Fender Design Trelleborg Doc
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Fender Design Section 12
Trelleborg Marine Systems
www.trelleborg.com/marine Ref. M1100-S12-V1-3-EN
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Ship Tables Berthing Modes Coefficients Berth Layout Panel Design Materials Fender Testing 13/04/2011 2:55 PM
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FENDER DESIGN Fenders must reliably protect ships, structures and themselves. They must work every day for many years in severe environments with little or no maintenance. As stated in the British Standard†, fender design should be entrusted to ‘appropriately qualified and experienced people’. Fender engineering requires an understanding of many areas: B B B B B B B B
Ship technology Civil construction methods Steel fabrications Material properties Installation techniques Health and safety Environmental factors Regulations and codes of practice
Using this guide This guide should assist with many of the frequently asked questions which arise during fender design. All methods described are based on the latest recommendations of PIANC* as well as other internationally recognised codes of practice. Methods are also adapted to working practices within Trelleborg and to suit Trelleborg products. Further design tools and utilities including generic specifications, energy calculation spreadsheets, fender performance curves and much more can be downloaded from the Trelleborg Marine Systems website (www.trelleborg.com/marine).
Codes and guidelines ROM 0.2-90
1990
Actions in the Design of Maritime and Harbor Works
† BS6349 :
1994
Code of Practice for Design of Fendering and Mooring Systems
Part 4 : 1994
Exceptions
EAU 1996
1996
Recommendations of the Committee for Waterfront Structures
These guidelines do not encompass unusual ships, extreme berthing conditions and other extreme cases for which specialist advice should be sought.
PIANC Bulletin 95
1997
Approach Channels – A Guide to Design Supplement to Bulletin No.95 (1997) PIANC
Japanese MoT 911
1998
Technical Note of the Port and Harbour Research Institute, Ministry of Transport, Japan No. 911, Sept 1998
* PIANC 2002
2002
Guidelines for the Design of Fender Systems : 2002 Marcom Report of WG33
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GLOSSARY Commonly used symbols Symbol B C CB CC CE CM CS D EN EA FL FS H K KC LOA LBP LS LL M M50 M75 MD P R RF V VB α δ θ μ ϕ
Definition Beam of vessel (excluding beltings and strakes) Positive clearance between hull of vessel and face of structure Block coefficient of vessel’s hull Berth configuration coefficient Eccentricity coefficient Added mass coefficient (virtual mass coefficient) Softness coefficient Draft of vessel Normal berthing energy to be absorbed by fender Abnormal berthing energy to be absorbed by fender Freeboard at laden draft Abnormal impact safety factor Height of compressible part of fender Radius of gyration of vessel Under keel clearance Overall length of vessel’s hull Length of vessel’s hull between perpendiculars Overall length of the smallest vessel using the berth Overall length of the largest vessel using the berth Displacement of the vessel Displacement of the vessel at 50% confidence limit Displacement of the vessel at 75% confidence limit Displacement of vessel Fender pitch or spacing Distance from point of contact to the centre of mass of the vessel Reaction force of fender Velocity of vessel (true vector) Approach velocity of the vessel perpendicular to the berthing line Berthing angle Deflection of the fender unit Hull contact angle with fender Coefficient of friction Velocity vector angle (between R and V)
Units m m – – – – – m kNm kNm m – m m m m m m m tonne tonne tonne tonne m m kN m/s m/s degree % or m degree – degree
Definitions Rubber fender
Units made from vulcanised rubber (often with encapsulated steel plates) that absorbs energy by elastically deforming in compression, bending or shear or a combination of these effects.
Pneumatic fender
Units comprising fabric reinforced rubber bags filled with air under pressure and that absorb energy from the work done in compressing the air above its normal initial pressure.
Foam fender
Units comprising a closed cell foam inner core with reinforced polymer outer skin that absorb energy by virtue of the work done in compressing the foam.
Steel Panel
A structural steel frame designed to distribute the forces generated during rubber fender compression.
