This document summarizes the design of a cotter joint to connect two rods subjected to an axial tensile load of 28kN. It outlines the 10 potential failure modes of the joint and provides the equations to size each component based on the material properties. An example solution is then provided to design a cotter joint with a rod diameter of 30mm based on allowable stresses of 50MPa (tension), 60MPa (compression), and 35MPa (shear). Component sizes such as the spigot diameter, socket diameter, cotter thickness, and collar dimensions are calculated.
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
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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
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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.
Theory of metal cutting MG University(S8 Production Notes)Denny John
Theory of metal cutting MG University(S8 Production Notes)
Scenario of manufacturing process – Deformation of metals,
Schmid’s law (review only) – Performance and process parameters – single point cutting
tool nomenclature - attributes of each tool nomenclature - attributes of feed and tool
signature on surface roughness obtainable, role of surface roughness on crack initiation -
Oblique and orthogonal cutting – Mechanism of metal removal - Primary and secondary
deformation shear zones - Mechanism of chip formation, card model, types of chip,
curling of chips, flow lines in a chip, BUE, chip breakers, chip thickness ratio –
Mechanism of orthogonal cutting: Thin zone and thick zone, Merchant’s analysis – shear
angle relationship, Lee and Shaffer`s relationship, simple problems – Friction process in
metal cutting: nature of sliding friction, columb`s law, adhesion theory, ploughing, sublayer
flow – Empirical determination of force component.
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.
Theory of metal cutting MG University(S8 Production Notes)Denny John
Theory of metal cutting MG University(S8 Production Notes)
Scenario of manufacturing process – Deformation of metals,
Schmid’s law (review only) – Performance and process parameters – single point cutting
tool nomenclature - attributes of each tool nomenclature - attributes of feed and tool
signature on surface roughness obtainable, role of surface roughness on crack initiation -
Oblique and orthogonal cutting – Mechanism of metal removal - Primary and secondary
deformation shear zones - Mechanism of chip formation, card model, types of chip,
curling of chips, flow lines in a chip, BUE, chip breakers, chip thickness ratio –
Mechanism of orthogonal cutting: Thin zone and thick zone, Merchant’s analysis – shear
angle relationship, Lee and Shaffer`s relationship, simple problems – Friction process in
metal cutting: nature of sliding friction, columb`s law, adhesion theory, ploughing, sublayer
flow – Empirical determination of force component.
Design analysis of Cotter joint used in piston rod and crosshead a.pptx138HemangiAhire
Design analysis of Cotter joint
used in piston rod and crosshead
1.Abstract
2.Introduction
3.Literature survey
4.Design of cotter joint
5.Cotter joint to connect piston rod and crosshead
6.Example problem statement
7.3d modelling of cotter joint
8.Analysis of cotter joint
9.Result and discussion
10.Conclusion
11.Suggestion for future
12.References
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A hierarchical digital twin of a Naval DC power system has been developed and experimentally verified. Similar to other state-of-the-art digital twins, this technology creates a digital replica of the physical system executed in real-time or faster, which can modify hardware controls. However, its advantage stems from distributing computational efforts by utilizing a hierarchical structure composed of lower-level digital twin blocks and a higher-level system digital twin. Each digital twin block is associated with a physical subsystem of the hardware and communicates with a singular system digital twin, which creates a system-level response. By extracting information from each level of the hierarchy, power system controls of the hardware were reconfigured autonomously. This hierarchical digital twin development offers several advantages over other digital twins, particularly in the field of naval power systems. The hierarchical structure allows for greater computational efficiency and scalability while the ability to autonomously reconfigure hardware controls offers increased flexibility and responsiveness. The hierarchical decomposition and models utilized were well aligned with the physical twin, as indicated by the maximum deviations between the developed digital twin hierarchy and the hardware.
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(C) 2024 Robbie E. Sayers
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1. Subject :- Machine Design And Industrial Drafting
Topic :- Design of cotter joint
•Made By :-
-Utkarsh Gandhi -150990119007
-Digvijaysinh Gohil-150990119008
-Jaimin Prajapati-150990119010
-Abhijitsinh Kher-150990119012
•Guided By :-
-Mr. Rudra Parmar
2. COTTER JOINT
•A cotter joint is used to connect rigidly two co-axial rods or bars which
are subjected to axial tensile or compressive forces . It is a temporary
fastening.
