12 april 2001northern california sname meeting 1 fatigue prediction verification of fiberglass hulls...
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12 April 2001 Northern California SNAME Meeting 1
Fatigue Prediction Verification of Fiberglass Hulls
Paul H. MillerDepartment of Naval Architecture and Ocean Engineering
U. S. Naval Academy
12 April 2001 Northern California SNAME Meeting 2
Why Study Fiberglass Fatigue?
• Approximately 30% of structural materials now used in the marine environment are fiberglass.
• Little long-term fatigue data exists.
• 1998 Coast Guard data shows 118 fiberglass failures resulting in 6 fatalities
12 April 2001 Northern California SNAME Meeting 3
This Project’s Goals
• Extend the standard fatigue methods used for metal vessels to composite vessels
• Verify the new method by testing coupons, panels and full-size vessels.
12 April 2001 Northern California SNAME Meeting 4
Background-Current ABS Composite Design Methods
• Semi-empirical, theory and previous vessels
• Quasi-static “head”
• Beam and isotropic plate equations
• Conservative
• 2.33 for bulkheads
• 3 for interior decks
• 4 for hull and exterior decks
Factors of Safety(Working Stress Design)
Includes fatigue and uncertainties in loads
12 April 2001 Northern California SNAME Meeting 5
Simplified Metal Ship Fatigue Design
1. Predict wave encounter ship “history”
2. Find hull pressures and accelerations using CFD for each condition
3. Find hull stresses using FEA• Wave pressure and surface elevation• Accelerations
4. Use Miner’s Rule and S/N data to get fatigue life
12 April 2001 Northern California SNAME Meeting 6
Project Overview
• Material and Application Selection
• Testing (Dry, Wet/Dry, Wet)• ASTM Coupons, Panels, Full Size• Static and Fatigue
• Analysis• Local/Global FEA• Statistical and Probabilistic
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Material & Application Selection
• Polyester Resin (65%)• E-glass (73%)• Balsa Core (30%)• J/24 Class Sailboat
• 5000+ built• Many available locally• Builder support• Small crews
Ideally they should represent a large fraction of current applications!
Another day of research…
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Target Structure Analysis• Hull Shell Design
• 35% of LWL aft of Fwd Perpendicular• 0 to 1’ off CL
• Determine loss of stiffness vs. stress cycle history (microcracking)
• Requires knowing load effects and test method bias
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Loads on Target Area
• Hydrostatic
• Hydrodynamic• Slamming• Wave slap• Motion• Foil lift/drag
• Moisture
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Quantified Material Properties• Mostly linear stress/strain
• Brittle (0.8-2.7% ultimate strain)
• Stiffness and Strength Properties Needed (ASTM tests – Wet/Dry)• Tensile• Compressive • Shear• Flex• Fatigue
E-glass Mat/Polyester Sample #1
0
5000
10000
15000
20000
0 0.05 0.1 0.15 0.2 0.25
Extension [in]
Stre
ss [
psi]
Tensile Test
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Moisture Background and Tests
• Porous materials (up to 2% weight)• Few documented moisture failures• Test results ambiguous (Stanford vs.
UCSD)• Test methods suspect (long-term vs.
boiling)• Fickian Diffusion• Tested for 1 year
• Dry, 100% relative humidity, submerged
12 April 2001 Northern California SNAME Meeting 12
Moisture Absorption Results
0.00%
0.50%
1.00%
1.50%
2.00%
2.50%
0 33 66 99 132 165 198 231Days
Weig
ht G
ain
TNR TNW SNR SNW Fickian
1.8% weight gain for submerged
1.3% for 100% relative humidity
Equilibrium in 4 months
These results were used for coupon and vessel test preparation.
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Finite Element Analysis
• Coupon, panel, global• Element selection
• Linear/nonlinear• Static/dynamic/quasi-static• CLT shell• Various shear deformation theories used
(Mindlin and DiScuiva)
• COSMOS/M software• Material property inputs from coupon
tests
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Coupon Test Results
• Tensile Mod: 1.2 msi dry, -12% wet, -13% boiled
• Shear Mod: 0.56 msi dry, -11% wet, -16% boiled
• Comp Mod: 0.92 msi dry, -6% wet, -12% boiled
• Tensile Str: 11.3 ksi dry, -20% wet, -24% boiled
• Shear Str: 5.5 ksi dry, -11% wet, -22% boiled
• Comp Str: 25.3 ksi dry, -16% wet, -25% boiled
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Coupon FEA Results
Strains were within 2%, strength within 15%
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Fatigue Analysis for Vessels
0 )(
)(
i
i
sN
dsspfTDE
E[D] = the expected accumulated damage ratioT = the time at frequency fp(si) = the probabilistic distribution of the number of
stress cycles at stress si
N(si) = the number of cycles to failure at stress si
)()(
)cos(),()()()()(
wsswsw
wswsws UTUU
UUUfUpmppfT
12 April 2001 Northern California SNAME Meeting 18
Fatigue Results – S/N Data
70%
80%
90%
100%
1 10 100 1,000 10,000 100,000 1,000,000
Stress Cycles
Pe
rce
nt
of
Ori
gin
al S
tiff
ne
ss
12.5%-Wet 12.5%-Dry 25%-Wet 25%-Dry 37.5%-Dry37.5%-Wet 50%-Dry 50%-Wet 75%-Dry 75%-Wet
Specimens failed when stiffness dropped 15-25%No stiffness loss for 12.5% of static failure load specimens25% load specimens showed gradual stiffness loss
Moisture decreased initial and final stiffness but the rate of loss was the same.