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WHY FENDER? ‘There is a simple reason to use fenders: it is just too expensive not to do so’. These are the opening remarks of PIANC* and remain the primary reason why every modern port invests in protecting their structures with fenders. Well-designed fender systems will reduce construction costs and will contribute to making the berth more efficient by improving turn-around times. It follows that the longer a fender system lasts and the less maintenance it needs, the better the investment. It is rare for the very cheapest fenders to offer the lowest long term cost. Quite the opposite is true. A small initial saving will often demand much greater investment in repairs and upkeep over the years. A cheap fender system can cost many times that of a well-engineered, higher quality solution over the lifetime of the berth as the graphs below demonstrate.
10 reasons for quality fendering B B B B B B B B B B
Capital costs
Maintenance costs 700
180 160
120
500
400
80
300
Purchase price
100
60 40 20
Trelleborg
200
rg
o Trelleb
100
Other
Purchase price + Design approvals + Delivery delays + Installation time + Site support = Capital cost
er Oth
Other costs
600
140
0
Safety of staff, ships and structures Much lower lifecycle costs Rapid, trouble-free installation Quicker turnaround time, greater efficiency Reduced maintenance and repair Berths in more exposed locations Better ship stability when moored Lower structural loads Accommodate more ship types and sizes More satisfied customers
0
10
20 30 Service life (years)
40
50
Wear & tear + Replacements + Damage repairs + Removal & scrapping + Fatigue, corrosion = Maintenance cost
Capital cost + Maintenance cost = FULL LIFE COST
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DESIGN FLOWCHART Functional B type(s) of cargo B safe berthing and mooring
B better stability on berth B reduction of reaction force
Operational B berthing procedures B frequency of berthing B limits of mooring and operations (adverse weather) B range of vessel sizes, types B special features of vessels (flare, beltings, list, etc) B allowable hull pressures
B light, laden or partly laden ships B stand-off from face of structure (crane reach) B fender spacing B type and orientation of waterfront structure B special requirements B spares availability
Site conditions B wind speed B wave height B current speed
B topography B tidal range B swell and fetch
B temperature B corrosivity B channel depth
Design criteria B B B B B B
codes and standards design vessels for calculations normal/abnormal velocity maximum reaction force friction coefficient desired service life
B B B B B
safety factors (normal/abnormal) maintenance cost/frequency installation cost/practicality chemical pollution accident response
Design criteria
Calculation of berthing energy
Mooring layout CC berth configuration factor CS softness factor
CM virtual mass factor CE eccentricity factor
B location of mooring B strength and type B pre-tensioning of equipment and/or dolphins of mooring lines mooring lines
Calculation of fender energy absorption
Assume fender system and type
B selection of abnormal berthing safety factor
Computer simulation (first series) Selection of appropriate fenders Check results Determination of: B energy absorption B reaction force B deflection
B check vessel motions in six degrees of freedom B check vessel acceleration
B environmental factors B frictional loads B angular compression B chains etc B hull pressure
Check impact on structure and vessel B horizontal and vertical loading B chance of hitting the structure (bulbous bows etc) B face of structure to accommodate fender
B check deflection, energy and reaction force B check mooring line forces
Computer simulation (optimisation)
B implications of installing the fender B bevels/snagging from hull protrusions B restraint chains
Final selection of fender B determine main characteristics of fender B PIANC Type Approved B verification test methods
B B B B
check availability of fender track record and warranties future spares availability fatigue/durability tests
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THE DESIGN PROCESS Many factors contribute to the design of a fender:
Ships Ship design evolves constantly – shapes change and many vessel types are getting larger. Fenders must suit current ships and those expected to arrive in the foreseeable future.
Structures Fenders impose loads on the berthing structure. Many berths are being built in exposed locations, where fenders can play a crucial role in the overall cost of construction. Local practice, materials and conditions may influence the choice of fender.
Berthing Many factors will affect how vessels approach the berth, the corresponding kinetic energy and the load applied to the structure. Berthing modes may affect the choice of ship speed and the safety factor for abnormal conditions.
