaft.
3. The shaft rotates on rolling contact or bush bearings and uses features like retaining rings to take up axial loads.
4. Couplings are used to transmit power between drive and driven shafts like between a motor and gearbox.
This document contains a question bank for the Design of Machine Elements course covering various topics in 5 units. It includes over 180 questions related to steady and variable stresses in machine members, shafts and couplings, joints, energy storing elements, and bearings. The questions cover topics such as stress analysis, materials selection, fits and tolerances, failure theories, stress concentration, fatigue design, and design of common machine components. The document also lists the textbook and references used for the course.
This presentation contains basic idea regarding spur gear and provides the best equations for designing of spur gear. One can Easily understand all the parameters required to design a Spur Gear
The document discusses the design of connecting rods for internal combustion engines. It describes the functions of connecting rods as transmitting force between the piston and crankshaft. The dimensions and material selection of connecting rods are important considerations. Connecting rods must be strong enough to withstand buckling forces while also being as lightweight as possible. The document provides steps for calculating the cross-sectional dimensions, sizes of bearings, bolts, and other components of connecting rods based on engine specifications and safety factors.
This document summarizes information about journal bearings. It defines a journal bearing as a block of cast iron with a hole for supporting a rotating shaft. It describes how lubricating oil is fed into the bearing and dragged by the shaft, creating hydrodynamic lift and resisting shaft motion. There are three types of journal bearings: dry, hydrodynamic, and hydrostatic. The document discusses the pressure distribution in a journal bearing due to the flow of viscous fluid in a converging channel, and defines the eccentricity ratio as the ratio of eccentricity to radial clearance. It concludes with discussing the study of bearing functions and types, and viewing the pressure distribution curve of a journal bearing.
This document discusses the design of solid and hollow shafts subjected to different types of loads. It covers standard shaft sizes and materials, design considerations based on strength and stiffness, stresses due to bending, axial force and torsion, and design according to the ASME code. Example problems are also included to calculate shaft diameters based on strength using factors like load, material properties, and safety factors.
Design and Analysis of Centrifugal Governor: A ReviewIRJET Journal
This document provides a review of the design and analysis of a centrifugal governor. It begins with an abstract describing the objective to identify stress concentration areas and areas most susceptible to failure when the governor rotates. It then discusses the materials used for different governor parts, including stainless steel for the spindle and arms due to its strength. The document outlines the governor design process and criteria. It also analyzes the stresses on parts like the shaft and bearings. Graphs show how the governor's axial deflection increases with angular velocity. The analysis identifies high stress concentration areas that require strengthening to avoid failure.
,
diploma mechanical engineering
,
mechanical engineering
,
machine design
,
design of machine elements
,
knuckle joint
,
failures of knuckle joint under different streses
,
fork end
,
single eye end
,
knuckle pin
Unit 5- balancing of reciprocating masses, Dynamics of machines of VTU Syllabus prepared by Hareesha N Gowda, Asst. Prof, Dayananda Sagar College of Engg, Blore. Please write to hareeshang@gmail.com for suggestions and criticisms.
The document discusses transmission shafts and their design. It defines a transmission shaft as a rotating element that supports transmission elements like gears and transmits power. Stepped shafts are commonly used, with maximum diameter in the middle and minimum at the ends. Shaft material is typically carbon steel. Design considers strength based on stresses from loads, torsional rigidity based on permissible twist, and ASME code factors for shock/fatigue. Equivalent moment concepts are introduced for combined loading conditions.
This document discusses the design of connecting rods for internal combustion engines. It describes the functions of connecting rods as transmitting force between the piston and crankshaft. Key aspects covered include common connecting rod designs, considerations for determining connecting rod length, materials used, forces acting on connecting rods, and design parameters such as cross-sectional dimensions and crankpin/piston pin sizes. Formulas are provided for calculating cross-sectional moments of inertia to ensure equal resistance to buckling in both planes.
1. The document discusses different types of clutches including positive clutches and friction clutches. It describes the key components and operation of a single plate clutch commonly used in automotive applications.
2. Formulas are presented for calculating the torque capacity of clutches under uniform pressure and uniform wear conditions based on geometric parameters, pressure, and coefficient of friction.
3. The document provides an example problem demonstrating the use of the formulas to design a multi-plate clutch meeting specific torque and speed requirements.
Design of Flat belt, V belt and chain drivesDr. L K Bhagi
Geometrical relationships, Analysis of belt tensions, Condition for maximum power transmission, Characteristics of belt drives, Selection of flat belt, V- belt, Selection of V belt, Roller chains, Geometrical relationship, Polygonal effect, Power rating of roller chains, Design of chain drive, Introduction to belt drives and belt construction, Introduction to chain drives
Rolling contact bearings and design procedureJashavant singh
this slide will give you idea about the rolling contact bearing , its types application areas and also you will learn how to design rolling contact bearing ,
comparison between the rolling contact and sliding contact bearing , advantage and disadvantages.
The document discusses different types of gears including spur gears, helical gears, herringbone gears, rack and pinion gears, bevel gears, and worm gears. It provides details on each type, such as how they transmit power at different angles, speeds, and ratios. Spur gears have parallel teeth and are used in devices like electric screwdrivers. Helical gears operate more smoothly than spur gears. Herringbone gears are a type of double helical gear. Rack and pinion gears convert rotational motion to linear motion. Bevel gears transmit power at intersecting shafts. Worm gears provide large gear reductions and can easily turn in one direction.
