Triaxial Stress Analysis
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Transcript of Triaxial Stress Analysis
Triaxial stress analysis
Casing Design
Prepared by: Tan Nguyen
The fundamental basis of casing design is that if stresses in the pipe
wall exceed the yield strength of the material, a failure condition
exists. Hence the yield strength is a measure of the maximum
allowable stress. To evaluate the pipe strength under combined
loading conditions, the uniaxial yield strength is compared to the
yielding condition.
The most widely accepted yielding criterion is based on the
maximum distortion energy theory, which is known as the
Huber-Von-Mises Theory. This theory states that if the triaxial stress
exceeds the yield strength, a yield failure is indicated. Note that the
triaxial stress is not a true stress. It is a theoretical value that allows a
generalized three-dimensional stress state to be compared with a
uniaxial failure criterion (the yield strength).
Casing Design
Combined Stress Effects (Triaxial stress analysis)
VME z t t r r z Ys s s2
s s2
s s2
s2
1
Where
sY – minimum yield stress, psi
sVME – triaxial stress, psi
VME: Von Mises Equivalent
sz, st, sr – axial tress, tangential
stress, and radial stress, psi
(1)
Casing Design
Setting the triaxial stress equal to the yield strength and solving
Y
z i
Y
z i
Y
t pi p p
s
s
s
s
s
s
2
1
4
31
2
This equation is for the ellipse of plasticity. Combining this eq. and
the equation of tangential stresses together and let r = ri, will give
the combinations of internal pressure, external pressure and axial
stress that will result in a yield strength mode of failure.
equation (1) give the results:
(2)
st – tangential stressespi –internal pressure
(3)
Casing Design
As axial tension increases, the critical burst-pressure
increases and the critical collapse-pressure decreases.
In contrast, as the axial compression increases, the
critical burst-pressure decreases and the critical
collapse-pressure increases.
Casing Design
Example
Compute the nominal collapse pressure rating for 5.5’’, N-80 casing
with a nominal wall thickness of 0.476’’ and a nominal weight per
foot of 26 lbf/ft. In addition, determine the collapse pressure for
in-service conditions in which the pipe is subjected to a 40,000 psi
axial tension stress and a 10,000 psi internal pressure. Assume a
yield strength mode of failure.
2 2
2 2 2 2
o i
i o i e o
tr r
p r r p r
s
Y
i
o i
i o i e o
Y
t i
pr r
p r r p r
p
s s
s
2 2
2 2 2 2
Y
i e
o i
o
Y
t i p p
r r
p r
s s
s2 2
2 2
5.5 4.548 80,000
2 5.52 2
2
i e
Y
t pi p p
s
s
12,649 12,649
i e e
Y
t pi p p p
s
s
Solution
For collapse pressure rating, r = ri then eq. (3) becomes
Casing Design
0
Y
z pi
s
s
1
Y
t pi
s
s
112,649
pe
pe 12,649 psi
From eq. (2) with we have
For in-service conditions of sz = 40,000 psi and pi = 10,000 psi
12,649
10,000 e
Y
t pi p
s
s
0.62580,000
40,000 10,000
Y
z pi
s
s
Solving eq. (14) gives
0.528412,649
10,000
e
Y
t pi p
s
s
pe 16,684 psi
Casing Design