RSA Symposium, 28 Sept. 2011, NTU
ympos um on es gn o ee Structures using Eurocodes
Dynamic fatigue assessment and es gn o on a ner uay rane o Eurocode Eurocode 3 Presented by Associate Professor Lee Chi Kin Division of Structures and Mechanics School of Civil and Environmental Engineering, Nanyang Nanyang Technological echnological University University 28 September 2011 1
RSA Symposium, 28 Sept. 2011, NTU
Topics of presentation Introduction ¾ Actions of fatigue Fatigue Design Philosophy of EN1993-1-9 ¾ Asse Assess ssme ment nt meth method ods s ¾ Partial factors ¾ S-N Curves Curves and and fatigu fatigue e assessm assessment ent Application example: Dynamic Fatigue Assessment of Container Quay Crane ¾ Introduction and structural form ¾ Operations and dynamic actions Conclusions
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RSA Symposium, 28 Sept. 2011, NTU
Introduction ¾ ¾
Actions of fatigue Everything you need to know about fati ue in ten minutes
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RSA Symposium, 28 Sept. 2011, NTU
Introduction
Actions of fatigue Fatigue “The process of initiation and propagation of fluctuating stress” (EN1993-1-9, stress” (EN1993-1-9, 1.3.1.1) Fatigue design and assessment could be one of the main criteria for ultimate limit states check for many structures subjected to cyclic loadings
“Cantilevered” Headquarters, Lamar Construction Corporation Hudsonville, Michigan 4 4
RSA Symposium, 28 Sept. 2011, NTU
Introduction
Everything you need to know about fatigue in 10 minutes Basic actions, concept of fatigue failure
Constant amplitude stress range Q or σ
S‐N curves for different details
time
Q => Δσ welding
Δσ or “S” (log scale)
Δσ
1
Q => Δσ m=3
bolts
Q => Δσ
No. of cycles to failure or “N” (log scale)
Q => Δσ
Constant amplitude
‐ Higher stress and stress range =k Δσ , k>1 near connection => Modified nominal stress range
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RSA Symposium, 28 Sept. 2011, NTU
Introduction
Everything you need to know about fatigue in 10 minutes How to use the S-N curves for assessment and design? Q => Δσ
Δσ
For fatigue assessment: time Determine Q, then Δσ and N , ’ (FAT check in EC3)
Δσ or “S” (log scale)
Q or σ
Δσ
N No. of cycles to failure or “N” (log scale)
For fatigue design: Determine Q, select plate thickness and other details, com ute Δσ , and than N , check for client’s requirement (FAT check in EC3)
5%, 2.3%)
. .
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RSA Symposium, 28 Sept. 2011, NTU
Introduction
Everything you need to know about fatigue in 10 minutes Some important remarks Q => Δσ
Q => Δσ
k Δσ (depends on opening size) ¾ For a given values of Q, value of k Δσ depends on the geometry and details , . ¾ To help designers, many design guides (e.g. BS 7608 and EN1993-1-9)
provide tables for different standard construction details (“Detail Category” ) w c re a e e nom na s ress range Δσ o a g ven s an ar - curve S-N curve No.
