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.
ME010 801 Design of Transmission Elements
(Common with AU010 801)
Teaching scheme Credits: 4
2 hours lecture, 2 hour tutorial and 1 hour drawing per week
Objectives
To provide basic design skill with regard to various transmission elements like clutches, brakes, bearings and
gears.
Module I (20 Hrs)
Clutches - friction clutches- design considerations-multiple disc clutches-cone clutch- centrifugal clutch -
Brakes- Block brake- band brake- band and block brake-internal expanding shoe brake.
Module II (17 Hrs)
Design of bearings - Types - Selection of a bearing type - bearing life - Rolling contact bearings - static
and dynamic load capacity - axial and radial loads - selection of bearings - dynamic equivalent load -
lubrication and lubricants - viscosity - Journal bearings - hydrodynamic theory - design considerations -
heat balance - bearing characteristic number - hydrostatic bearings.
Module III (19 Hrs)
Gears- classification- Gear nomenclature - Tooth profiles - Materials of gears - design of spur, helical,
bevel gears and worm & worm wheel - Law of gearing - virtual or formative number of teeth- gear tooth
failures- Beam strength - Lewis equation- Buckingham’s equation for dynamic load- wear loadendurance strength of tooth- surface durability- heat dissipation - lubrication of gears - Merits and
demerits of each type of gears.
Module IV (16 Hrs)
Design of Internal Combustion Engine parts- Piston, Cylinder, Connecting rod, Flywheel
Design recommendations for Forgings- castings and welded products- rolled sections- turned parts,
screw machined products- Parts produced on milling machines. Design for manufacturing - preparation
of working drawings - working drawings for manufacture of parts with complete specifications including
manufacturing details.
Note: Any one of the following data book is permitted for reference in the final University examination:
1. Machine Design Data hand book by K. Lingaiah, Suma Publishers, Bangalore/ Tata Mc Graw Hill
2. PSG Design Data, DPV Printers, Coimbatore.
Text Books
1. C.S,Sarma, Kamlesh Purohit, Design of Machine Elements Prentice Hall of India Ltd NewDelhi
2. V.B.Bhandari, Design of Machine Elements McGraw Hill Book Company
3. M. F. Spotts, T. E. Shoup, Design of Machine Elements, Pearson Education.
Reference Books
1. J. E. Shigley, Mechanical Engineering Design, McGraw Hill Book Company.
2. Juvinall R.C & Marshek K.M., Fundamentals of Machine Component Design, John Wiley
3. Doughtie V.L., & Vallance A.V., Design of Machine Elements, McGraw Hill Book Company.
4. Siegel, Maleev & Hartman, Mechanical Design of Machines, International Book Company
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.
ME010 801 Design of Transmission Elements
(Common with AU010 801)
Teaching scheme Credits: 4
2 hours lecture, 2 hour tutorial and 1 hour drawing per week
Objectives
To provide basic design skill with regard to various transmission elements like clutches, brakes, bearings and
gears.
Module I (20 Hrs)
Clutches - friction clutches- design considerations-multiple disc clutches-cone clutch- centrifugal clutch -
Brakes- Block brake- band brake- band and block brake-internal expanding shoe brake.
Module II (17 Hrs)
Design of bearings - Types - Selection of a bearing type - bearing life - Rolling contact bearings - static
and dynamic load capacity - axial and radial loads - selection of bearings - dynamic equivalent load -
lubrication and lubricants - viscosity - Journal bearings - hydrodynamic theory - design considerations -
heat balance - bearing characteristic number - hydrostatic bearings.
Module III (19 Hrs)
Gears- classification- Gear nomenclature - Tooth profiles - Materials of gears - design of spur, helical,
bevel gears and worm & worm wheel - Law of gearing - virtual or formative number of teeth- gear tooth
failures- Beam strength - Lewis equation- Buckingham’s equation for dynamic load- wear loadendurance strength of tooth- surface durability- heat dissipation - lubrication of gears - Merits and
demerits of each type of gears.