Installation and maintenance Fender installation should be considered early in the design process. Accessibility for maintenance, wear allowances and the protective coatings will all affect the full life cost of systems. The right fender choice can improve turnaround times and reduce downtime. The safety of personnel, structures and vessels must be considered at every stage – before, during and after commissioning.
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ENVIRONMENT Typical berthing locations Berthing structures are located in a variety of places from sheltered basins to unprotected, open waters. Local conditions will play a large part in deciding the berthing speeds and approach angles, in turn affecting the type and size of suitable fenders.
Non-tidal basins With minor changes in water level, these locations are usually sheltered from strong winds, waves and currents. Ship sizes may be restricted due to lock access.
Tidal basins Larger variations in water level (depends on location) but still generally sheltered from winds, waves and currents. May be used by larger vessels than non-tidal basins.
Coastal berths Maximum exposure to winds, waves and currents. Berths generally used by single classes of vessel such as oil, gas or bulk.
River berths Largest tidal range (depends on site), with greater exposure to winds, waves and currents. Approach mode may be restricted by dredged channels and by flood and ebb tides. Structures on river bends may complicate berthing manoeuvres.
Tides
Currents and winds
Tides vary by area and may have extremes of a few centimetres (Mediterranean, Baltic) or over 15 metres (parts of UK and Canada). Tides will influence the structure’s design and fender selection.
HRT
HRT HAT MHWS MHWN MLWN MLWS LAT LRT
MLWS
Highest Recorded Tide Highest Astronomical Tide Mean High Water Spring Mean High Water Neap Mean Low Water Neap Mean Low Water Spring Lowest Astronomical Tide Lowest Recorded Tide
HAT MHWS MHWN
MSL MLWN
LAT LRT
Current and wind forces can push vessels onto or off the berth, and may influence the berthing speed. Once berthed, and provided the vessel contacts several fenders, the forces are usually less critical. However special cases do exist, especially on very soft structures. As a general guide, deep draught vessels (such as tankers) will be more affected by current and high freeboard vessels (such as RoRo and container ships) will be more affected by strong winds.
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STRUCTURES The preferred jetty structure can influence the fender design and vice versa. The type of structure depends on local practice, the geology at the site, available materials and other factors. Selecting an appropriate fender at an early stage can have a major effect on the overall project cost. Below are some typical structures and fender design considerations.
Features Open pile jetties
B Simple and cost-effective B Good for deeper waters B Load-sensitive B Limited fixing area for fenders
Design considerations B Low reaction reduces pile sizes and concrete mass B Best to keep fixings above piles and low tide B Suits cantilever panel designs
B Vulnerable to bulbous bows
Dolphins
B Common for oil and gas terminals
B Few but large fenders
B Very load-sensitive
B Total reliability needed
B Flexible structures need careful design to match fender loads
B Low reactions preferred
B Structural repairs are costly
Monopiles
B Inexpensive structures B Loads are critical B Not suitable for all geologies B Suits remote locations B Quick to construct
B Large panels for low hull pressures need chains etc
B Fenders should be designed for fast installation B Restricted access means low maintenance fenders B Low reactions must be matched to structure B Parallel motion systems
Mass structures
B Most common in areas with small tides
B Keep anchors above low tide
B Fender reaction not critical
B Care needed selecting fender spacing and projection
B Avoid fixings spanning pre-cast and in situ sections or expansion joints
B Suits cast-in or retrofit anchors B Many options for fender types
Sheet piles
B Quick to construct B Mostly used in low corrosion regions B In situ concrete copes are common B Can suffer from ALWC (accelerated low water corrosion)
B Fixing fenders direct to piles difficult due to build tolerances B Keep anchors above low tide B Care needed selecting fender spacing and projection
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SHIP TYPES General cargo ship B B B B
Prefer small gaps between ship and quay to minimise outreach of cranes. Large change of draft between laden and empty conditions. May occupy berths for long periods. Coastal cargo vessels may berth without tug assistance.