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RSA Symposium, 28 Sept. 2011, NTU
Introduction
Everything you need to know about fatigue in 10 minutes Some important remarks ¾ S-N curve is a log-log curve => N quickly reduced as Δσ increases ¾ For any structural detail that is not included in the design guide or
non-uniform stress distribution occurred, designers should use other aids and tools e. . stress concentration formula charts and tables to obtain the modified nominal stress (Hot Spot Stress) ¾ Finite element analysis may be needed to estimate the value of hot
spo s ress ¾ Use of numerical methods implies that both global and local
structural anal ses are often needed => Fati ue desi n could be more demanding in both structural analysis and detail stress analysis than strength design
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RSA Symposium, 28 Sept. 2011, NTU
Introduction
Everything you need to know about fatigue in 10 minutes ar a e amp u e s ress range ¾ In practice, constant amplitude stress range is anything but exception range (or stress spectrum) ¾ The number of occurrences of different stress ranges can be counted
y us ng
e reservo r me o B
B
Δσ 1 Δσ 2
Δσ 1 Δσ A
Δσ 3
2
A C
Time
Cycles
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RSA Symposium, 28 Sept. 2011, NTU
Introduction
Everything you need to know about fatigue in 10 minutes a gue assessmen
or var a e amp u e s ress range
¾ For variable amplitude stress range
, contributed by different stress ranges is used or a g ven s ress range σ i e corresponding cycle to failure, N Ri is found from an appropriate S-N curve ¾ Damage factor: nEi / N Ri n n Ei ¾ Damage Dd = i =1 Ri
(Palmgren-Miner’s summation)
n Ei y c n e q e r F
Stress range
Δσ i
Δσ i (Qk )
¾ Acceptable if Dd < 1.0
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RSA Symposium, 28 Sept. 2011, NTU
EN1993-1-9 ¾
Assessment methods
¾
S-N Curves and fatigue assessment
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RSA Symposium, 28 Sept. 2011, NTU
Fatigue design philosophy of EN1993-1-9
Assessment methods - ¾ The damage tolerance method “Provide acceptable reliability so that a structure will perform satisfactorily
for its design life, provide that a prescribed inspection and maintenance regime for detecting and correcting fatigue is implemented” (EN1993-1-9) 9 Potential fatigue crack initiation size should be accessible 9 Checks on crack initiation 9 Specified minimum size of detectable fatigue crack 9 Specified maximum tolerable size of crack (using fracture mechanics) 9 Time taken for fatigue crack to grow from minimum to maximum size
(T1) 9 Inspection/out of service and repair/strengthening plans
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RSA Symposium, 28 Sept. 2011, NTU
Fatigue design philosophy of EN1993-1-9
Assessment methods - ¾ The safe life method “Provide acceptable reliability so that a structure will perform satisfactorily
for its design life without the need for regular in-service inspection for fatigue damage. It should be applied in cases where local formation of cracks in one com onent could ra idl lead to failure of the element or structure” (EN1993-1-9) The safe life method is recommended by BS and SS NA for new buildings
or c v eng neer ng s ruc ures What are the differences in the design procedures for the damage
tolerance method and the safe life method? Same assessment procedure but the damage tolerance method allows for higher stress range ( ≈17%) than the safe design method
an erent s cause method
ya
g er part a actor γ Mf va ue or t e sa e
e
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RSA Symposium, 28 Sept. 2011, NTU
Fatigue design philosophy of EN1993-1-9
The partial factors The partial load factors γ Ff for safe life method As usual, appears everywhere when stress ranges are used Depends on how the characteristic loads are determined Values given in BS and SS NA (only for safe life design)
No. of S.D. on load intensity 0 +1 +
S.D on intensity
No. of S.D. on no. of cycles 0 +2 1.5 1.4 1.3 1.2 . .
σ
r Δσ o Q
S.D on cycles
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RSA Symposium, 28 Sept. 2011, NTU
Fatigue design philosophy of EN1993-1-9
The partial factors The partial material factors Mf Appears whenever resistances/strengths (N ) are used Depends on how the assessment method used EN1993-1-9 suggested values (Clause 3.7 (b), Table 3.1)
Assessment method Damage tolerant Safe life
Unreasonable to use 1.15 >1.10 here. Hence 1.10
Consequence of failure Low High 1.00 1.15
1.15 1.35
BS and SS NA suggested a value .
