User:Sachin ghode

A mechanical joint is a part of machine which are used to connect the other mechanical part or mechanism. Mechanical joints may be temporary or permanent. Most types are designed to be disassemble when required.

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Types Of Mechanical Joints
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1.Knuckle Joints

2.Turnbuckle Joints

3.Pin Joints 4.Cotter Joints

5.Bolted joints

6.Screw Joints

7.Welded Joints

Knuckle Joints
A knuckle joint is used to connect the two rods which are under the tensile load, when there is requirement of small amount of flexibility or angular moment is necessary. There is always axial or linear line of action of load.

The knuckle joint assembly consist of following major components :

1.Single eye.

2.Double eye or fork.

3.Knuckle pin.

At one end of the rod the single eye is formed and double eye is formed at the other end of the rod.Both, single and double eye are connected by a pin inserted through eye.The pin has a head at one end and at other end there is a taper pin or split pin. For gripping purpose the ends of the rod are of octagonal forms.Now, when the two eyes are pulled apart, the pin holds them together .The solid rod portion of the joint in this case is much stronger than the portion through which the pin passes.

The modes of failure are :

1.Shear failure of pin (single shear).

2.Crushing of pin against rod.

3.Tensile failure of flat end bar.

Application :

1.Tie rod joint of roof truss.

2.Tension link in bridge structure.

3.Link of roller chain.

4.Tie rod joint of jib crane.

5.The knuckle joint is also used in tractor.

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Design of knuckle joint
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The assembly diagram of knuckle joint is as shown in fig.

The dimension of knuckle joints are

Diameter of rod = d

Diameter of knuckle pin = dp

Outside diameter of single eye = doe

Outside diameter of double eye = dod

Thichness of single eye = t

Thickness of fork = t1

Axial tensile force on rod = P

(1) Diameter of rod

Consider the rod is subjected to a direct tensile stress

ς = P /πd2

From above equation ,diameter of rod 'd' is obtained.

(2) Design of pin (dp)

(a) Consider the failure of pin under double shear due to tensile force.

Therefore, direct shear stress induced in knuckle pin is given by Equation

ς= P/ 2A = (P/2) × (Π/4)dp2 = 2P/ Πdp2

(b) Failure of knuckle pin in bending

Assume there is no clearance or slack but in actual, knuckle pin is loose in forks to permit angular moment of one with respect to other, so it is subjected to bending moment in addition to shear, consider uniformly distributed load along the portion of pin.

Taking moment about axis XX

M = [(-P/2) × (t/4)] + { (P/2) × [ (t2/2)+(t1/3) ] }

= P/2 [(t1/3)+(t/2)-(t1/4) ]

=P/2 [ (t1/3)+(t/4) ]

Section modulus,

Z=(π/ 32)dp3

Maximum bending stress, σb

σb= M/Z = { P/2 [(t1/3)+(t/4)] } / {(π/ 32)dp3}

Here,we check the pin in bending and find the value of dp

(3) Design of single eye :

(a) To find the outside diameter diameter of single eye (doe) The single eye is subjected to a direct tensile stress, due to this single eye under tear.

σt = P/A = P/ (doe-dp)× t

(b) Due to direct tensile strength, the single eye is subjected to double shear.

Resisting shearing area = 2(doe-dp)×(t/2)

The direct shear stress induced is

ς=P/(doe-dp)×t

From this equation the outside diameter of single eye doe is obtained.

(C) Failure of single eye or pin due to tensile load in crushing

Resisting crushing area = dp × t

σc = P/(dp×t)

Form this equation crushing stress checked if fail, increase the thickness of eye (t).

(4) Design of fork (double eye):

(a) The tearing of the double eye at weakest section due to tension

Area resisting tear = (dof – dp) × 2 t1

σt =   p/ [(dof – dp) × 2 t1]

From this equation, find the outside diameter of fork (dof).

(b) Failure of double eye (fork) in double shear due to tensile load.

Area resisting shear = 4 × [(dof – dp) ]/2 × t1

= 2 × (dof – dp) t1

The shear stress is given by,

ς = p/[(dof – dp) × 2 t1]

From this equation ,check shear stress if less than design, increase thickness of fork t1.

(c) Failure double eye in crushing (thickness of fork)

Double eye may fail in crushing due to tensile load

The crushing stress is given by,

σc = P/( 2×dp ×t1)

Check crushing stress or find t1

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TURN BUCKLE
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The buckle or a coupler is a mechanical joint used to connect two members which are subjected to tensile loading which require slight adjustment of length or tension under loaded conditions. It consist of central hexagonal nut called coupler and tie rod having right hand and left hand threads. A coupler of hexagonal shape is to facilitate the turning of it with a spanner or sometime a hole is provide in the nut so that tommy bar can be inserted for rotating it. As coupler rotate, the tie rod are either pulled together or pushed apart depending upon the direction of the rotation coupler normally the tie rods are made of steel, while coupler is made of steel or C.I.

Application :

1. To tighten the members of the roof truss.

2. Used to connect link in a mechanism to transfer motion

3. Used between the two railway wagon or bogies.

4. To tighten the cable or stay ropes of electric distribution poles.

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Design of Turn Buckle
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Consider a turnbuckle, subjected to an axial tensile force P. The various dimensions of the turnbuckle are calculated as follows:

(1) Diameter of tie rod ‘dc2 :

Due to axial tensile load p, the rod is subjected to tensile stress. Also due to twisting moment in the tie rod.

The tie rod is design for direct tensile load of Pd=1.25P

The tensile stress induced in tie rod is given by

σt = 4Pd/ (π×dc×dc)

From above equation the core diameter of the tie rod is obtained. The nominal diameter can be selected from I.S.O metric screw threads table or it can be found by,

do = dc/ 0.84

(2) Length of couple nut (ln) :

Consider the direct shearing of the thread at the root of the coupler nut and the screw.

(a) The direct shear stress induced in screw thread is

ςs = P/(π×dc×ln)

(b) The direct shear stress induced in nut

ςn = P/ (π×do×ln)

Where,

ςs and ςn = shear stress in screw and nut respectively in N/mm2 do =   Nominal diameter of the screw

dc = Core diameter of the screw

ln = Length of the coupler nut

(c) Check of crushing of the thread

crushing resistance of the thread = (π/4) × [do2- dc2] ×n×ln× σc

Where,

n =   number of threads per length  = ln/p

σc = crushing stress induced in the coupler

p = pitch of the thread in mm

Equating the design load with crushing resistance

'''pd = (π/4) × [do2- dc2] ×n×ln× σc '''

(3) Outside diameter of the coupler nut (D) :

The coupler nut is subjected to a direct tensile load P and a torque T.

Consider tearing of the coupler nut due to tensile stress induced in it. In order to account for the torque, the tensile load is taken as Pd.

The tensile stress induced in coupler nut is given by

σt = 4P/(π×(D2- do2))

By empirical relation, the outside diameter of the coupler nut D is taken as

D = 1.25 do or 1.5 do

(4) Outside diameter of coupler (D2):

Let,D1= Inside diameter of the coupler

D2 = Outside diameter of the coupler

Consider a coupler is subjected to direct tensile load P and a torque T.So for design the coupler outside diameter ,the design load is consider.

By empirical relation ,

The outside diameter of the coupler D2 is taken as,

D2 = 1.5do or 1.75 do

(5) Length of the coupler nut (Ln)

Ln = 6 do

(6) Thickness of the coupler = t = 0.75 do

(7)Thickness of the coupler nut = t1 = 0.5 do

'''=Referance= '''