Flow Forces and the Tilting of Spring Loaded Valve Plates - Part
Determination of Contact Stress Distribution in Pin Loaded Orthotropic Plates
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Transcript of Determination of Contact Stress Distribution in Pin Loaded Orthotropic Plates
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Determination of Contact Stress Distribution in Pin Loaded Orthotropic Plates
Neville A. Tomlinson
Department of Mechanical Engineering
Howard University
Washington D C
December 2006
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Outline Introduction
Joints Orthotropic materials The pin loaded plate
Orthotropic Plate Theory Problem definition Mathematical Formulations For the Pin Loaded Plate with Clearance and
Friction The contact equation Boundary conditions at the pin-plate interface Friction Trigonometric displacement functions Stress-stress functions Stress Equations
Results Conclusions Recommendations Contribution Acknowledgements
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Introduction
Joints Important form of mechanical joining of structural elements
Reason Ease of assembly and disassembly
Joint Types Bolted Joints, riveted joints, welded joints, pin joints
Pin Joint For plane stress analysis pin joint is representative of joint
analysis
Common Joint Materials Iron, Steel, Aluminum (isotropic, strong, heavy and/or expensive) Fiber reinforced Composites (orthotropic, can design strength,
light, relatively inexpensive)
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Orthotropic Materials
Anisotropic materials Material having different properties in different directions
Orthotropic materials Thin anisotropic materials whose transverse stresses are
considered negligible and therefore transverse properties are ignored
Considered in plane problems of elasticity
Simplifies the analysis
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The Pin Loaded Plate
In studying pin loaded joints only the plate is considered in this analysis
Assumption: pin is rigid
Plate
Pin
hole
Schematic of a Pin Loaded Plate
P
P/2 P/2
clevis
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Orthotropic Plate Theory
Equilibrium Equation (no body force)
Constitutive Equation
Compatibility Equation
0
0
xyx
xy y
x y
x y
11 12 16
12 22 26
16 26 66
x x
y y
xy xy
a a a
a a a
a a a
2 22
2 20y xyx
x yy x
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Orthotropic Plate Theory (Continued)
Airy Stress Function
Governing Partial Differential Equation for Orthotropic Material
2
2x
F
y
2
2y
F
x
2
xy
F
x y
4 4 4 4 4
22 26 12 66 16 114 3 2 2 3 42 (2 ) 2 0
F F F F Fa a a a a a
x x y x y x y y
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Orthotropic Plate Theory (continued)
Complex Stress Function
Characteristic Equation
Roots
Re-writing Governing Equation
k = 1 to 4
Solution for F (invoking rule of complex addition)
( , ) ( ) x yF x y F x y e
4 3 211 16 12 66 26 222 (2 ) 2 0a a a a a a
1 2 3 1 4 2, , ,i i i i
( 0k kF x yx y
1 1 2 22Re[ ( ) ( )]F F z F z
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Orthotropic Plate Theory (continued)
By defining two complex functions
and where
In terms of complex stress functions stresses become
11 1
1
( )dF
zdz
22 2
2
( )dF
zdz
k k
k k
z x y
z x y
2 ' 2 '1 1 1 2 2 22Re ( ) ( )x z z
' '1 1 2 22Re ( ) ( )y z z
' '1 1 1 2 2 22Re ( ) ( )xy z z
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Problem Definition
hr
region of no contact
region of contact
Plate thickness = unity
Hole radius =
Clearance =
Pin radius =
Pin force =
Pin displacement =
Hole center = A
Contact point = B
Contact angle =
( 0.02)hr
p hr r
P
0u
B
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Mathematical Formulations For the Pin Loaded Plate with Clearance and Friction
Equation of ellipse
Point B has coordinates
2 2
2 21
x y
a b
0 cospx u r
'sin By R
222 2
0 0
2 22 2 2 20 0
cos 1 cos *
cos 1 cos 0
B p B
h B B p h p
u r u
r u r r u r
Contact Equation
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Boundary Conditions at the Pin-plate Interface
1 0u u0u u0v
0 B
0r 0r B
0( ) cos sinu u v B B
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Friction Assuming Coulomb Frictional relation,
-ve sign: shear opposes the direction of relative displacements between the pin and the plate
Introduce Friction into the model by the relation
r f r
0 0
B B
h hrr fr d r d
f Constant Coefficient of Friction