Remarks: If a value of γ Mf =1.10 is used throughout, no difference
between the dama e tolerant method and the safe life method
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RSA Symposium, 28 Sept. 2011, NTU
Fatigue design philosophy of EN1993-1-9
The S-N curves and fatigue assessment - . . ¾ Tri-linear log-log curves of
(life to failure) cycles
Δσ C at 2 million cycles (curve labels
¾ Based on 5% probability of
a ure
Constants amplitude fatigue limit
¾ Curves labeled by the
detail cate or nominal stress range corresponding to 2 million cycles, Δσ C
m=3
onstant amplitude atigue limit at 5 million cycles ¾ Cut-off limit at 100 million
cycles
m=5
Cut-off limit
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RSA Symposium, 28 Sept. 2011, NTU
Fatigue design philosophy of EN1993-1-9
The S-N curves and fatigue assessment
The S-N curves used in EN1993-1-9 (Fig. 7.1)
¾ The nominal stress ran e corres ondin to 2 million constant
amplitude cycles, Δσ C , is used as the reference fatigue strength for the curve. It also labels the curve (detail category). , , nominal stress range of 100MPa will able to fail the detail in 2 million cycles ¾ The S-N curve can be written as
( Δσ R )mN R = ( Δσ c )m(2x10 6 ) ¾ Δσ R and N R are respectively the design strength and life of the
detail category
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RSA Symposium, 28 Sept. 2011, NTU
Fatigue design philosophy of EN1993-1-9
The S-N curves and fatigue assessment - . . Some important remarks Ff
Mf
¾ Between the constant amplitude limit (5 million cycles) and the cut-
off limit, the slope of the curve is 1/m = 1/5 ¾ The 1/m=1/5 part is for stress spectrum that consists of stress
ranges both above and below the constant amplitude limit ress ranges a ove e cons an amp u e m w cause damage or growth of flaw => Reduce the constant amplitude limit As time oes on, more stress ran es below the constant
amplitude limit shall contribute to crack growth (but at a lower rate with 1/m=1/5)
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RSA Symposium, 28 Sept. 2011, NTU
Fatigue design philosophy of EN1993-1-9
The S-N curves and fatigue assessment - ¾ Two approaches: the stress domain approach and the damage The stress domain approach
- - , y u frequently used => They are mainly material properties ¾ However, “buckling strength, f buc ” does not exist (but
does)
¾ In EN1993-1-9, the reference fatigue strength Δσ C
corresponding to 2 million cycles of failure is used even it is not a ma er a proper y ¾ Δσ C is used in EN993-1-9 to (1) label the S-N curves and (2) for
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RSA Symposium, 28 Sept. 2011, NTU
Fatigue design philosophy of EN1993-1-9
The S-N curves and fatigue assessment - ¾ Damage equivalent factors
i k
constant stress range? ¾ Yes: Through the concept of equivalent damage 1
y c n e u q e r F
Stress range spectrum: Dd = n1 /N R1+ n2 /N R2
n2
N R1 and N R2 from SN curve 1
2
Stress range
ame amage or a cons an stress range Δσ E for n3 cycle Dd = (n3 )/N E . 3 2. Calculate N E 3. From S-N Curve => Δσ E
3
y c n e u q e r F
E
Stress range
Δσ E can be expressed as Δσ E =λ 1Δσ (Qk ), or in general for n stress range spectra
amplitude stress range
) factors Δσ E =λ 1 λ 2 ⋅⋅⋅⋅⋅⋅⋅⋅λ n Δσ (Qk
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RSA Symposium, 28 Sept. 2011, NTU
Fatigue design philosophy of EN1993-1-9
The S-N curves and fatigue assessment - The stress domain approach i ,
i
i
3,
the detail category nor Δσ C ¾ If λ i are known and Δσ E is calculated, fatigue verification against, say 2
million cycles, is reduced to (EN1993-1-9, Clause 8(2)) Ff
Δ C
E , 2 Mf
≤ 1 . 0
Warning: Actual fatigue life required may be more than 2 million cycles
where Δσ E,2 is the equivalent constant amplitude stress range ¾ λ i are not given in EN1993-1-9 and should be specified in the relevant
parts of EN1993 (e.g. crane loading in EN1991-3) which generally are based on simplified loading model
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RSA Symposium, 28 Sept. 2011, NTU
Fatigue design philosophy of EN1993-1-9
The S-N curves and fatigue assessment - The damage domain approach
, which is more representative of the loading expected ¾ Designer needs to obtain information on the loading ranges, frequencies an e r ac ons o e s ruc ures or s m ar s ruc ures Steps for damage domain assessment i
, frequency, actions) on the structure (or similar structures) 2. Global Structural model: Create a global model of the structure 3. Global responses: Compute the responses of the global model (natural frequencies, nominal forces or stresses etc). If possible, verify the results based on in-situ measurements or scaled model test
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RSA Symposium, 28 Sept. 2011, NTU
Fatigue design philosophy of EN1993-1-9
The S-N curves and fatigue assessment - Steps for damage domain approach (continued)
.
, at locations/details of interests and then their corresponding variable stress range spectra .