• A cotter is a flat wedge shaped piece of rectangular cross section and its
width is tapered (either on one side or on both sides) from one end to
another for an easy adjustment.
.
Socket Cotter
Spigot
3. APPLICATIONS OF COTTER
1. Connection of the piston rod with the cross heads
2. Joining of tail rod with piston rod of a wet air
pump
3. Foundation bolt
4. Connecting two halves of fly wheel (cotter and
dowel arrangement)
4. Design of Spigot and Socket Cotter
Let P = Load carried by the rods,
d = Diameter of the rods,
d₁ = Outside diameter of socket,
d₂ = Diameter of spigot or inside
diameter of socket,
d₃ = Outside diameter of spigot
collar,
t₁ = Thickness of spigot collar,
d₄ = Diameter of socket collar,
c = Thickness of socket collar,
b = Mean width of cotter,
t = Thickness of cotter,
l = Length of cotter,
a = Distance from the end of the slot to the end of rod,
σt = Permissible tensile stress for the rods material,
τ = Permissible shear stress for the cotter material, and
σc = Permissible crushing stress for the cotter material.
5. SPIGOT BREAKING IN
TENSION OUTSIDE THE
JOINT
SPIGOT BREAKING IN
TENSION ACROSS
SLOT
Cotter joint – modes of failure
18. Example :- Design a socket and spigot joint to resist a
tensile load of 28kN. All the parts of the joints are
made from same material with following allowable
stresses:
σt=50 N/mm2 , σc=60 N/mm2 , τ=35 N/mm2 .
Solution,
Data :- P=28kN
σt=50 N/mm2
σc=60 N/mm2
τ=35 N/mm2
19. 1. Diameter of rod (d) :-
• Tensile stress induced in rod,
4/2
d
P
t
4/
10*28
50 2
3
d
mmd 30
20. 2. Diameter of spigot (dt) and thickness of cotter (t) :-
• Taking t=0.3d=0.3*30=9mm
• The tensile stress in spigot,
)9*4/( 1
2
dd
P
t
)9*4/(
10*28
50
1
2
3
dd
mmd 341
21. • The crushing stress in cotter and spigot:-
• Taking larger dia,
td
P
c
1
9*
10*28
50
1
3
d
mmd 521
mmd 521
22. 3.outside diameter of socket (Dt) :-
• The tensile stress in socket,
tdDdD
P
t
11
2
1
2
1 4/
9524/52
10*28
50
1
22
1
3
DD
mmD 601
23. 4.Distance from the end of slot to the end of spigot
(a):-
ad
P
12
a*52*2
10*28
35
3
mma 8
24. 5. Diameter of socket collar (D2) :-
tdD
P
c
)( 12
9)52(
10*28
60
2
3
D
mmD 602
25. 6. Thickness of socket collar (c) :-
• The direct stress in socket collar,
cdD
P
)(2 12
c)52104(2
10*28
35
3
mmc 8
26. 7. Diameter of spigot collar (d2) :-
• The crushing stress in spigot collar,
4/
2
1
2
2 dd
P
c
4/52
10*28
22
2
3
d
c
mmd 582
27. 8. Thickness of spigot collar (t1) :-
• The direct stress in spigot collar,
11td
P
1
3
*52*
10*28
35
t
mmt 51
28. 9. Width of the cottar (b) :-
• The direct shear stress in cottar,
bt
P
2
9*2
10*28
35
3
b
mmb 45
29. 10. Cottar under bending :-
• The maximum bending moment on cottar ,
42262
1112 dPddDP
M
462
112 ddDP
4
52
6
52104
2
10*28 3
mmN.10*033.3 3
30. • The maximum bending stress in a cottar,
3
12
1
2/*
tb
bM
I
MX
yy
b
2
6
tb
M
b
2
3
*9
10*033.3*6
50
b
mmb 64