B B B B
Need to be close to berth face to minimise shiploader outreach. Possible need to warp ships along berth for shiploader to change holds. Large change of draft between laden and empty conditions. Require low hull contact pressures unless belted.
B B B B B
Flared bows are prone to strike shore structures. Increasing ship beams needs increase crane outreach. Some vessels have single or multiple beltings. Bulbous bows may strike front piles of structures at large berthing angles. Require low hull contact pressures unless belted.
B B B B
Need to avoid fire hazards from sparks or friction. Large change of draft between laden and empty conditions. Require low hull contact pressures. Coastal tankers may berth without tug assistance.
B B B B B
Ships have own loading ramps – usually stern, slewed or side doors. High lateral and/or transverse berthing speeds. Manoeuvrability at low speeds may be poor. End berthing impacts often occur. Many different shapes, sizes and condition of beltings.
B B B B
Small draft change between laden and empty. White or light coloured hulls are easily marked. Flared bows are prone to strike shore structures. Require low hull contact pressures unless belted.
Ferry
B B B B B
Quick turn around needed. High berthing speeds, often with end berthing. Intensive use of berth. Berthing without tug assistance. Many different shapes, sizes and condition of beltings.
Gas carrier
B B B B B
Need to avoid fire hazards from sparks or friction. Shallow draft even at full load. Require low hull contact pressures. Single class of vessels using dedicated facilities. Manifolds not necessarily at midships position.
Bulk carrier
Container ship
Oil tanker
RoRo ship
Passenger (cruise) ship
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SHIP FEATURES Bow flares
Common on container vessels and cruise ships. Big flare angles may affect fender performance. Larger fender may be required to maintain clearance from the quay structure, cranes, etc.
Bulbous bows
Most modern ships have bulbous bows. Care is needed at large berthing angles or with widely spaced fenders to ensure the bulbous bow does not catch behind the fender or hit structural piles.
Beltings & strakes
Almost every class of ship could be fitted with beltings or strakes. They are most common on RoRo ships or ferries, but may even appear on container ships or gas carriers. Tugs and offshore supply boats have very large beltings.
Flying bridge
Cruise and RoRo ships often have flying bridges. In locks, or when tides are large, care is needed to avoid the bridge sitting on top of the fender during a falling tide.
Low freeboard
Barges, small tankers and general cargo ships can have a small freeboard. Fenders should extend down so that vessels cannot catch underneath at low tides and when fully laden.
Stern & side doors
RoRo ships, car carriers and some navy vessels have large doors for vehicle access. These are often recessed and can snag fenders – especially in locks or when warping along the berth.
High freeboard
Ships with high freeboard include ferries, cruise and container ships, as well as many lightly loaded vessels. Strong winds can cause sudden, large increases in berthing speeds.
Low hull pressure
Many modern ships, but especially tankers and gas carriers, require very low hull contact pressures, which are achieved using large fender panels or floating fenders.
Aluminium hulls
High speed catamarans and monohulls are often built from aluminium. They can only accept loads from fenders at special positions: usually reinforced beltings set very low or many metres above the waterline.
Special features
Many ships are modified during their lifetime with little regard to the effect these changes may have on berthing or fenders. Protrusions can snag fenders but risks are reduced by large bevels and chamfers on the frontal panels.
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BERTHING MODES Side berthing
α Typical values
ϕ
0° ≤ α ≤ 15° 100mm/s ≤ V ≤ 300mm/s
V
60° ≤ ϕ ≤ 90°
Dolphin berthing
α
Tug
Typical values 0° ≤ α ≤ 10°
ϕ
100mm/s ≤ V ≤ 200mm/s 30° ≤ ϕ ≤ 90°
V End berthing
α
Typical values
ϕ
0° ≤ α ≤ 10°
V
200mm/s ≤ V ≤ 500mm/s 0° ≤ ϕ ≤ 10°
Lock entrances
V
Typical values
ϕ
0° ≤ α ≤ 30°
α
300mm/s ≤ V ≤ 2000mm/s 0° ≤ ϕ ≤ 30°
Ship-to-ship berthing
ϕ
α
Typical values 0° ≤ α ≤ 15° 150mm/s ≤ V ≤ 500mm/s
V
60° ≤ ϕ ≤ 90°
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BERTHING ENERGY The kinetic energy of a berthing ship needs to be absorbed by a suitable fender system and this is most commonly carried out using well recognised deterministic methods as outlined in the following sections.