Module IV (16 Hrs)
Design of Internal Combustion Engine parts- Piston, Cylinder, Connecting rod, Flywheel
Design recommendations for Forgings- castings and welded products- rolled sections- turned parts,
screw machined products- Parts produced on milling machines. Design for manufacturing - preparation
of working drawings - working drawings for manufacture of parts with complete specifications including
manufacturing details.
Note: Any one of the following data book is permitted for reference in the final University examination:
1. Machine Design Data hand book by K. Lingaiah, Suma Publishers, Bangalore/ Tata Mc Graw Hill
2. PSG Design Data, DPV Printers, Coimbatore.
Text Books
1. C.S,Sarma, Kamlesh Purohit, Design of Machine Elements Prentice Hall of India Ltd NewDelhi
2. V.B.Bhandari, Design of Machine Elements McGraw Hill Book Company
3. M. F. Spotts, T. E. Shoup, Design of Machine Elements, Pearson Education.
Reference Books
1. J. E. Shigley, Mechanical Engineering Design, McGraw Hill Book Company.
2. Juvinall R.C & Marshek K.M., Fundamentals of Machine Component Design, John Wiley
3. Doughtie V.L., & Vallance A.V., Design of Machine Elements, McGraw Hill Book Company.
4. Siegel, Maleev & Hartman, Mechanical Design of Machines, International Book Company
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.
A helical gear has teeth in form of helix around the gear. Two such gears may be used to connect two parallel shafts in place of spur gears. The helixes may be right handed on one gear and left handed on the other. The pitch surfaces are cylindrical as in spur gearing, but the teeth instead of being parallel to the axis, wind around the cylinders helically like screw threads.
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
A helical gear has teeth in form of helix around the gear. Two such gears may be used to connect two parallel shafts in place of spur gears. The helixes may be right handed on one gear and left handed on the other. The pitch surfaces are cylindrical as in spur gearing, but the teeth instead of being parallel to the axis, wind around the cylinders helically like screw threads.
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
SEMINAR @Design And Analysis Of A Connecting Rod With Different MaterialsDr.M BALA THEJA
Internal Combustion engine has many parts like cylinder, piston, connecting rod, crank and crank shaft. The connecting rod is very important part of an engine.
The connecting rod is very important part of an engine. Working of the connecting rod is to transmit power of piston to crank pin.
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.
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
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
Courier management system project report.pdfKamal Acharya
It is now-a-days very important for the people to send or receive articles like imported furniture, electronic items, gifts, business goods and the like. People depend vastly on different transport systems which mostly use the manual way of receiving and delivering the articles. There is no way to track the articles till they are received and there is no way to let the customer know what happened in transit, once he booked some articles. In such a situation, we need a system which completely computerizes the cargo activities including time to time tracking of the articles sent. This need is fulfilled by Courier Management System software which is online software for the cargo management people that enables them to receive the goods from a source and send them to a required destination and track their status from time to time.
COLLEGE BUS MANAGEMENT SYSTEM PROJECT REPORT.pdfKamal Acharya
The College Bus Management system is completely developed by Visual Basic .NET Version. The application is connect with most secured database language MS SQL Server. The application is develop by using best combination of front-end and back-end languages. The application is totally design like flat user interface. This flat user interface is more attractive user interface in 2017. The application is gives more important to the system functionality. The application is to manage the student’s details, driver’s details, bus details, bus route details, bus fees details and more. The application has only one unit for admin. The admin can manage the entire application. The admin can login into the application by using username and password of the admin. The application is develop for big and small colleges. It is more user friendly for non-computer person. Even they can easily learn how to manage the application within hours. The application is more secure by the admin. The system will give an effective output for the VB.Net and SQL Server given as input to the system. The compiled java program given as input to the system, after scanning the program will generate different reports. The application generates the report for users. The admin can view and download the report of the data. The application deliver the excel format reports. Because, excel formatted reports is very easy to understand the income and expense of the college bus. This application is mainly develop for windows operating system users. In 2017, 73% of people enterprises are using windows operating system. So the application will easily install for all the windows operating system users. The application-developed size is very low. The application consumes very low space in disk. Therefore, the user can allocate very minimum local disk space for this application.
