2. 6-2
Roadmap of This Talk
1. A rogue’s gallery of examples
2. Classical buckling and imperfection sensitivity
3. Nonlinear collapse and linear bifurcation model
4. Bifurcation buckling from nonlinear
prebuckling state
5. Effect of boundary conditions
6. Examples of stable post-buckling
7. Interaction of local and general instability
8. Effect of imperfections on stiffened shells
20. 6-20
Prebuckling Deformation of Nuclear Containment
Shell Due to Horizontal Ground Motion
Buckling will
occur here
due to
maximum
axial
compression
24. 6-24
Laying Oil Pipeline at Sea
Buckling can occur on
compressive side of bent
pipe on bottom of pipe;
here, top of pipe where it
bends other way near
sea bed
25. 6-25
Offshore Oil Platform Support
Supporting
truss consists
of assemblage
of thin
cylindrical
shells with
large diameters
30. 6-30
Possible Buckling of Partially Filled LNG Tank
Buckling is
from hoop
compression
just below
the equator
Prebuckling
stress state is
meridional
tension
combined
with hoop
compression
31. 6-31
Thin Shell Space Structures
Thin shell space structures for use in orbit
Many of these lightweight structures are designed by buckling
32. 6-32
Space shuttle external tank
Aerospace
structures like
this may buckle
due to launch
loads combined
with
circumferentially
varying dynamic
pressure
34. 6-34
Payload Shroud Consists of Several
Segments with Joints
The thicknesses
of the shell walls
varies along the
length because
the destabilizing
stresses
generated by the
launch loads vary
along the length
of the structure
42. 6-42
Buckling of Perfect & Imperfect Shell
In contrast to
the behavior
shown in the
previous slide,
here bifurcation
buckling, B,
occurs before
axisymmetric
collapse, A
45. 6-45
Buckling of Thin Cylindrical Shell Under Uniform
Axial Compression
The buckles are
widespread & small
compared to a
typical structural
dimension. This
behavior indicates
extreme sensitivity
of the critical load
to initial shape
imperfections
46. 6-46
Comparison of Test & Theory for Axially
Compressed Thin Cylindrical Shells
(Perfect shell)
Design
recommendation
47. 6-47
Buckling of Externally Pressurized Thin
Spherical Shell
Mandrel inside
shell prevents
collapse
Critical loads of
shells with this
type of buckling
are extremely
sensitive to initial
shape
imperfections
48. 6-48
Buckling of Externally Pressurized
Spherical Caps
Deeper caps
behave more
like complete
spherical
shells
Their critical
pressures are
therefore more
sensitive to
initial shape
imperfections
than are those
for shallow
caps
49. 6-49
Comparison of Test & Theory for Buckling of
Spherical Caps Under Uniform External Pressure
56. 6-56
Buckling of Axially Compressed Stiffened
Cylindrical Shell
Tested by Professor Josef
Singer, et al (Technion)
Critical loads of stiffened
shells are less sensitive to
initial imperfections than
monocoque shells
because typical buckle
size is comparable to size
of test specimen: effective
thickness for axial bending
is large
57. 6-57
Buckling of Axially Stiffened Cylindrical
Shells Under Axial Compression
Buckling of
perfect
cylindrical
shells with
outside vs.
inside
stringers
Koiter
imperfection
sensitivity
parameter, b
58. 6-58
Buckling of Perfect & Imperfect 3-Layered
Composite Axially Compressed Cylindrical Shells
Note that critical
load of strongest
shell (40°) is
most sensitive
to amplitude of
initial
imperfection
61. 6-61
Axially Compressed Cylindrical Shell With
Rectangular Cutout
Note initial buckling
near vertical edge of
cutout
Buckling on either
side of cutout causes
shedding of axial
load to rest of shell,
which continues to
accept more axial
load
Test by Almroth
62. 6-62
State of Shell at Collapse
Shell
continues to
accept more
& more axial
load until
cylindrical
wall buckles
everywhere
64. 6-64
Buckling of Torispherical Shell Under Internal
Pressure
Under internal pressure, knuckle
region is under meridional
tension combined with hoop
compression
Therefore, buckles are elongated
in meridional direction
First buckle forms, relieving
compressive hoop stress in its
neighborhood, permitting further
loading of shell as additional
isolated buckles form one by one
as internal pressure is further
increased
68. 6-68
Simulation of Fabrication Process
Thru-thickness stress distribution after
rolling the skin to radius smaller than final
radius
Thru-thickness stress distribution after
springback to final radius, Rnominal
Stress distribution after springback & after
welding rings to exterior shell wall
Stress distribution after application of
pressure
79. 6-79
Modal Interaction in Buckling of 2-Flanged
Column
Maximum imperfection sensitivity is near the design for
which local & overall buckling occur at the same load.
Flange width, b
(Euler buckling)
(Flange buckling)
80. 6-80
OPTIMIZATION OF AN AXIALLY
COMPRESSED RING AND STRINGER
STIFFENED CYLINDRICAL SHELL
WITH A GENERAL BUCKLING MODAL
IMPERFECTION
AIAA Paper 2007-2216
David Bushnell, Fellow, AIAA, retired
81. 6-81
General buckling mode from STAGS
External T-stringers,
Internal T-rings,
Loading: uniform axial
compression with axial
load, Nx = -3000 lb/in
This is a STAGS model.
50 in.
75 in.
82. 6-82
TWO MAJOR EFFECTS OF A GENERAL
IMPERFECTION
1. The imperfect shell bends when any loads
are applied. This “prebuckling” bending
causes redistribution of stresses between
the panel skin and the various segments of
the stringers and rings.
2. The “effective” radius of curvature of
the imperfect and loaded shell is larger
than the nominal radius: “flat” regions
develop.
87. 6-87
SOME MAIN POINTS
1. Get a “feel” for buckling from many examples.
2. If your structure has a region of compression
buckling is possible. Watch out!
3. There are two kinds of static buckling:
a. nonlinear collapse
b. bifurcation buckling.
4. There are two phases of a buckling problem:
a. prebuckling stress analysis
b. eigenvalue problem.
88. 6-88
MORE MAIN POINTS
5. Imperfections often have a huge influence.
6. Boundary conditions often have a huge influence.
7. A linear bifurcation buckling model is sometimes
a poor predictor of load-carrying capacity.
8. Some structures are stable after buckling first occurs.
9. The load-carrying capacity of optimally designed
structures is often reduced more by imperfections
than is so for other structures.