Note that if the interested detail could not be found in the detail category of
EN1993 (or further stress concentration appears), local models (e.g. FE models) should be created to compute the stress range spectra (Δσ i )
5. Cycles to failure: Factor the stress range spectra to generate the design spectra ( γ Ff Δσ i ) and then check against the factored S-N curve 6. Damage verification: Compute damage due to different stress range and then the total damage by the Miner’s summation For variable amplitude stress range, damage caused by both stress range
above and below the constant stress range limit must be computed
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RSA Symposium, 28 Sept. 2011, NTU
Fatigue design philosophy of EN1993-1-9
The S-N curves and fatigue assessment - What to do if a given detail failed the verification?
ncrease e c ness o mem ers e a s no re- es gn needed) 9 Reduce nominal stress ran e 9 Thickness correction factor for some details with thickness > 25mm ¾ Upgrade the details to next details category ( ≈12% increase in stress range) => local re-design (e.g. connection details) ¾ Re-design of global structural form (e.g. damping, members
arrangement and sizes) => Improve overall responses of structure, reduce forces in members
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RSA Symposium, 28 Sept. 2011, NTU
Fatigue design philosophy of EN1993-1-9
Comparison with BS 7608 BS5950 steel structures
a gue es gn and assessment of steel structures n orma ve annexes and references
BS5400 Steel, concrete and composite bridges
Structural Dynamic Fracture mechanics In general: BS more comprehensive Easier to use Less iterations in reading More designer friendly But (perhaps) similar results
Other EN: EN1991, EN1993, NCCI and PD EN1993-1-9 Design of steel structures: Fatigue “Minimum” Annexes NA to EN1993-1-9: Choices of parameters
Similar details given
Partial factors in EN More complete detail category in EN
, Shear and combine stress failure in some EN details Thickness correction: BS >16mm, EN >25mm
PD6695-1-9-2008 Recommendations, information for design and use
.
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RSA Symposium, 28 Sept. 2011, NTU
pp ca on examp e: ynam c Fatigue Assessment of Container Quay Crane ¾
Introduction and structural form
¾
Quay crane fatigue assessment
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Introduction and structural form Container Quay Crane (CQC) ¾
A special from of gantry crane
¾
Key machinery for efficient port operations
¾
Main functions: load and unload container to/from ships
¾
Special lifting device called a spreader for loading and discharging of containers
¾
Horizontal gantry rails for quayside movement
¾
Driven by an operator that sits in a cabin suspend from the trolley runs along rails (hoist block )
¾
Lorries/straddle-carriers move underneath the base of t e quay crane
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Introduction and structural form ¾ Typical dimensions: Boom level: +44m Overall height: 75m Boom length: 55m
A-frame
Backstay
Forestay Support beams Boom
Leg spacing: 30m ¾ Outreach:18 containers ¾ Self Weight: up to 2000
tons ¾ Trolley, machine and
Trolley
Landside upper leg
Spreader container
Landside lower leg
spreader (Hoist block) we g t: tons Portal girders Sill beams 28
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Introduction and structural form
Structural form
¾
“Machine-on-trolley” design => Crane machinery moves with trolley for
¾
Designed as a “structure” of thin-plate box girder (plate thickness≤22mm) with many longitudinal and transverse stiffeners
¾
Low stress level in STR limit state: Typical stress level < 50MPa ( f y of steel = 420MPa). For EQU limit: Only 4 legs provide no redundancy
¾
oom ra
es gn ase on
e cons era on o crane ac ons
¾
FAT limit state is critical in design and services: Owner may prefer to s ecific the FAT limit state in terms of the numbers of c cles of operations instead of years of service
¾
Frequent maintenance and services check (4-6 days per year)
¾
Dynamic fatigue analysis is deemed to be compulsory
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Operations and dynamic actions
Operations
¾ Hoist block load and unloading container to ship and truck
Ship-to-Truck (S-T) and Truck-to-Ship (T-S)
Dynamic loadings
¾
Movement of crane along wharf-line railway (gantry movement) Slow and relativity low frequency of occurrence: not critical Wind loading More severe when the forestay is stowed Not critical for Singapore terminals but critical for places like HK due to t hoon Dynamic loadings due to S-T and T-S movements of hoist block High frequency operations (S-T and T-S Cycles)
¾
¾
Effect could be highly localized
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Operations and dynamic actions ¾ Cycle counting: one cycle per every S-
T (or T-S) operation operations ms: mass of spreader mt : mass o ro ey w mac ne mc : mass of container (variable) av : vertical acceleration of spreader aH : horizontal acceleration of trolley With container Vertical : F = m +m a Horizontal : F H = (ms+mt +mc )( aH ) Without container = Horizontal : F H = (ms+m )( ) t aH