The document discusses various types of shafts and shaft couplings. It provides information on shaft materials, sizing, layout and design considerations. Regarding couplings, it describes rigid couplings like sleeve, flange and marine couplings. It also discusses flexible bush pin couplings. Key points covered include shaft material selection, stress analysis for sizing, deflection requirements, coupling design for strength, rigidity and alignment between connected shafts. Common shaft and coupling types, their designs and applications are explained.
This document discusses different types of keys used to connect rotating machine elements to shafts. It describes sunk keys like rectangular, square, parallel, gib-head, and feather keys. It also discusses saddle keys, tangent keys, round keys, and splines. The main types of keys covered are sunk keys like rectangular, square, parallel, gib-head, and feather keys which are partially inserted in the shaft and hub keyways. It provides details on the purpose and design of each key type.
A key connects a shaft to a pulley to prevent relative motion. Common key types include sunk, saddle, tangent, round, and splined keys. A rectangular sunk key is usually d/4 wide and d/6 thick, with a 1 in 100 taper on top. It transmits torque from the shaft to the pulley, withstanding both shearing and crushing stresses. The key length to transmit full shaft power is calculated as 1.571 times the shaft diameter.
Definition, Use, Types of beariings, Types of Journal bearing, Materials for journal bearing, Failures of journal bearing, Design terms for journal bearing, Types of roller contact bearing, applications of roller contact bearing, Designation of roller contact bearing, Design terms for roller contact bearing, comparison between journal and roller bearings, characteristics of bearings, selection procedure of bearings
This presentation provides an overview of worm gears, including their two types (cylindrical and cone), three types of worm gears, common materials used, key terms, how they work to reduce speed and increase torque via a high velocity ratio, common applications, advantages of being self-locking and occupying less space, disadvantages of higher costs and lower efficiency, and areas for further research such as improved lubrication. Worm gears are widely used gear systems for transmitting power between non-intersecting shafts, especially at high velocity ratios.
Design of clutch theory Prof. Sagar a DhotareSagar Dhotare
This covers following points,
Introduction to clutch
Classification
Requirement of good friction clutch
Requirements of material used for friction clutch
Material used for friction clutch
Considerations in Designing a Friction Clutch
Design of Single Disc or Plate Clutch
Design of Multi Disc or Plate Clutch
Design of Cone Clutch
Comparison between Single and Multi Plate Clutch
Comparison between Plate and Cone Clutch
1. A shaft transmits power and rotational motion and has machine elements like gears and pulleys mounted on it.
2. Press fits, keys, dowel pins, and splines are used to attach machine elements to the shaft.
3. The shaft rotates on rolling contact or bush bearings and uses features like retaining rings to take up axial loads.
4. Couplings are used to transmit power between drive and driven shafts like between a motor and gearbox.
This document contains a question bank for the Design of Machine Elements course covering various topics in 5 units. It includes over 180 questions related to steady and variable stresses in machine members, shafts and couplings, joints, energy storing elements, and bearings. The questions cover topics such as stress analysis, materials selection, fits and tolerances, failure theories, stress concentration, fatigue design, and design of common machine components. The document also lists the textbook and references used for the course.
This presentation contains basic idea regarding spur gear and provides the best equations for designing of spur gear. One can Easily understand all the parameters required to design a Spur Gear
The document discusses the design of connecting rods for internal combustion engines. It describes the functions of connecting rods as transmitting force between the piston and crankshaft. The dimensions and material selection of connecting rods are important considerations. Connecting rods must be strong enough to withstand buckling forces while also being as lightweight as possible. The document provides steps for calculating the cross-sectional dimensions, sizes of bearings, bolts, and other components of connecting rods based on engine specifications and safety factors.
This document summarizes information about journal bearings. It defines a journal bearing as a block of cast iron with a hole for supporting a rotating shaft. It describes how lubricating oil is fed into the bearing and dragged by the shaft, creating hydrodynamic lift and resisting shaft motion. There are three types of journal bearings: dry, hydrodynamic, and hydrostatic. The document discusses the pressure distribution in a journal bearing due to the flow of viscous fluid in a converging channel, and defines the eccentricity ratio as the ratio of eccentricity to radial clearance. It concludes with discussing the study of bearing functions and types, and viewing the pressure distribution curve of a journal bearing.
This document discusses the design of solid and hollow shafts subjected to different types of loads. It covers standard shaft sizes and materials, design considerations based on strength and stiffness, stresses due to bending, axial force and torsion, and design according to the ASME code. Example problems are also included to calculate shaft diameters based on strength using factors like load, material properties, and safety factors.
Design and Analysis of Centrifugal Governor: A ReviewIRJET Journal
This document provides a review of the design and analysis of a centrifugal governor. It begins with an abstract describing the objective to identify stress concentration areas and areas most susceptible to failure when the governor rotates. It then discusses the materials used for different governor parts, including stainless steel for the spindle and arms due to its strength. The document outlines the governor design process and criteria. It also analyzes the stresses on parts like the shaft and bearings. Graphs show how the governor's axial deflection increases with angular velocity. The analysis identifies high stress concentration areas that require strengthening to avoid failure.
SEMINAR @Design And Analysis Of A Connecting Rod With Different MaterialsDr.M BALA THEJA
This document describes a study analyzing connecting rods made of different materials using ANSYS software. The study models connecting rods made of forged steel, silicon carbide, aluminum 7068 alloy, and stainless steel 304. It simulates each material to calculate stress, strain, and deformation. The results show that a connecting rod made of silicon carbide experiences the highest maximum stress of 2.9968x108 MPa but the lowest deformation of 0.00056179. The conclusion is that using lighter materials like aluminum alloys can reduce the connecting rod's weight while still withstanding the forces.