Normal Berthing Energy (EN) Most berthings will have energy less than or equal to the normal berthing energy (EN). The calculation should take into account worst combinations of vessel displacement, velocity, angle as well as the various coefficients. Allowance should also be made for how often the berth is used, any tidal restrictions, experience of the operators, berth type, wind and current exposure. The normal energy to be absorbed by the fender can be calculated as:
EN = 0.5 × M × VB2 × CM × CE × CC × CS Where, EN = Normal berthing energy to be absorbed by the fender (kNm) M = Mass of the vessel (displacement in tonne) at chosen confidence level.* VB = Approach velocity component perpendicular to the berthing line† (m/s). CM = Added mass coefficient CE = Eccentricity coefficient CC = Berth configuration coefficient CS = Softness coefficient * PIANC suggests 50% or 75% confidence limits (M50 or M75) are appropriate to most cases. † Berthing velocity (VB) is usually based on displacement at 50% confidence limit (M50).
Abnormal Berthing Energy (EA) Abnormal impacts arise when the normal energy is exceeded. Causes may include human error, malfunctions, exceptional weather conditions or a combination of these factors. The abnormal energy to be absorbed by the fender can be calculated as:
EA = FS × EN
PIANC Factors of Safety (FS) Vessel type
Size
FS
Tanker, bulk, cargo
Largest Smallest
1.25 1.75
Container
Largest Smallest
1.5 2.0
General cargo
Where, EA = Abnormal berthing energy to be absorbed by the fender (kNm) FS = Safety factor for abnormal berthings
1.75
RoRo, ferries
≥ 2.0
Tugs, workboats, etc
2.0
Choosing a suitable safety factor (FS) will depend on many factors:
Source: PIANC 2002; Table 4.2.5.
B B B B B B
PIANC recommends that ‘the factor of abnormal impact when derived should be not be less than 1.1 nor more than 2.0 unless exception circumstances prevail’. Source: PIANC 2002; Section 4.2.8.5.
The consequences a fender failure may have on berth operations. How frequently the berth is used. Very low design berthing speeds which might easily be exceeded. Vulnerability to damage of the supporting structure. Range of vessel sizes and types using the berth. Hazardous or valuable cargoes including people.
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SHIP DEFINITIONS Many different definitions are used to describe ship sizes and classes. Some of the more common descriptions are given below. Vessel Type
DWT
10,000–40,000 dwt 130,000–200,000 dwt >200,000 dwt 200,000–300,000 dwt >300,000 dwt
Comments 1st Generation container 8,000 teu All vessel types in Suez Canal All vessel types in St Lawrence Seaway Bulk carrier Bulk carrier Bulk carrier Oil tanker Oil tanker
2. Suez Canal The canal, connecting the Mediterranean and Red Sea, is about 163km long and varies from 80–135m wide. It has no lock chambers but most of the canal has a single traffic lane with passing bays.
3. St Lawrence Seaway The seaway system allows ships to pass from the Atlantic Ocean to the Great Lakes via six short canals totalling 110km, with 19 locks, each 233m long, 24.4m wide and 9.1m deep.