av
18 rows for the CQC studied, row 1 nearest to dock
aH
p Sea-to-truck Truck-to-sea
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Quay crane fatigue assessment
Overall assessment procedure rea e mo e for global dynamic analysis
Identify fatigue prone oca ons and obtain the stress range s ectrum
Some could only be
Global dynamic
Could be obtained
measurements
wireframe models
measurements or by detailed 3D solid FE modelling
data (aV , aH , mt , mc , ms and frequencies)
assessment by using suitable rules
Butt weld
Fillet weld
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Backstay tip
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Quay crane fatigue assessment
Global dynamic analysis
¾ Governin
e uation of the s stem in term of dis lacement u
&& + C u& + Ku = F (mg, oper(t), T(t), env(t)) u Self-weight
Operations Temperature Environmental
¾ Wireframe model for dynamic analysis ¾ Dimensions and sections details from
cons ruc on raw ngs ¾ 430 joints, 353 beam-column elements, approx. 2600 DOF ¾ Hoist block modelled as point mass and point load while other utilities as distributed loads ¾ Lump mass matrix, single damping factor
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Quay crane fatigue assessment
Global dynamic analysis
¾ To predict the following structural properties of
the CQC under dynamic loading 9 Natural frequencies and mode shapes (1st horizontal 0.64Hz, 1st vertical 1.16Hz) 9 Member forces and force ranges 9 Fatigue prone location(s) = Design spectra due to different operations ¾ Key parameters to be calibrated: shape (for different locations of hoist block) 9 Ground support conditions (spring stiffness for 9 Damping factors
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Quay crane fatigue assessment
In situ measurements
¾ Two different tests done with real time
¾ 9
9 9
Extreme land position
Row 18
measuremen s: on ro es an Operation test Control test Separated horizontal hoisting and veridical lifting operations with maximum container weight followed by free vibration Provide specific excitations Responses monitored: Deflection at sea side boom end by HD video Accelerations: Two accelerometers Member forces: Strain au es at two levels, on the four side walls of one of the lower land side legs
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Quay crane fatigue assessment
Control test results and calibrations
¾ “Stiff” (150kN/mm) ground support condition
gave best modelling results ¾ Natural frequencies correctly predicted by the model ¾ There is a small change in natural frequencies when the hoist block moved from extreme sea side to extreme land side (≈5%) ¾ Deflections and strain gauges readings compared well with the model Under static loading deflection range at sea side boom end ≈ 240mm ≈1/460 of boom+ girder
,
=
¾ Damping factors obtained by tracing the peak
res onse deca rate durin free vibration ¾ Horizontal actions: 1%, vertical actions: 0.25% of critical damping ratio
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Quay Crane fatigue assessment
Critical locations and key parameters
¾ From the control test and global model,
the stiffener ends of sea facing walls of the lower land side legs ¾ The horizontal motions of the hoist block is more critical (≈3-5 times higher in stress range) than vertical lifting of container ¾ Other critical parameters that affecting Loading and unloading rows Weight of container
or zon a an ver ca acce era ons o e hoist block and container during operation => operator’s “style” 38 38
RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Quay Crane fatigue assessment
Operation test
¾ To obtain magnitudes, distributions and frequency of critical parameters:
, containers Loading/unloading times a a o a ne rom oa ng an un oa ng opera ons “ uns” on a sma container ship (operation rows 1 to 6), 7 runs from ship-to-truck and 28 runs from truck-to-ship v eo recor s or o s oc or zon a mo ons an con a ner ver ca motions ¾ Accelerometers (on trolley) and strain gauges measurements (side walls of ower an s e eg ¾ In addition, the starting/ending rows distributions during loading/unloading operations from 10 years record (0.85 million operations) from crane owner
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Quay Crane fatigue assessment
Motions paths for hoist block and container
¾ The horizontal acceleration of the hoist block and the vertical acceleration of the
container are the two most important parameters that affect the dynamic forces applied and stress range induced
Motion path of
h Position S
S m
hm
S d os
on
h s
S
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Quay Crane fatigue assessment
Motions paths for hoist block and container
Operator accelerated/braked whenever he/she felt necessary for operations or to achieve a minimum time of travel
Motion plot
Velocity and acceleration for a typical cycle
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Quay Crane fatigue assessment
Motions equations
¾
Velocity and acceleration limits of hoist block and container: max =
¾
.