1. The document describes a horizontal shaft supported by bearings at each end that carries two gears.
2. Gears C and D are located 250mm and 400mm from their respective bearings and have pitch diameters of 600mm and 200mm.
3. The shaft transmits 20kW of power at 120rpm, delivered at gear C and taken out at gear D, with vertical tooth pressures on each gear.
4. The question asks to determine the shaft diameter if the working stresses are 100MPa in tension and 56MPa in shear.
Review of shaft failure in Coil Car AssemblyIRJET Journal
This document summarizes a study on failures of shafts in coil car assemblies. The researchers investigated a failed coil car shaft and found that reversed bending fatigue caused it to fracture, occasionally due to misalignment. They calculated loads on the existing shaft theoretically and analytically and found the stresses exceeded permissible levels, indicating it was prone to failure. To improve shaft design, they examined increasing diameter and using fillets/chamfers to disperse stresses. A literature review showed other shaft failures were due to low radius of curvature, incorrect chamfer size increasing stress concentration, and vibrations from imbalance.
STATIC AND DYNAMIC ANALYSIS OF HIGH SPEED MOTORIZED SPINDLEIRJET Journal
This document analyzes the static and dynamic behavior of a high-speed motorized spindle used in computer numerical control (CNC) machining centers. A spindle model is created in ANSYS software and analyzed under static rotational loading and dynamic cutting forces. Modal analysis identifies the spindle's natural frequencies and mode shapes. Harmonic response analysis examines deflection under simulated cutting forces from 0-1400Hz. Testing is done for spindle materials EN24 and H13 under aluminum machining parameters. Results show maximum deflections of 0.016mm and 0.005mm under rotational and cutting loads for EN24. Natural frequencies up to 2754Hz are identified. The study provides data on spindle stiffness and vibrational behavior to improve machining
ME6503 design of machine elements - question bank.Mohan2405
This document contains questions and problems related to the design of machine elements, specifically regarding shafts and couplings. It includes 20 questions in Part A testing basic recall and understanding, 13 multi-part problems in Part B applying concepts to design scenarios, and 4 complex design problems in Part C. The topics covered include stresses in shafts, hollow vs solid shafts, keys and keyways, rigid and flexible couplings, and the design of shafts and keys based on strength and rigidity considerations.
5 shaft shafts subjected to combined twisting moment and bending momentDr.R. SELVAM
1. The document discusses the design of shafts that are subjected to both twisting moments and bending moments.
2. It describes two theories for analyzing combined stresses: maximum shear stress theory for ductile materials like steel, and maximum normal stress theory for brittle materials like cast iron.
3. It provides an example of determining the diameter of a shaft made of 45 C 8 steel that is subjected to a bending moment of 3000 N-m and torque of 10,000 N-m, with a safety factor of 6.
IRJET- Design and Analysis of a two Wheeler Shock Absorber Coil SpringIRJET Journal
This document summarizes the design and analysis of a coil spring for a two-wheeler shock absorber. It describes the design process for an oil-tempered spring steel spring, including calculations to determine dimensions. Finite element analysis was performed using ANSYS to analyze deformation and stresses on the spring under different loading conditions: the weight of the bike plus two people, one person, and just the bike. The results were also compared between oil-tempered spring steel and beryllium copper materials. The analysis found that beryllium copper had lower stresses but greater deformation, indicating it is safer but oil-tempered spring steel has better stiffness.
IRJET - Optimization of Crankshaft by Modification in Design and MaterialIRJET Journal
This document summarizes an analysis and optimization of a crankshaft design for a 4-cylinder inline gasoline engine. A 3D model of the crankshaft was created in Siemens NX software based on engine specifications. Finite element analysis was performed in ANSYS to evaluate stresses and deformation. The analysis showed maximum von Mises stress of 223.76 MPa and shear stress of 127.31 MPa, both at joints between the crankshaft spindle and web. Total deformation was a minimal 0.14091 mm. The safety factor of 1.5195 indicated the design would withstand fatigue loading over an infinite lifespan. Modifications like added fillets helped reduce stresses by distributing loads more evenly. The optimized
Design and Construction of a Connecting rodFaisal Niloy
The document describes the design and construction of a connecting rod. It begins with the objectives of studying the connecting rod, understanding its function, designing it using CAD, and constructing a physical model. It then provides an introduction to connecting rods, explaining that they connect the piston to the crankshaft and transmit reciprocating motion to rotational motion. The document discusses different manufacturing processes for connecting rods and compares technologies. It presents the design process for the connecting rod, showing calculations for dimensions. Finally, it includes the CAD model and photos of the constructed physical connecting rod.
Design & Construction of a Connecting rodFaisal Niloy
The document describes the design and construction of a connecting rod. It begins with the objectives of studying the connecting rod, understanding its function, designing it using CAD, and constructing a physical model. It then provides an introduction to connecting rods, explaining that they connect the piston to the crankshaft and transmit reciprocating motion to rotational motion. The document discusses different manufacturing processes for connecting rods and compares technologies. It presents the design process for the connecting rod, showing calculations for dimensions. Examples are provided of both the CAD model and real constructed connecting rod.
A shaft is a rotating machine element which is used to transmit power from one place to another. with help of couplings or gears.