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Trigonometric displacement
function
1 2 3
1 2 3
cos 2 cos 4 cos6
sin 2 sin 4 sin 6
u u u u
v v v v
0 0
0
0
0B B
rB
r
h h Brr fr d r d
y
2 0 ,2Bu u
Traction conditions on the hole boundary requires that
Assumed three terms displacement field along the contact region as
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Trigonometric Displacement Function (continued)
0 0 1 2 3
1 0 1 2 3
2 0 1 2 3
cos 2 cos 4 cos 6
cos cos 2 cos3B B B
B B B
u u u u
u u u u
u u u u
B
/ 2B
4 2
1 0 0 0 0 21
0 2 0
sec 2 222 3 564 1 2
BB
B B
B BB
co Sec u u u cos u cosu
u cos u coscos
4
0 1 0 0 2
2 0 0 2
0
2sec2
2 2 38 1 2cos 1 2cos 2cos 2
4
BB
B BB B B
B
u u u cosco
u u cos u cos
u cos
4 2
0 1 0 0
3 0 2 0 2
0
sec sec2 2
2 2 264 1 2cos cos 2 cos3
3
B BB
B BB B B
B
u u u cosco
u u cos u cos
u cos
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Trigonometric Displacement Function (continued)
1 1 0 1 2
2 2 0 1 2
3 3 0 1 2
( , , , )
( , , , )
( , , , )
B
B
B
v v u
v v u
v v u
0( ) cos sinu u v
0 1 2 3
1 2 3
( ( cos 2 cos 4 cos 6 ))cos
( sin 2 sin 4 sin 6 )sin
u u u u
v v v
Using the following relation,
Evaluate at , ,2 4B
B
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Determination of the Stress Functions
and Stresses
0
0
m mm m
m
m mm m
m
u
v
0 0
, tan
,
cons ts
rigid body displacement
unit hole radius
1 1 0 1 1 2 1 2 2 2 2 2 121
1 1 1( ) ln ( )
2m
m mm
z A A q p ibq ap q pD D
2 2 0 2 1 1 1 1 1 1 1 1 222
1 1 1( ) ln ( )
2m
m mm
z B B q p ibq ap q pD D
0 0,A B Constants
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Determination of the Stress Functions and Stresses (continued)
k
2 2 2(1 )
(1 )k k h k
kh k
z z r
r i
cos sinie i
1 1
cos2
1 1
sin2i
mapping function
Introduce unit circle to satisfy boundary conditions
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Determination of the Stress Functions and Stresses (continued)
2 2 4 4 6 6
1 2 32 2 2u u u u
2 2 4 4 6 6
1 2 32 2 2v v v v
i i i
0
0
m mm m
m
m mm m
m
u
v
2 4 61 1 1 1 2 1 2 1 2 2 2 2 1 3 2 3 2 1
2 4 62 2 2 1 1 1 1 2 2 1 2 1 2 3 1 3 1 2
1( ) ln
21
( ) ln2
A u q iv p u q iv p u q iv pD
B u q iv p u q iv p u q iv pD
Comparing coefficients yields
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Determination of the Stress Functions and Stresses (continued)Stress stress function relationship
Stress transformation from x,y system to polar system
2 ' 2 '1 1 1 2 2 2
' '1 1 2 2
' '1 1 2 2 2
2Re
2Re
2Re
x
y
xy
z z
z z
z z
2 2
2 2
2 2
cos sin 2sin cos
sin cos 2sin cos
sin cos sin cos cos sin
r x
y
r xy
2 2' '1 1 1 2 2 2
2 2' '1 1 1 2 2 2
'1 1 1 1
'2 2 2 2
2Re sin cos sin cos
2Re sin cos sin cos
sin cos cos sin2Re
sin cos cos sin
r
r
z z
z z
z
z
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Determination of the Stress Functions and Stresses (continued)
1 2 3 4
1 2 3 411
5 6 7
1 2 3 4
cos cos3 cos5 cos 7
cos cos cos 2 cos cos 42
cos cos 6 cos cos8 cos cos10
sin sin 3 sin 5 sin 7
r
h
r
H H H H
a E
r
I I I I
221 2 1 2
11
661 2 1 2 12
11
( ) ( ) 2( )
ak
a
an i i k
a
, , ,H I E Functions of material parameters, the displacement coefficients and the hole radius
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Determination of
Displacement Parameters obtained as functions of
0 1 2, ,u
0 0
0
0
B B
r B
r B
h hrr f
at
at
r d r d
1 2 3 4
1 2 3 4
1 2 3 4
0
1 2 3 4
0
cos cos3 cos5 cos7 0
sin sin 3 sin 5 sin 7 0
sin sin 3 sin 5 sin 7
cos cos3 cos5 cos7
B
B
B B B B
B B B B
h
f h
H H H H
I I I I
I I I I r d
H H H H r d
, , , ,ij B fa P
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Determination of B
222 2
0 0
2 22 2 2 20 0
cos 1 cos *
cos 1 cos 0
B p B
h B B p h p
u r u
r u r r u r
0 , , ,p hu r r
, , ,ij fa P Given
Substitute
Re-stated as
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Determination of Determination of allows the determination of the
displacement coefficients
0 1 2, , ,B u
1 2 3 1 2 3, , , ,u u u v v and v
4 2
1 0 0 0 0 21
0 2 0
4
0 1 0 0 2
2 0 0 2
0
3
sec 2 222 3 564 1 2
2sec2
2 2 38 1 2cos 1 2cos 2cos 2
4
sec2
BB
B B
B BB
BB
B BB B B
B
B
co Sec u u u cos u cosu
u cos u coscos
u u u cosco
u u cos u cos
u cos
co
u
4 2
0 1 0 0
0 2 0 2
0
sec2
2 2 264 1 2cos cos 2 cos3
3
BB
B BB B B
B
u u u cos
u cos u cos
u cos
1 1 0 1 2
2 2 0 1 2
3 3 0 1 2
( , , , )
( , , , )
( , , , )
B
B
B
v v u
v v u
v v u
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Determination of stresses
The determination of allows the complete determination of stresses
