In memory of Frank Brogan, 1925 - 2006, co-developer of STAGS
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Transcript of In memory of Frank Brogan, 1925 - 2006, co-developer of STAGS
![Page 1: In memory of Frank Brogan, 1925 - 2006, co-developer of STAGS](https://reader031.fdocuments.net/reader031/viewer/2022013122/568131fb550346895d98577e/html5/thumbnails/1.jpg)
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
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In memory of Frank Brogan, 1925 - 2006, co-developer of STAGS
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Summary of talk1. The configuration studied here2. Two effects of a general imperfection3. PANDA2 and STAGS4. PANDA2 philosophy5. Seven cases studied here6. The optimization problem7. Buckling and stress constraints8. Seven cases explained9. How the shells fail10. Imperfection sensitivity
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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.
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Expanded region of buckling mode
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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.
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Loaded imperfect cylinder
Maximum stress, sbar(max)=66.87 ksi
“Flat” region
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The entire deformed cylinder
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The area of maximum stress
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The “flattened” region
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Computer programs PANDA2 and STAGS
PANDA2 optimizes ring and stringer stiffened flat or cylindrical panels and shells made of laminated composite material or simple isotropic or orthotropic material. The shells can be perfect or imperfect and can be loaded by up to five combinations of Nx, Ny Nxy.
STAGS is a general-purpose program for the nonlinear elastic or elastic-plastic static and dynamic analyses. I used STAGS to check the optimum designs previously obtained by PANDA2.
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PHILOSOPHY OF PANDA21. PANDA2 obtains optimum designs through the use of many
relatively simple models, each of which yields approximate buckling load factors (eigenvalues) and stresses.
2. Details about these models are given in previous papers. Therefore, they are not repeated here.
3. “Global” optimum designs can be obtained reasonably quickly and are not overly unconservative or conservative.
4. Because of the approximate nature of PANDA2 models, optimum designs obtained by PANDA2 should be checked by the use of a general-purpose finite element computer program.
5. STAGS is a good choice because PANDA2 automatically generates input data for STAGS, and STAGS has excellent reliable nonlinear capabilities.
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Example of PANDA2 philosophyPANDA2 computes general buckling from a simple closed-form model in which the stringers and rings are “smeared out” as prescribed by Baruch and Singer (1963). [Bushnell (1987)]
Correction factors (knockdown factors) are computed to compensate for the inherent unconservativeness of this “smeared” model: one knockdown factor for “smearing” the stringers and another knockdown factor for “smearing” the rings.
The next several slides demonstrate why a knockdown factor is needed to compensate for the inherent unconservativeness of “smearing” the rings and how this knockdown factor is computed.
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A general buckling mode from STAGS
Next slide shows detail in this region
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Detail showing local/global deformation in STAGS model
Note the local deformation of the outstanding ring flange in the general buckling mode
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The same general buckling mode from BIGBOSOR4 (Bushnell, 1999).
n = 3 circumferential waves
Deformed
Undeformed
Buckling model shown on next slide
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Approximate BIGBOSOR4 model of general buckling, n = 3
Symmetry Symmetry
Note the deformation of the outstanding flange of the ring.
Undeformed
Undeformed Deformed
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Knockdown factor to compensate for inherent unconservativeness of
“smearing” rings
Ring knockdown factor =
(Buckling load from the BIGBOSOR4 model)/
(“Classical” ring buckling formula)
“Classical” ring buckling formula= (n2 - 1) EI/r3
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SEVEN PANDA2 CASES IN TABLE 4 OF THE PAPER
Case 1: perfect shell, “no Koiter”, ICONSV=1
Case 2: imperfect, “no Koiter”, yes change imperf., ICONSV=-1
Case 3: imperfect, “no Koiter”, yes change imperf., ICONSV= 0
Case 4: imperfect, “no Koiter”, yes change imperf., ICONSV =1
Case 5: imperfect, “yes Koiter”, yes change imperf., ICONSV=1
Case 6: as if perfect, “no Koiter”, Nx=-6000 lb/in, ICONSV= 1
Case 7: imperfect, “no Koiter”, no change imperf., ICONSV= 1
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Summary of talk1. The configuration studied here2. Two effects of a general imperfection3. PANDA2 and STAGS4. PANDA2 philosophy5. Seven cases studied here6. The optimization problem 7. Buckling and stress constraints8. Seven cases explained9. How the shells fail10. Imperfection sensitivity
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Decision variables for PANDA2 optimization
Stringer spacing B(STR), Ring spacing B(RNG), Shell skin thickness T1(SKIN)
T-stringer web height H(STR) and outstanding flange width W(STR)
T-stringer web thickness T2(STR) and outstanding flange thickness T3(STR)
T-ring web height H(RNG) and outstanding flange width W(RNG)
T-ring web thickness T4(RNG) and outstanding flange thickness T5(RNG)
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OBJECTIVE =MINIMUM WEIGHT
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Global optimization: PANDA2
Objective, weight
Design iterations
Each “spike” is a new “starting” design, obtained randomly.