The shafts are usually cylindrical, but may be square or cross-shaped in section. They are solid in cross-section but
sometimes hollow shafts are also used.
Types of Shafts
The following two types of shafts are important from the subject point of view :
Transmission shafts. These shafts transmit power between the source and the machines absorbing power. The counter shafts, line shafts, over head shafts and all factory shafts are transmission shafts. Since these shafts carry machine parts such as pulleys, gears etc., therefore they are subjected to bending in addition to twisting.
2. Machine shafts. These shafts form an integral part of the machine itself. The crank shaft is an example of machine shaft.
Stresses in Shafts
The following stresses are induced in the shafts :
1. Shear stresses due to the transmission of torque (i.e. due to torsional load).
2. Bending stresses (tensile or compressive) due to the forces acting upon machine elements like gears, pulleys etc. as well as due to the weight of the shaft itself.
3. Stresses due to combined torsional and bending loads.
Material Used for Shafts
The material used for shafts should have the following properties :
1. It should have high strength.
2. It should have good machinability.
3. It should have low notch sensitivity factor.
4. It should have good heat treatment properties.
5. It should have high wear resistant properties.
The material used for ordinary shafts is carbon steel of grades 40 C 8, 45 C 8, 50 C 4 and 50 C 12.
The mechanical properties of these grades of carbon steel are given in the following table.
This document describes the design and construction of a connecting rod. It begins with the objectives of studying the connecting rod, understanding its function, designing it using CAD, and constructing a physical model. It then provides an introduction to connecting rods, explaining that they connect the piston to the crankshaft and transmit reciprocating motion to rotational motion. The document discusses different manufacturing processes for connecting rods and compares their strengths. It presents the design process for the connecting rod, showing calculations for dimensions. Examples are provided of both the CAD model and physical constructed connecting rod. Materials used and their properties are also outlined.
The document analyzes and compares three different configurations of 220kV transmission line towers: a square base self-supporting tower, a triangular base self-supporting tower, and a square base guyed mast tower. Each tower is modeled and analyzed using STAAD software. The triangular tower has the heaviest member sections for the legs to handle the same loads with fewer legs. The guyed mast tower has the lowest forces in the leg members due to load transfer through guy ropes. The triangular tower experiences the highest forces in the leg members. Overall, the triangular tower requires the heaviest member sections to support the same loads as the other tower configurations.
The document provides an overview of mechanics of materials concepts related to torsion, including:
- Torsion causes shearing stresses that vary linearly from zero at the center to a maximum at the surface for circular shafts.
- Torsion can cause both shearing stresses and normal stresses depending on the orientation of the material element.
- Ductile materials fail in shear while brittle materials fail in tension when subjected to torsion.
- The angle of twist is proportional to the applied torque, material properties, and shaft length based on elastic torsion formulas.
- Stress concentrations can occur due to geometric discontinuities and influence the maximum shearing stress.
ANALYSIS OF CNC LATHE SPINDLE FOR MAXIMUM CUTTING FORCE CONDITION AND BEARING...AM Publications
The present CNC machine structures consist of spindle system which plays a relating to the quality of the
final product and the overall productivity and efficiency of the machine tool itself. The spindle of a CNC lathe
machine, which is rotated by the main motor, holds the cutting tool, which cuts the work piece, so that the cutting
forces are generated which effects the spindle accuracy directly. The forces which are affecting the CNC machine tool
spindle are tangential force (Ft), feed force (Fc), radial force (Fr) and will be estimated. Based on maximum cutting
force incurred the analysis will be carried out. The main objective is to find the static, fatigue analysis of spindle
structure for maximum cutting force condition and predicting life of bearings. From static analysis stress and
deformation of the spindle can be found. Stress obtained from the stress analysis is less than the yield strength of the
material and deformation of the spindle is very less which can be neglected. Equivalent alternating stress, factor of
safety and life of the spindle is found by fatigue analysis and which results are closely matches with the analytical
value
This document describes the design and analysis of a high speed milling spindle to minimize deflection. Various spindle diameters and bearing configurations were considered, including duplex and triplet bearing arrangements. Static analysis was performed to calculate spindle nose deflection from bending and bearing elasticity. The optimum bearing span length that minimizes deflection was determined analytically and verified using ANSYS software. Results showed that bearing stiffness and span length significantly impact spindle deflection, with shorter spans and higher stiffness bearings reducing deflection.
The main objective of project is to understand the working of cone
type CVT which offers a continuum of gear ratios between the fixed
desired limits . It includes the analysis of
1) Design of CVT.
2) Fabrication of CVT model.
3) Performance analysis and testing
The document analyzes the crankshaft of a single cylinder four stroke engine using ANSYS software to determine the optimal material. Three materials were considered for the crankshaft: structural steel, aluminum alloy, and nickel chromium molybdenum steel. The crankshaft was modeled in SolidWorks and imported into ANSYS for stress analysis. Von Mises stress and total deformation were compared for each material. The results showed that aluminum alloy had the lowest von Mises stress of 146.28 MPa, making it the strongest and best material candidate for withstanding the loads on the crankshaft.
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Unit 2 Design Of Shafts Keys and Couplings
1. Unit 2
Design of Shafts, Keys & Couplings
Prepared By
Prof. M.C. Shinde [9970160753]
Mech. Engg. Dept., JSCOE, Hadapsar
2. Unit 2
Design of Shafts ,Keys & Couplings
Session 2.1 Introduction to Transmission Shaft
Prepared By
Prof. M.C. Shinde
Mech. Engg. Dept., JSCOE, Hadapsar
3. SPPU Syllabus Content
• Shaft design on the basis of strength, torsional rigidity and lateral rigidity,
A.S.M.E. code for shaft design. Transmission shaft:- Theoretical treatment
only. Design of keys and splines. Design of Flange Coupling and Flexible
Bushed Pin Coupling.
