User:Sachin ghode

MECHANICAL JOINTS

Definition

Mechanical joints are defined as the part of machine which are used to connect the other mechanical part or mechanism.These mechanical joints may be temporary or permanent.The joints may be disassemble whenever we required.^[1]

Types Of Mechanical Joints

1.Knuckle Joints

2.Turn Buckle

3.Cotter Joints

4.Bolted joints

5.Screw Joints

6.Welded Joints

7.Pin Joints^[2]

Knuckle Joint

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.^[3]

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.^[4]

Design of knuckle joint

^[5]

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 = d_p

Outside diameter of single eye = d_oe

Outside diameter of double eye = d_od

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 (d_p)

(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)d_p² = 2P/ Πd_p²

(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)d_p³

Maximum bending stress, σ_b

σ_b= M/Z = { P/2 [(t₁/3)+(t/4)] } / {(π/ 32)d_p³}

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

(3) Design of single eye :

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

σt = P/A = P/ (d_oe-d_p)× t

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

Resisting shearing area = 2(d_oe-d_p)×(t/2)

The direct shear stress induced is

ς=P/(d_oe-d_p)×t

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

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

Resisting crushing area = d_p × t

σ_c = P/(d_p×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 = (d_of – d_p) × 2 t₁

σ_t = p/ [(d_of – d_p) × 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 × [(d_of – d_p) ]/2 × t₁

= 2 × (d_of – d_p) t₁

The shear stress is given by,

ς = p/[(d_of – d_p) × 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×d_p ×t₁)

Check crushing stress or find t₁

TURN BUCKLE

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.

Design of Turn Buckle

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 ‘d_c² :

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 P_d=1.25P

The tensile stress induced in tie rod is given by

σ_t = 4P_d/ (π×d_c×d_c)

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,

d_o = d_c/ 0.84

(2) Length of couple nut (l_n) :

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

ς_s = P/(π×d_c×l_n)

(b) The direct shear stress induced in nut

ς_n = P/ (π×d_o×l_n)

Where,

ς_s and ς_n = shear stress in screw and nut respectively in N/mm2

d_o = Nominal diameter of the screw

d_c = Core diameter of the screw

l_n = Length of the coupler nut

(c) Check of crushing of the thread

crushing resistance of the thread = (π/4) × [d_o²- d_c²] ×n×l_n× σ_c

Where,

n = number of threads per length = l_n/p

σ_c = crushing stress induced in the coupler

p = pitch of the thread in mm

Equating the design load with crushing resistance

p_d = (π/4) × [d_o²- d_c²] ×n×l_n× σ_c

(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 P_d.

The tensile stress induced in coupler nut is given by

σ_t = 4P/(π×(D₂- d_o²))

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

D = 1.25 d_o or 1.5 d_o

(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 = 1.5d_o or 1.75 d_o

(5) Length of the coupler nut (L_n)

L_n = 6 d_o

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

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

Referance

^ Blake, Alexander (1985). Design of mechanical joints. CRC Press. ISBN 978-0824773519. {{cite book}}: |access-date= requires |url= (help)
^ Jr, [editors in chief,] Joseph E. Shigley, Charles R. Mischke, Thomas H. Brown, (2004). Standard handbook of machine design (3rd ed. ed.). New York: McGraw-Hill. ISBN 9780071441643. {{cite book}}: |edition= has extra text (help); |first= has generic name (help)CS1 maint: extra punctuation (link) CS1 maint: multiple names: authors list (link)
^ Gupta, R.S. Khurmi, J.K. (2008). A textbook of machine design (S.I. units) : [a textbook for the students of B.E. / B.Tech., U.P.S.C. (Engg. Services); Section 'B' of A.M.I.E. (1)] (14th ed. ed.). Ram Nagar, New Delhi: Eurasia Publishing House. ISBN 8121925371. {{cite book}}: |edition= has extra text (help)CS1 maint: multiple names: authors list (link)
^ Bhandari, V.B. (2001). Introduction to machine design. New Delhi: Tata McGraw-Hill. ISBN 9780070434493.
^ Gupta, R.S. Khurmi, J.K. (2008). A textbook of machine design (S.I. units) : [a textbook for the students of B.E. / B.Tech., U.P.S.C. (Engg. Services); Section 'B' of A.M.I.E. (1)] (14th ed. ed.). Ram Nagar, New Delhi: Eurasia Publishing House. ISBN 8121925371. {{cite book}}: |edition= has extra text (help)CS1 maint: multiple names: authors list (link)

[1] Blake, Alexander (1985). Design of mechanical joints. CRC Press. ISBN 978-0824773519. {{cite book}}: |access-date= requires |url= (help)

[2] Jr, [editors in chief,] Joseph E. Shigley, Charles R. Mischke, Thomas H. Brown, (2004). Standard handbook of machine design (3rd ed. ed.). New York: McGraw-Hill. ISBN 9780071441643. {{cite book}}: |edition= has extra text (help); |first= has generic name (help)CS1 maint: extra punctuation (link) CS1 maint: multiple names: authors list (link)

[3] Gupta, R.S. Khurmi, J.K. (2008). A textbook of machine design (S.I. units) : [a textbook for the students of B.E. / B.Tech., U.P.S.C. (Engg. Services); Section 'B' of A.M.I.E. (1)] (14th ed. ed.). Ram Nagar, New Delhi: Eurasia Publishing House. ISBN 8121925371. {{cite book}}: |edition= has extra text (help)CS1 maint: multiple names: authors list (link)

[4] Bhandari, V.B. (2001). Introduction to machine design. New Delhi: Tata McGraw-Hill. ISBN 9780070434493.

[5] Gupta, R.S. Khurmi, J.K. (2008). A textbook of machine design (S.I. units) : [a textbook for the students of B.E. / B.Tech., U.P.S.C. (Engg. Services); Section 'B' of A.M.I.E. (1)] (14th ed. ed.). Ram Nagar, New Delhi: Eurasia Publishing House. ISBN 8121925371. {{cite book}}: |edition= has extra text (help)CS1 maint: multiple names: authors list (link)

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