Hybrid optimization of pumped hydro system and solar- Engr. Abdul-Azeez.pdffxintegritypublishin
Advancements in technology unveil a myriad of electrical and electronic breakthroughs geared towards efficiently harnessing limited resources to meet human energy demands. The optimization of hybrid solar PV panels and pumped hydro energy supply systems plays a pivotal role in utilizing natural resources effectively. This initiative not only benefits humanity but also fosters environmental sustainability. The study investigated the design optimization of these hybrid systems, focusing on understanding solar radiation patterns, identifying geographical influences on solar radiation, formulating a mathematical model for system optimization, and determining the optimal configuration of PV panels and pumped hydro storage. Through a comparative analysis approach and eight weeks of data collection, the study addressed key research questions related to solar radiation patterns and optimal system design. The findings highlighted regions with heightened solar radiation levels, showcasing substantial potential for power generation and emphasizing the system's efficiency. Optimizing system design significantly boosted power generation, promoted renewable energy utilization, and enhanced energy storage capacity. The study underscored the benefits of optimizing hybrid solar PV panels and pumped hydro energy supply systems for sustainable energy usage. Optimizing the design of solar PV panels and pumped hydro energy supply systems as examined across diverse climatic conditions in a developing country, not only enhances power generation but also improves the integration of renewable energy sources and boosts energy storage capacities, particularly beneficial for less economically prosperous regions. Additionally, the study provides valuable insights for advancing energy research in economically viable areas. Recommendations included conducting site-specific assessments, utilizing advanced modeling tools, implementing regular maintenance protocols, and enhancing communication among system components.
CFD Simulation of By-pass Flow in a HRSG module by R&R Consult.pptxR&R Consult
CFD analysis is incredibly effective at solving mysteries and improving the performance of complex systems!
Here's a great example: At a large natural gas-fired power plant, where they use waste heat to generate steam and energy, they were puzzled that their boiler wasn't producing as much steam as expected.
R&R and Tetra Engineering Group Inc. were asked to solve the issue with reduced steam production.
An inspection had shown that a significant amount of hot flue gas was bypassing the boiler tubes, where the heat was supposed to be transferred.
R&R Consult conducted a CFD analysis, which revealed that 6.3% of the flue gas was bypassing the boiler tubes without transferring heat. The analysis also showed that the flue gas was instead being directed along the sides of the boiler and between the modules that were supposed to capture the heat. This was the cause of the reduced performance.
Based on our results, Tetra Engineering installed covering plates to reduce the bypass flow. This improved the boiler's performance and increased electricity production.
It is always satisfying when we can help solve complex challenges like this. Do your systems also need a check-up or optimization? Give us a call!
Work done in cooperation with James Malloy and David Moelling from Tetra Engineering.
More examples of our work https://www.r-r-consult.dk/en/cases-en/
Vaccine management system project report documentation..pdfKamal Acharya
The Division of Vaccine and Immunization is facing increasing difficulty monitoring vaccines and other commodities distribution once they have been distributed from the national stores. With the introduction of new vaccines, more challenges have been anticipated with this additions posing serious threat to the already over strained vaccine supply chain system in Kenya.
Immunizing Image Classifiers Against Localized Adversary Attacksgerogepatton
This paper addresses the vulnerability of deep learning models, particularly convolutional neural networks
(CNN)s, to adversarial attacks and presents a proactive training technique designed to counter them. We
introduce a novel volumization algorithm, which transforms 2D images into 3D volumetric representations.
When combined with 3D convolution and deep curriculum learning optimization (CLO), itsignificantly improves
the immunity of models against localized universal attacks by up to 40%. We evaluate our proposed approach
using contemporary CNN architectures and the modified Canadian Institute for Advanced Research (CIFAR-10
and CIFAR-100) and ImageNet Large Scale Visual Recognition Challenge (ILSVRC12) datasets, showcasing
accuracy improvements over previous techniques. The results indicate that the combination of the volumetric
input and curriculum learning holds significant promise for mitigating adversarial attacks without necessitating
adversary training.
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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.