4. Transmission Shafts
• Rotating member, usually of circular cross section used to
transmit power or motion.
• supports transmission elements like gears, pulleys and sprockets.
• A transmission shaft supporting a gear in a speed reducer is
shown in Fig.
• The shaft is always stepped with maximum diameter in the
middle.
• portion and minimum diameter at the two ends, where bearings
are mounted.
5. • transmission shafts are made of medium carbon steels with a carbon content
from 0.15 to 0.40 per cent such as 30C8 or 40C8.
• Commercial shafts are made of low carbon steels.
• produced by hot-rolling and finished to size either by cold-drawing or by
turning and grinding.
• Steel bars up to 200 mm in diameter are commercially available.
6. Specific Categories Of Transmission Shafts
• Axle-supports rotating elements like wheels, hoisting drums. Used in
rear axle of a railway wagon, automobile rear axle.
7. Specific Categories Of Transmission Shafts
• Spindle- A spindle is a short rotating shaft , used in all machine tools
such as the small drive shaft of a lathe or the spindle of a drilling
machine.
8. Specific Categories Of Transmission Shafts
• Countershaft It is a secondary shaft, driven by the main shaft and
from which the power is supplied to a machine component. rotates
‘counter’ to the direction of the main shaft. used in multi-stage
gearboxes.
9. Stresses induced in the shaft
• Transmission shafts are subjected to axial tensile force, bending moment or
torsional moment or their combinations.
• tensile stress
• bending stresses
• torsional shear stress
When the shaft is subjected to combination of loads, the principal stress and
principal shear stress are obtained by constructing Mohr’s circle
10.
11. Shaft Design On Strength Basis
1. Design of shaft by theories of failures
2. Design of shaft by A.S.M.E. Code
12. 1.Shaft Design by theories of failures
i] Maximum Shear Stress Theory:- the shaft is subjected to bending and
torsional moments
These equations are used to determine shaft diameter on the basis of
maximum shear stress theory.
The maximum shear stress theory is applicable to ductile materials. Since the
shafts are made of ductile materials, it is more logical to apply this theory to
shaft design.
13. ii] Maximum Principal Stress Theory:- the shaft is subjected to bending and
torsional moments
These equations are used to determine shaft diameter on the basis of principal
stress theory
maximum principal stress theory gives good predictions for brittle materials.
Shafts are made of ductile material like steel and therefore, this theory is not
applicable to shaft design.
14. iii] Distortion Energy Theory:- the shaft is subjected to bending and torsional
moments
These equations are used to determine shaft diameter on the basis of
distortion energy theory.
The maximum shear stress theory is applicable to ductile materials. The design
of shaft by distortion energy theory is very accurate. Hence distortion energy
theory is most widely theory used for shaft design.
15. 2. Shaft Design by A.S.M.E. CODE
A.S.M.E. code used for design of shaft is based on maximum shear stress
theory.
According to A.S.M.E. code the values of allowable shear stress are as follows;
[without keyway] take minimum of two values
According to A.S.M.E. code the values of allowable shear stress are as follows;
[with keyway] take minimum of two values
Note :- the keyway on the shaft reduces the strength of the shaft. This is due
to stress concentration near corners of keyway.
16. Shaft Design On Rigidity Basis
1. Design of shaft based on Torsional Rigidity
2. Design of shaft based on Lateral Rigidity
17. 1. Design of shaft based on Torsional Rigidity
Torsional rigidity is defined as “ torque required to produce a torsional
deflection or an angle of twist of one radian in the shaft.”
This equation is used to design the shaft on the basis of torsional rigidity.
The permissible angle of twist for machine tool applications is 0.25° per metre
length. For line shafts, 3° per metre length is the limiting value. Modulus of
rigidity for steel is 79 300 N/mm2
18. 2. Design of shaft based on Lateral Rigidity
Lateral rigidity of the shaft at given location is “the lateral force required to
produce a lateral deflection of one unit”.
This equation is used to design the shaft on the basis of lateral rigidity.
e.g. for cantilever beam maximum
deflection is given by,
19. Q.1 What are different materials used for manufacturing of shafts.
Q.2 What are stresses induced in the transmission shafts.
Q.3 Write down formula to design shaft using ASME Code.
Assignment 2.1
20. Unit 2
Design of Shafts ,Keys & Couplings
Session 2.2 Numerical on Design of Shafts
Prepared By
Prof. M.C. Shinde
Mech. Engg. Dept., JSCOE, Hadapsar
21. Ex.1 A mild steel shaft transmits 20kW power at 200 r.p.m. If the
allowable shear stress for shaft material in 42 Mpa , determine the
diameter of shaft.
22. Ex. 2. A mild steel shaft transmits 20kW power at 200 r.p.m.it carries a central
load of 1000 N and is simply supported between bearings 2.5m apart. The
allowable shear stress for shaft material in 42 Mpa. If the shock & fatigue factors
for bending and torsion are 1.5 and 1.0, determine the diameter of shaft by
maximum shear stress theory.