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CONSTRAINT CONDITIONSFive classes of constraint conditions:
1. Upper and lower bounds of decision variables
2. Linking conditions
3. Inequality constraints
4. Stress constraints
5. Buckling constraints
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DEFINITIONS OF MARGINS
Buckling margin= (buckling constraint) -1
(buckling constraint) =
(buckling load factor)/(factor of safety)
Stress margin = (stress constraint) - 1.0
(stress constraint) = (allowable stress)/
[(actual stress)x(factor of safety)]
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TYPICAL BUCKLING MARGINS
1. Local buckling from discrete model
2. Long-axial-wave bending-torsion buckling
3. Inter-ring buckling from discrete model
4. Buckling margin, stringer segment 3
5. Buckling margin, stringer segment 4
6. Buckling margin, stringer segments 3 & 4 together
7. Same as 4, 5, and 6 for ring segments
8. General buckling from PANDA-type model
9. General buckling from double trig. series expansion
10. Rolling only of stringers; of rings
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Example of local buckling: STAGS
P(crit)=1.0758 (STAGS)
P(crit)=1.0636 (PANDA2)
P(crit)=1.0862 (BOSOR4)
Case 2
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Example of local buckling: BIGBOSOR4
Case 1
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Example of bending-torsion buckling
P(crit)=1.3826 (STAGS)
P(crit)=1.378 or 1.291 (PANDA2)
P(crit)=1.289 (BOSOR4)
STAGS model, Case 2
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Bending-torsion buckling: BIGBOSOR4
Case 2
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Example of general buckling: STAGS
P(crit)=1.9017 (STAGS)
P(crit)=1.890 (PANDA2)
P(crit)=1.877 (BOSOR4)
Case 2
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Example of general buckling: BIGBOSOR4
Case 2
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Multiple planes of symmetry
60-degree model: STAGS model
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60-degree STAGS model: End view
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Close-up view of part of 60-deg. model
STAGS model
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60-degree STAGS model
Detail shown on the next slide
Case 2
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Detail of general buckling modeSTAGS model, Case 2
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TYPICAL STRESS MARGINS
1. Effective stress, material x, location y, computed from SUBROUTINE STRTHK (locally post-buckled skin/stringer discretized module)
2. Effective stress, material x, location y, computed from SUBROUTINE STRCON (No local buckling. Stresses in rings are computed)
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Buckling and stress margins in PANDA2 design sensitivity study
Optimum configuration
Case 4
H(STR)
Design margins
0 Margin
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Summary of talk1. The configuration studied here2. Two effects of a general imperfection3. PANDA2 and STAGS4. PANDA2 philosophy5. Seven cases studied here6. The optimization problem7. Buckling and stress constraints8. Seven cases explained9. How the shells fail10. Imperfection sensitivity
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SEVEN PANDA2 CASESCase 1: perfect shell, “no Koiter”, ICONSV=1
Case 2: imperfect, “no Koiter”, yes change imperf., ICONSV=-1
Case 3: imperfect, “no Koiter”, yes change imperf., ICONSV= 0
Case 4: imperfect, “no Koiter”, yes change imperf., ICONSV =1
Case 5: imperfect, “yes Koiter”, yes change imperf., ICONSV=1
Case 6: as if perfect, “no Koiter”, Nx=-6000 lb/in, ICONSV= 1
Case 7: imperfect, “no Koiter”, no change imperf., ICONSV= 1
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THE MEANING OF “ICONSV”ICONSV = 1 (the recommended value):
1. Include the Arbocz theory for imperfection sensitivity.
2. Use a conservative knockdown for smearing stringers.
3. Use the computed knockdown factor for smearing rings.
ICONSV = 0:
1. Do not include the Arbocz theory.
2. Use a less conservative knockdown for smearing stringers.
3. Use the computed knockdown factor for smearing rings.
ICONSV = -1:
Same as ICONSV=0 except the knockdown factor for smear-ing rings is 1.0 and 0.95 is used instead of 0.85 for ALTSOL.
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THE MEANING OF “YES CHANGE IMPERFECTION”
The general buckling modal imperfection amplitude is made proportional to the axial wavelength of the critical general buckling mode shape.
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A simple general buckling modal imperfection
P(crit) = 1.090, Case 1
Wimp = 0.25 inch STAGS model: Case 1
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A “complex” general buckling modal imperfection
P(crit) = 1.075, Case 1
Wimp =0.25/4.0 inch
Case 1
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“Oscillation” of margins with “no change imperfection” option
Design Margins
Design Iterations
0 Margin
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“Oscillation” of margins with “yes change imperfection” option
Design Margins
Design Iterations
0 Margin
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THE MEANING OF “NO” AND “YES KOITER”
“NO KOITER” = no local postbuckling state is computed.
“YES KOITER” = the local post-buckling state is computed. A modified form of the nonlinear theory by KOITER (1946), BUSHNELL (1993) is used.
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Local postbuckling: PANDA2
A single discretized skin-stringer module model (BOSOR4-type model) of the Case 4 optimum design as deformed at four levels of applied axial compression, Nx.