Where are functions of
1 2, 3 1 2, 3, , ,u u u v v and v
1 2 3 4
1 2 3 411
5 6 7
1 2 3 4
cos cos3 cos5 cos 7
cos cos cos 2 cos cos 42
cos cos 6 cos cos8 cos cos10
sin sin 3 sin 5 sin 7
r
h
r
H H H H
a E
r
I I I I
,H I and 1 2, 3 1 2, 3, , ,u u u v v and v
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Results
Consider three orthotropic materials
Plate a11
(TPa)-1
a22
(TPa)-1
a12
(TPa)-1
a66
(TPa)-1 laminate
A 49.02 8.95 -5.93 59.17 0.121
B 17.27 17.27 -53.52 45.32 0.310
C11.69 38.88
-78.01 45.18 0.667
12
0 0490 / 45
S
0 0 00 / 45 / 90S
0 0
20 / 45S
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Contact angle analysis
Fixed clearance and varying friction (Plate A)
f P B(GN) (degrees)
0.0 0.2 15.6 88.52
0.4 21.0 88.80
0.01 0.2 15.05 76.18
0.4 20.6 76.58
0.02 0.2 14.0 71.05
0.4 17.0 72.19
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Contact angle analysis
Fixed friction and varying clearance (Plate A)
f P B(GN) (degrees)
0.2
0.0 15.6 88.52
0.01 15.05 76.18
0.02 14.0 71.05
0.4
0.0 21.0 88.80
0.01 20.6 76.58
0.02 17.0 72.19
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Fixed Friction and Clearance (Plate C)
P0u B
(GN)(degrees)
7.0 0.02 63.1
12.0 0.035 71.8
17.0 0.05 76.07
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Radial Streses for Plate A for Fixed Clearance0 0.05u
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Radial Streses for Plate A for Fixed Friction
0 0.05u
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Shear Stress for Plate A for Fixed Clearance
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Shear Stress for Plate A for Fixed Friction
0 0.05u
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Hoop Stress for Plate A for Fixed Clearance0 0.05u
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Hoop Stress for Plate A for Fixed Friction
0 0.05u
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Radial Stress for Plate B for Fixed Clearance0 0.035u
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Shear Stress for Plate B for Fixed Clearance0 0.035u
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Shear Stress for Plate B for Fixed Friction0 0.035u
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Hoop Stress for Plate B for Fixed Clearance 0 0.035u
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Hoop Stress for Plate B for Fixed Friction0 0.035u
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Stresses for Plate C for varying Pin displacement
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Conclusion Contact angle is not significantly affected with increasing friction for fixed clearance.
Contact angle decreases with increasing clearance for fixed friction. Friction and clearance strongly affects contact stress distribution.
Maximum radial stress decrease as friction increase for fixed clearance.
Maximum radial stress increase as clearance increase for fixed friction
Maximum shear and hoop stress increase with increasing friction for fixed clearance and with increasing clearance for fixed friction.
Maximum radial, shear and hoop stress increase with increasing pin displacements
Increasing pin displacement does not appear to affect hoop stress along load axis.
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Recommendations
Lateral deformation of ellipse: Account for lateral deformation of ellipse
Pin: Consider effect of pin elasticity
Plate: Consider finite plate
Constant Friction: Consider non linear friction
Friction Mode: Consider non-Coulombic friction model eg.
No-slip: Analysis assumed slip throughout the contact region. Consider the influence of no-slip zone on stresses.
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Contributions
Simpler method of analyzing contact region in pin loaded joints.
Simpler method for analyzing stresses in joints with or without clearance.
Method is capable of analyzing interference fitted pin joints.
Very little computer time is required for analysis.
Solution can be implemented using any computer and any symbolic mathematical software.
Simpler method of optimizing joint design which should prove friendly to designers.
Provides a simpler approach to the non-linear problem of pin loaded joints with clearance and friction.
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Acknowledgements
The thesis committee Dr. Lewis Thigpen Dr. Marcus A. Alfred Dr. Mrinal C. Saha Dr. Mohsen Mosleh Dr. Horace A. Whitworth