Length × Beam × Draft
Small feeder
200m × 23m × 9m
Feeder
215m × 30m × 10m
Panamax1
290m × 32.3m × 12m
Post-Panamax
305m × >32.3m × 13m
Super post-Panamax (VLCS) Suezmax 2 Seaway-Max3 Handysize Cape Size Very large bulk carrier (VLBC) Very large crude carrier (VLCC) Ultra large crude carrier (ULCC)
500m × 70m × 21.3m 233.5m × 24.0m × 9.1m
1. Panama Canal Lock chambers are 305m long and 33.5m wide. The largest depth of the canal is 12.5–13.7m. The canal is about 86km long and passage takes eight hours.
The ship tables show laden draft (DL) of vessels. The draft of a partly loaded ship (D) can be estimated using the formula below: LWT
MD = LWT + DWT
+
DWT
= MD
D≈
DL × LWT
=
MD
D
DL × (MD – DWT) MD
DL
USING SHIP TABLES 50%
75%
Ship tables originally appeared in PIANC 2002. They are divided into Confidence Limits (CL) which are defined as the proportion of ships of the same DWT with dimensions equal to or less than those in the table. PIANC considers 50% to 75% confidence limits are the most appropriate for design. Please ask Trelleborg Marine Systems for supplementary tables of latest and largest vessel types including Container, RoRo, Cruise and LNG.
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SHIP TABLES smaller
Type
General cargo ship
Bulk carrier
Container ship
Oil tanker
DWT/GRT
Displacement M50
LOA
LBP
B
FL
DL
larger
Wind area Lateral Front Full Load Ballast Full Load Ballast
1000
1580
63
58
10.3
1.6
3.6
227
292
59
88
2000
3040
78
72
12.4
1.9
4.5
348
463
94
134
3000
4460
88
82
13.9
2.1
5.1
447
605
123
172
5000
7210
104
96
16.0
2.3
6.1
612
849
173
236
7000
9900
115
107
17.6
2.5
6.8
754
1060
216
290
10000
13900
128
120
19.5
2.7
7.6
940
1340
274
361
15000
20300
146
136
21.8
3.0
8.7
1210
1760
359
463
20000
26600
159
149
23.6
3.1
9.6
1440
2130
435
552
30000
39000
181
170
26.4
3.5
10.9
1850
2780
569
709
40000
51100
197
186
28.6
3.7
12.0
2210
3370
690
846
5000
6740
106
98
15.0
2.3
6.1
615
850
205
231
7000
9270
116
108
16.6
2.6
6.7
710
1010
232
271
10000
13000
129
120
18.5
2.9
7.5
830
1230
264
320
15000
19100
145
135
21.0
3.3
8.4
980
1520
307
387
20000
25000
157
148
23.0
3.6
9.2
1110
1770
341
443
30000
36700
176
167
26.1
4.1
10.3
1320
2190
397
536
50000
59600
204
194
32.3
4.8
12.0
1640
2870
479
682 798
70000
81900
224
215
32.3
5.3
13.3
1890
3440
542
100000
115000
248
239
37.9
5.9
14.8
2200
4150
619
940
150000
168000
279
270
43.0
6.6
16.7
2610
5140
719
1140
200000
221000
303
294
47.0
7.2
18.2
2950
5990
800
1310
250000
273000
322
314
50.4
7.8
19.4
3240
6740
868
1450
7000
10200
116
108
19.6
2.4
6.9
1320
1360
300
396
10000
14300
134
125
21.6
3.0
7.7
1690
1700
373
477
15000
21100
157
147
24.1
3.9
8.7
2250
2190
478
591
20000
27800
176
165
26.1
4.6
9.5
2750
2620
569
687
25000
34300
192
180
27.7
5.2
10.2
3220
3010
652
770
30000
40800
206
194
29.1
5.8
10.7
3660