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Case 4 with “no Koiter” and with “yes Koiter”
Design loadStress margins computed with “no Koiter”
Stresses computed with “yes Koiter”
PANDA2 results: stress margins
Nx
Margins
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Case 4: Initial imperfection shape
Imperfection amplitude,
Negative Wimp =
-0.25/4.0 = -0.0625 in.
General buckling mode from STAGS 60-degree model
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Load-stress curve: static & dynamic
Static phase, PA = 0 to 0.98
Dynamic Phase, PA=1.
STAGS results
Effective stress in panel skin
Load factor, PA
Design Load, PA = 1.0
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Deformed panel at PA=0.98
Maximum Stress before dynamic STAGS run = 63.5 ksi See the next slide for detail.
STAGS results
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Example 1 of stress in the imperfect panelMaximum effective (von Mises) stress in the entire panel, 63.5 ksi. (Case 4 nonlinear STAGS static equilibrium at load factor, PA = 0.98, before the STAGS dynamic run)
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Example 1 of stress in the panel skin
Maximum effective (von Mises) stress in the panel skin= 47.2 ksi (Case 4 nonlinear STAGS static equilibrium at load factor, PA = 0.98, before the STAGS dynamic run)
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STAGS nonlinear dynamic response
Previous 2 slides, PA = 0.98
Next 2 slides, PA =1.0
Load factor held constant at PA= 1.0
Stress in the panel skin.
Stress
Time
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Example 2 of stress in the imperfect panel
Maximum effective (von Mises) stress in the entire panel, 70.38 ksi (Case 4 STAGS nonlinear static equilibrium after the dynamic STAGS run at load factor, PA = 1.00)
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Example 2 of stress in the panel skinMaximum effective (von Mises) stress in the panel skin=60.6 ksi (Case 4 nonlinear STAGS static equilibrium after dynamic STAGS run at load factor, PA = 1.00)
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Shell optimized with “yes Koiter”Maximum stress=57.3 ksi, next slide
STAGS result at PA = 1.0, Case 5
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Detail from previous slide: PA = 1.0
Maximum stress=57.3 ksi
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OPTIMIZED WEIGHTS FOR CASES 1 - 7: PANDA2
CASE WEIGHT(lb) COMMENT
1 31.81 perfect shell, no Koiter, ICONSV=1
2 39.40 imperfect, no Koiter, yes change imp., ICONSV=-1
3 40.12 imperfect, no Koiter, yes change imp., ICONSV= 0
4 40.94 imperfect, no Koiter, yes change imp., ICONSV= 1
5 41.89 imperfect, yes Koiter, yes change imp., ICONSV= 1
6 46.83 as if perfect, no Koiter, Nx = -6000 lb/in, ICONSV= 1
7 56.28 imperfect, no Koiter, no change imperf., ICONSV=1
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Summary of talk1. The configuration studied here2. Two effects of a general imperfection3. PANDA2 and STAGS4. PANDA2 philosophy5. Seven cases studied here6. The optimization problem7. Buckling and stress constraints8. Seven cases explained9. How the shells fail10. Imperfection sensitivity
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60-degree STAGS model of Case 2: General buckling mode
Wimp = -0.25/4.0 Use NEGATIVE of this mode as the imperfection shape.
Next, show how a shell with this imperfection collapses.
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Deformed shell at PA=1.02 with negative of general buckling mode
Next Slide
Case 2 STAGS model
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Enlarged view of collapsing zone
Case 2 STAGS model at PA=1.02
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Sidesway of central stringers vs PA
Design LoadStatic Dynamic
Case 2 STAGS results
Load
Sidesway
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Deformation after dynamic run
Case 2 STAGS results at PA=1.04
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Summary of talk1. The configuration studied here2. Two effects of a general imperfection3. PANDA2 and STAGS4. PANDA2 philosophy5. Seven cases studied here6. The optimization problem7. Buckling and stress constraints8. Seven cases explained9. How the shells fail10. Imperfection sensitivity
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Imperfection sensitivity, Case 5
PANDA2 results: “yes change imperfection amplitude”
Design Load
Koiter (1963)
PANDA2
Wimp(in.)
Nx(crit) (lb/in)
Effective thickness of stiffened shell=0.783 in.
Case 5 Wimp
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Margins from PANDA2 vs Nx
Case 5: Wimp = 0.5 inches
Nx
Margins
General buckling
0 Margin
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Imperfection sensitivity: Case 5
PANDA2 results: “no change imperfection amplitude”
Koiter
Nx(crit)
Wimp(in.)
Case 5 Wimp
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Results of survey of Wimp(m,n)Case 2 stringer rolling margin as function of general buckling modal imperfection shape, A(m) x wimp(m,n)
“yes change imperfection amplitude”
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Conclusions
1. There is reasonable agreement of PANDA2, STAGS, & BIGBOSOR4
2. Use “Yes Koiter” option to avoid too-high stresses.
3. Use “Yes change imperfection” option to avoid too-heavy designs.
4. There are other conclusions listed in the paper.