23. A mild steel shaft transmits 40kW power at 400 r.p.m.it carries a
central load of 2000 N and is simply supported between bearings 5m
apart. The allowable shear stress for shaft material in 84 Mpa. If the
shock & fatigue factors for bending and torsion are 1.5 and 1.0,
determine the diameter of shaft by maximum shear stress theory
Assignment 2.2
24. Unit 2
Design of Shafts ,Keys & Couplings
Session 2.3 Numerical on Design of Shafts based on
Maximum Shear Stress Theory
Prepared By
Prof. M.C. Shinde
Mech. Engg. Dept., JSCOE, Hadapsar
25. Ex. 3. A counter shaft with the bearings 800 mm apart receives 20kW power at 500 rpm
through a pulley 300mm in diameter and mounted at an overhung of 200 mm. A 360 mm
diameter pulley mounted midway between the bearings transmits torque to a shaft located
below it. Both the pulleys have vertical belt tensions and the coefficient of friction between the
bell and pulley is 0.3. if the required safety margin is 3. design the shaft using maximum shear
stress theory Use the following properties for shaft material.
1. Ultimate tensile strength=700 N/mm2,
2. Yield strength in tension=460 N/mm2
Important : Keep
Calculator with you
for solve problem]
33. Step IV Maximum Shear Stress Theory
Note:- Assume Kb = Kt = 1
34.
35. A counter shaft with the bearings 1000 mm apart receives 220kW
power at 1000 rpm through a pulley 600mm in diameter and
mounted at an overhung of 400 mm. A 720 mm diameter pulley
mounted midway between the bearings transmits torque to a shaft
located below it. Both the pulleys have vertical belt tensions and the
coefficient of friction between the bell and pulley is 0.6. if the required
safety margin is 6. design the shaft using maximum shear stress
theory .
Use the following properties for shaft material.
Ultimate tensile strength=800 N/mm2,
Yield strength in tension=360 N/mm2
Assignment 2.3
36. Unit 2
Design of Shafts ,Keys & Couplings
Session 2.4 Numerical on Design of Shafts based on
ASME Code
Prepared By
Prof. M.C. Shinde
Mech. Engg. Dept., JSCOE, Hadapsar
37. Ex. 5. A transmission shaft is supporting a spur gear B and pulley D, as shown in fig. The shaft is
mounted on two bearings A & C. the diameter of pulley and gear are 500 mm and 350 mm
respect. A 20kW power is transmitted at 500 r.p.m. from the pulley D to the gear B. F1 & F2 are
the belt tensions in the tight and slack sides, while Ft & Fr are tangential and radial components
of the gear tooth forces. Assume F1=3F2 and Fr=Ft tan 20. the gear and pulley are keyed to the
shaft. If the material for the shaft is 50C4(Sut=700 N/mm2 and Syt= 460 N/mm2), determine
the shaft diameter using ASME code, if Kb=Kt=1.5
49. Assignment 2.4
A transmission shaft is supporting a spur gear B and pulley D, as shown in fig. The shaft is
mounted on two bearings A & C. the diameter of pulley and gear are 700 mm and 350 mm
respect. A 40kW power is transmitted at 1000 r.p.m. from the pulley D to the gear B. F1 & F2
are the belt tensions in the tight and slack sides, while Ft & Fr are tangential and radial
components of the gear tooth forces. Assume F1=3F2 and Fr=Ft tan 20. the gear and pulley
are keyed to the shaft. If the material for the shaft is 50C4(Sut=500 N/mm2 and Syt= 260
N/mm2), determine the shaft diameter using ASME code, if Kb=Kt=1.0
50. Unit 2
Design of Shafts ,Keys & Couplings
Session 2.5 Numerical on Design of Shafts
Prepared By
Prof. M.C. Shinde
Mech. Engg. Dept., JSCOE, Hadapsar
51. Ex. 6. The layout of an intermediate shaft of a gear box, supporting two spur
gears B & C ,is shown in fig. the shaft is mounted on two bearings A & D. the pitch
circle diameter of gears B & C are 900mm & 600mm respect. The material of the
shaft is steel FeE 580(Sut=770N/mm2 & Syt=580N/mm2). The factors Kb & Kt are
1.5 & 2.0 respectively . Determine the shaft diameter using the ASME code.
Assume that the gears are connected to the shaft by means of keys.
61. Assignment 2.5
The layout of an intermediate shaft of a gear box, supporting two spur gears B
& C ,is shown in fig. the shaft is mounted on two bearings A & D. the pitch circle
diameter of gears B & C are 900mm & 600mm respect. The material of the shaft
is steel FeE 580(Sut=770N/mm2 & Syt=580N/mm2). The factors Kb & Kt are 1.5
& 2.0 respectively . Determine the shaft diameter using the ASME code. Assume
that the gears are connected to the shaft by means of keys.
62. Unit 2
Design of Shafts ,Keys & Couplings
Session 2.6 Numerical on Design of Shafts
Prepared By
Prof. M.C. Shinde
Mech. Engg. Dept., JSCOE, Hadapsar
63. Ex. 4. The shaft shown in fig. is driven by pulley D from an electric motor, while another belt
drive from pulley C is running a compressor. The belt tensions for pulley C are 1500 N & 600 N,
while the ratio of belt tensions for pulley D is 3.5. find the shaft diameter by A.S.M.E. code. Yield
strength and ultimate tensile strength for shaft material are 380 N/mm2 and 720 N/mm2
respectively. Take Kb=1.75 and Kt=1.25.