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Panel Analysis• Responds to
USCG/SNAME studies
• Solves edge-effect problems
• Hydromat test system
• More expensive
• Correlated with FEA
12 April 2001 Northern California SNAME Meeting 20
Panel Test Results
0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0.9
1
0 2 4 6 8 10 12 14
Pressure (psi)
Def
lect
ion
(in
)S
trai
n (
%)
Wet Defl Dry Defl Wet Strain Dry Strain
Wet vs. Dry results were similar to those from coupons; the one-sided wet specimens were marginally less stiff.
12 April 2001 Northern California SNAME Meeting 21
Panel FEA Results
0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0.9
1
0 2 4 6 8 10 12 14
Pressure (psi)
De
fle
ctio
n (
in)
Wet Deflection Dry DeflectionPanel Linear Panel NonLinPanel & Frame NonLin Panel & Frame Linear
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Impact Testing• The newest boat had the lowest stiffness.
• Did the collision cause significant microcracking?
Yes, there was significant microcracking!
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Global FEA
• Created from plans and boat checks• Accurately models vessel
• 8424 quad shell elements• 7940 nodes• 46728 DOF
• Load balance with accelerations
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Full-Size Testing – Boat History
• High Mileage – J6• Daily records for 3 years• Annual records since
new• NOAA wind records for
the same period (daylight)
• Course distribution• Velocity prediction
program for speed
The Bottom Line for J6:• 11,300 hours sailing• 10,200,000 wave encounters• The “low mileage” boat had 740 hours and 600,000
waves
0
20
40
60
80
100
120
Janu
ary
Feb
ruar
y
Mar
ch
Apr
il
May
June
July
Aug
ust
Sep
tem
ber
Oct
ober
Nov
embe
r
Dec
embe
r
J6 S
ailin
g H
ou
rs
1996 1997 1998 1999 Ave
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On-The-Water Testing- Set Up
Instrument LocationStrain Gage #1 Portside shroud chainplateStrain Gage #2 Forestay chainplateStrain Gage #3 Inside hull on centerlineStrain Gage #4 Inside hull off centerlineStrain Gage #5 Outside hull on centerlineStrain Gage #6 Outside hull off centerlineAccelerometer Bulkhead aft of strain gages
Instrument Locations for Boat Tests
Location ofsink through-hull (behindfender)
Location of straingauges (underepoxy)
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Data Records
J6 TestImajinationTest
Wind0
0.0002
0.0004
0.0006
0.0008
0.001
0.0012
0.0014
0.0016
2:29
:00
PM
2:29
:02
PM
2:29
:05
PM
2:29
:07
PM
2:29
:09
PM
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PM
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:14
PM
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:20
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:25
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:27
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PM
2:29
:32
PM
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:34
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:36
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:41
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Inside on CL Inside off CL
Strains
-0.06
-0.04
-0.02
0
0.02
0.04
0.06
0.08
0.1
0.12
2:29
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PM
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AccelAccelerations
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Slamming FEA
Inner Skin Outer Skin
Using measured accelerations and wave heights from pictures strains were 0.21% for inner and 0.17% for outer. (23% & 18% of ultimate strain)
WS=22.5 knots
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Comparison of Results• Slamming (Low Mileage
Boat- “Imajination”)• Peak measured 0.136%• Ave. of measured peaks
0.117%• FEA prediction 0.125%
Imajination J6Predicted Stiff Reduction -3% -14%
Measured with Strain Gauges -4% -18%
Global "String Test" -14% -52%
With all the fatigue cycles included, the stiffness loss is:
12 April 2001 Northern California SNAME Meeting 31
The Most Useful Conclusions
• The Metal Ship Fatigue Design Process can be extended to composite vessels
• Current factors will lead to fatigue lives of 10-30 years
• Visual clues for fatigue failure are evident
• Stiffness loss may be a better method of prediction
• Good FEA accuracy requires a lot of work!