,
max =
.
2 ,
vmax =
.
,
max =
2
.
All operators would try to minimize the time needed for each operation (within safety limits). Actual travel time depends on the skill and style of operator Different “forms” of motion equations were employed to represent the style and skill of operator
Six variables (Initial and final positions, velocities and accelerations) are required to define the initial and final conditions of the hoist block
Assuming
the position of the hoist block is a fifth order polynomial of time =
Acceleration
2
3
4
5
is then a cubic polynomial: aH =2c 3 + 6c 4t+ 12c 5 t 2 + 20c 6 t 3
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Quay crane fatigue assessment
Motions equations
¾
From the maximum velocity and acceleration, the minimum time of travel T (cubic) could be obtained
¾
The cubic acceleration form is corresponding to a “gentle” operator who tries to achieve a gentle acceleration/deceleration throughout the operation “ ” the order and “smoothness” of the acceleration equation to 1. Linear acceleration form => T min(linear) 2. Constant acceleration form=> T min(const)
¾
The constant acceleration form is corresponding to a “swift” operator who alwa s able to use the hoist block en ine u to its mechanical limit so that T min(cubic) > T min(linear) > T min(const)
¾
The main function of motion equations is not to reproduce the measured acceleration forces)
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Quay Crane fatigue assessment
Motions equations
¾
Checking with actual travel time from HD video records confirmed that the constant acceleration form could give a lower bound of the travel time => maximum dynamic forces
¾
For vertical motions of spreader, similar approach was used and it was found that a linear form is appropriate
50
Cubic form
45
40
) 35 s ( e m i t
Linear form
30 m u m i n i M25
Constant form
20
15
10 30
40 With container
50 Tmin(Con)
60
70
Sm(m) without container
Tmin(Lin)
80 Tmin(Cubic)
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Quay crane fatigue assessment
Dynamic loading on quay crane
¾
The final dynamic loading is the combination of horizontal and vertical . , were not synchronized as the operator needed to avoid obstacles (other containers in ship) during operation
¾
The dynamic loadings were applied with the following combinations to obtained the member force ranges 7 6 Rows 1 to 18 s n o i t 5 a S-T and T-S operations r e 0, 20, 40 tons =>Totally 108 analyses
p o 4 f o e g 3 a t n e c 2 e r P
1 0 1
2
3
4
5
6
7
8
9 ow
10 11 12 13 14 15 16 17 18 um er
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Quay crane fatigue assessment
Damage assessment
¾
No special treatment on resonance since period of operations >> > => -
¾
Lower land side leg walls nominal stress ranges:
From operation test measurement (Rows 1-6): 22MPa to 40MPa
Predicted from dynamic models (Rows 1-6): 31MPa to 55MPa
Higher stress ranges from S-T operations
Maximum stress range from S-T operation with 40 ton container, Row 18 operation => 83MPa (c.f. static range = 37MPa) = .
¾
For other parts such as backstay and addition bracing, FE analysis needed to calculate stress range from member force ranges
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Quay crane fatigue assessment
Damage assessment Butt weld
Fillet weld
Backstay tip
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RSA Symposium, 28 Sept. 2011, NTU
Dynamic Fatigue assessment of Container Quay Crane
Quay crane fatigue assessment ¾
From nominal/Hot spot stress, perform fatigue design/check by using the appropriate S-N curves 2.3 % failure probability curve was used (or 5% failure probability curve with γ Mf =1.10) Lower land side leg wall details shall be safe for at least 20 years’ services Damage contributions from different rows’ operations 12
n o 10 i t u b i r t n 8 o c e g a m 6 a d f o e g 4 a t n e c e r P 2
0 1
2
3
4
5
6
7
8
9
10
Row Number
11
12
13
14
15
16
17
18
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