64. Step I Permissible shear stress [ASME]
Note:- Assume Shaft with keyway effect
74. Assignment 2.6
The shaft shown in fig. is driven by pulley D from an electric motor, while another belt drive
from pulley C is running a compressor. The belt tensions for pulley C are 3000 N & 1200 N,
while the ratio of belt tensions for pulley D is 2.5. find the shaft diameter by A.S.M.E. code.
Yield strength and ultimate tensile strength for shaft material are 420 N/mm2 and 720
N/mm2 respectively. Take Kb=1. 5 and Kt=1.05.
75.
76. Unit 2
Design of Shafts ,Keys & Couplings
Session 2.7 Design of Splined Shafts & Design of Keys
Prepared By
Prof. M.C. Shinde
Mech. Engg. Dept., JSCOE, Hadapsar
78. Splines
• Multiple keys which are made integral with the shaft.
• Prevent the relative rotary motion ,but permit the relative axial motion
between the shaft and hub.
• Splines transmit much higher torque than the single key between the shaft
and hub.
• Used in automobile gear boxes and machine tool gear boxes.
• Splines are designated as N*d*D;
N- no. Of splines
D- Major diameter of splined shaft(mm)
d- minor diameter of splined shaft(mm)
79. Design of Splines
• As there exists a relative axial motion between the splined shaft and the hub, the
bearing pressure between the external splines on shaft and the internal splines
on hub must be considered.
82. Ex. 9. A standard splined connection 8*52*60mm is used for the gear and shaft
assembly of gear box. A 20kW power at 300 r.p.m. is transmitted by the splines. If
the normal pressure on the splines is limited to 6.5 N/mm2 and the coefficient of
friction is 0.06. calculate:
i) The length of hub of the gear
ii) The force required to shift the gear
Given
88. Keys
• A machine element which is used to connect
the transmission shaft to rotating machine
elements like pulleys, gears, sprockets or
flywheels.
• A keyed joint consisting of shaft, hub and key
• The primary function of the key is to transmit
the torque from the shaft to the hub of the
mating element and vice versa
• The second function of the key is to prevent
relative rotational motion between the shaft
and the joined machine element like gear or
pulley.
• A recess or slot machined either on the shaft
or in the hub to accommodate the key is
called keyway
90. Sunk keys:-
• A sunk key is a key in which half the thickness of the key fits into the keyway on the
shaft and the remaining half in the keyway on the hub.
• keyways are required both on the shaft as well as the hub of the mating element.
• In sunk key, power is transmitted due to shear resistance of the key.
• sunk key is suitable for heavy duty application, since there is no possibility of the key
to slip around the shaft.
• A sunk key with rectangular cross-section is
called a flat key.
a) Rectangular key
b) Square key
c) Parallel key
d) Gib headed key
e) Feather key
f) Woodruff key
93. Crushing or compressive stress in key
Note:- compressive stress induced in a square key due to torque transmitted is
twice the shear stress.
94. Ex. 7. A square key is to be used to fix a gear to a 35 mm diameter shaft. The hub
length of the gear is 60mm. Both the shaft and key are to be made of the same
material, having an allowable shear stress of 55 N/mm2. if the torque to be
transmitted is 395 N-m. determine the minimum dimensions of key cross section.
Given
To find dimensions of key cross section.
96. Ex. 8. A 16*10 mm2 cross section parallel key is to be used to transmit 60kW
power at 1440 rpm from a shaft of 45mm diameter. The key is made of plain
carbon steel with yield strength of 300 N/mm2. if the required safety margin is 3,
determine the key length.
Given
To find length of key cross section.
101. Assignment 2.7
1. Explain Splined shaft with neat sketch
2. What is key? Explain different types of keys
3. Write stresses induced in the keys with equations.
4. A standard splined connection 4*26*30mm is used for the gear and shaft
assembly of gear box. A 50kW power at 800 r.p.m. is transmitted by the
splines. If the normal pressure on the splines is limited to 8.5 N/mm2 and the
coefficient of friction is 0.06. calculate: a) The length of hub of the gear b)
The force required to shift the gear
102. Unit 2
Design of Shafts ,Keys & Couplings
Session 2.8 Introduction ,Classification of Couplings &
Design of muff coupling
Prepared By
Prof. M.C. Shinde
Mech. Engg. Dept., JSCOE, Hadapsar
103. Couplings
• It is the mechanical element used to connect two shafts of a transmission system.
• The couplings are located as near as possible to bearing so as to minimize
deflection.
• mechanical device that permanently joins two rotating shafts to each other.
104. Purposes of Couplings
• It provides for the connection of shafts of two different units such as an electric
motor and machine.
• It makes the provision for disconnection of two units for repairs or alternations.
• It introduces mechanical flexibility between two connected units.
• It reduces the transmission of vibrations and shocks between two connected
units.
105. Rigid Couplings Flexible Couplings
Used to connect two shafts which are
perfectly aligned
Used to connect two shafts which are
having small misalignment.
Cannot tolerate any misalignment
between two shafts
Can tolerate small amount of lateral
or and angular misalignment
between two shafts
Cannot absorb shock & vibrations Can absorb shock & Vibrations
Less expensive More expensive
e.g. muff coupling, split muff, rigid
flange
e.g. bushed pin type, oldham
coupling and universal coupling
106. Couplings
Rigid Couplings
Muff/Sleeve
Coupling
Used for Line
Shaft
Split
Muff/Clamp
Coupling
Used for Line
Shaft
Rigid Flange
Coupling
Used for
connecting
electric motor
to pump
Flexible
Couplings
Bushed Pin
Type
Used for
connecting
diesel engine
to generator
Oldham
Coupling
Used for
connecting two
eccentric
shafts
Universal
Coupling
Used between
gear box and
differential of
automobile
107. Design of Muff (Sleeve) Couplings
• It is the simplest type of rigid coupling used to connect two shafts rigidly.
• Design of Muff coupling involve following steps
1. Design of Shaft
2. Dimensions of sleeve as standard proportions
3. Design of sleeve
4. Design of key
108. Design of Muff (Sleeve) Couplings
Step 1: Design of Shaft
• Same as discussed in earlier session 2.1 & 2.2
109. Design of Muff (Sleeve) Couplings
Step 2: Dimensions of sleeve as standard proportions
• Outside diameter of sleeve D=2d
• Length of Sleeve L=3.5d
Where , d=diameter of shaft, mm
110. Design of Muff (Sleeve) Couplings
Step 3: Design of Sleeve
• Torsional Shear Stress induced in Sleeve is given by
Where ,k=d/D
For the safety of sleeve against shear failure ,the torsional shear stress induced in a
sleeve must be less than allowable shear stress for sleeve i.e.
111. Design of Muff (Sleeve) Couplings
Step 4: Design of Key
• The key dimensions are calculated as discussed in design of key session
• For design purpose length of key is taken as l=L/2
112. Assignment 2.8
1. Give Classification of Couplings
2. Explain steps for design of muff couplings.
3. Differentiate between Rigid and Flexible Couplings
113. Unit 2
Design of Shafts ,Keys & Couplings
Session 2.9 Design of Rigid Flange Coupling &
Numericals
Prepared By
Prof. M.C. Shinde
Mech. Engg. Dept., JSCOE, Hadapsar
114. Design of Rigid Flange Couplings
A rigid flange coupling consist of two flanges one keyed to the driver shaft and
other to driven shaft.
Types of Rigid Flange Coupling
1.Unprotected type rigid flange coupling
2. Protected type rigid flange coupling
3. Marine type rigid flange coupling
115. Ex. A protected type rigid flange coupling is used to transmit 25kW power at 500
rpm from an engine to a machine. Design a coupling for an overload capacity of
25% .Assume following permissible stresses for components of coupling. Assume
number of bolts as 6.
116. d-diameter of shaft, mm
D-Outer diameter of hub ,mm
D1- diameter of bolt circle ,mm
D2- outer diameter of flange, mm
D3- diameter of flange recess, mm
l-length of hub, mm
tf- thickness of flange, mm
tp- thickness of protective flange, mm
db- nominal diameter of bolt, mm
N- no. of bolts
123. Step 3. Design of key
Selecting largest of three values of length(l)
124. Step 4. Design of hub
Length of hub , l=79 mm
Outer diameter of hub, D=2d= 2*45=90 mm
Shear stress induced in hub given by
Hence, hub is safe against shear failure
125. Step 5. Design of flange
Thickness of flange,
Thickness of protective flange,
Diameter of bolt circle,
Outer diameter of flange,
Diameter of flange recess,
126. Step 5. Design of flange
Direct shear stress induced in a flange at junction with hub is
Hence flange is safe against shear failure
127. Step 6. Design of bolts
a. Considering Shearing of bolt
128. Step 6. Design of bolts
b. Considering Crushing of bolt
130. Assignment 2.9
1. Design a flange coupling for steel shaft transmitting 20kW power at 250
r.p.m. the maximum torque is 30% greater than full load torque. The
material properties are as follow:
• Allowable shear stress for shaft and key =40MPa
• Allowable shear stress for bolts =30MPa
• Allowable crushing stress for shaft & key =80MPa
• Allowable shear stress for flange =14MPa
• Allowable compressive stress for bolts =60MPa
• Number of bolts =4
132. Ex.1 A transmission shaft supporting a helical gear B and an overhung bevel gear D is shown in Fig. The shaft is
mounted on two bearings, A and C. The pitch circle diameter of the helical gear is 450 mm and the diameter of the
bevel gear at the forces is 450 mm. Power is transmitted from the helical gear to the bevel gear. The gears are
keyed to the shaft. The material of the shaft is steel 45C8 (Sut = 600 and Syt = 380 N/ mm2). The factors kb and kt
of ASME code are 2.0 and 1.5 respectively. Determine the shaft diameter using the ASME code.
133. Ex.2. The armature shaft of a 40 kW, 720 rpm electric motor, mounted on two bearings A and B, is shown in Fig.
The total magnetic pull on the armature is 7 kN and it can be assumed to be uniformly distributed over a length of
700 mm midway between the bearings. The shaft is made of steel with an ultimate tensile strength of 770 N/mm2
and yield strength of 580 N/mm2. Determine the shaft diameter using the ASME code if, kb = 1.5 and kt = 1.0
Assume that the pulley is keyed to the shaft.
134. Ex.3. It is required to design a square key for fixing a gear on a shaft of 25 mm diameter. The
shaft is transmitting 15 kW power at 720 rpm to the gear. The key is made of steel 50C4 (Syt =
460 N/mm2) and the factor of safety is 3. For key material, the yield strength in compression
can be assumed to be equal to the yield strength in tension. Determine the dimensions of the
key.
Ex.4. The standard cross-section for a flat key, which is fitted on a 50 mm diameter shaft, is 16 *
10 mm. The key is transmitting 475 N-m torque from the shaft to the hub. The key is made of
commercial steel (Syt = Syc = 230 N/mm2).Determine the length of the key, if the factor of
safety is 3.