3370
729
850
40000
53700
231
218
32.3
6.8
11.7
4480
4040
870
990
50000
66500
252
238
32.3
7.7
12.5
5230
4640
990
1110
60000
79100
271
256
35.2
8.5
13.2
5950
5200
1110
1220
1000
1450
59
54
9.7
0.5
3.8
170
266
78
80
2000
2810
73
68
12.1
0.7
4.7
251
401
108
117
3000
4140
83
77
13.7
1.0
5.3
315
509
131
146
5000
6740
97
91
16.0
1.4
6.1
419
689
167
194
7000
9300
108
102
17.8
1.7
6.7
505
841
196
233
10000
13100
121
114
19.9
2.0
7.5
617
1040
232
284
15000
19200
138
130
22.5
2.6
8.4
770
1320
281
355
20000
25300
151
143
24.6
3.1
9.1
910
1560
322
416
30000
37300
171
163
27.9
3.7
10.3
1140
1990
390
520
50000
60800
201
192
32.3
4.9
11.9
1510
2690
497
689
70000
83900
224
214
36.3
5.7
13.2
1830
3280
583
829
100000
118000
250
240
40.6
6.8
14.6
2230
4050
690
1010
150000
174000
284
273
46.0
8.3
16.4
2800
5150
840
1260
200000
229000
311
300
50.3
9.4
17.9
3290
6110
960
1480
300000
337000
354
342
57.0
11.4
20.1
4120
7770
1160
1850
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12–15 50%
SHIP TABLES smaller
larger
Type
RoRo ship
Passenger (cruise) ship
DWT/GRT
Displacement M50
LOA
LBP
B
FL
DL
1000
1970
66
60
13.2
2.0
3.2
2000
3730
85
78
15.6
2.9
3000
5430
99
90
17.2
3.6
5000
8710
119
109
19.5
Wind area Lateral Front Full Load Ballast Full Load Ballast 700
810
216
217
4.1
970
1110
292
301
4.8
1170
1340
348
364
4.7
5.8
1480
1690
435
464
7000
11900
135
123
21.2
5.5
6.6
1730
1970
503
544
10000
16500
153
141
23.1
6.7
7.5
2040
2320
587
643
15000
24000
178
163
25.6
8.2
8.7
2460
2790
701
779
20000
31300
198
182
27.4
9.5
9.7
2810
3180
794
890
30000
45600
229
211
30.3
11.7
11.3
3400
3820
950
1080
1000
850
60
54
11.4
2.2
1.9
426
452
167
175
2000
1580
76
68
13.6
2.8
2.5
683
717
225
234
3000
2270
87
78
15.1
3.2
3.0
900
940
267
277
5000
3580
104
92
17.1
3.9
3.6
1270
1320
332
344
7000
4830
117
103
18.6
4.5
4.1
1600
1650
383
396
10000
6640
133
116
20.4
5.0
4.8
2040
2090
446
459
15000
9530
153
132
22.5
5.9
5.6
2690
2740
530
545
20000
12300
169
146
24.2
5.2
7.6
3270
3320
599
614
30000
17700
194
166
26.8
7.3
7.6
4310
4350
712
728
50000
27900
231
197
30.5
10.6
7.6
6090
6120
880
900
70000
37600
260
220
33.1
13.1
7.6
7660
7660
1020
1040
1000
810
59
54
12.7
1.9
2.7
387
404
141
145
2000
1600
76
69
15.1
2.5
3.3
617
646
196
203
3000
2390
88
80
16.7
2.8
3.7
811
851
237
247
5000
3940
106
97
19.0
3.3
4.3
1150
1200
302
316
7000
5480
119
110
20.6
3.7
4.8
1440
1510
354
372
10000
7770
135
125
22.6
4.2
5.3
1830
1930
419
442
15000
11600
157
145
25.0
4.7
6.0
2400
2540
508
537
20000
15300
174
162
26.8
5.2
6.5
2920
3090
582
618
30000
22800
201
188
29.7
5.9
7.4
3830
4070
705
752
40000
30300
223
209
31.9
6.5
8.0
4660
4940
810
860
1000
2210
68
63
11.1
1.0
4.3
350
436
121
139
2000
4080
84
78
13.7
1.6
5.2
535
662
177
203
3000
5830
95
89
15.4
2.0
5.8
686
846
222
254
5000
9100
112
104
17.9
2.7
6.7
940
1150
295
335
7000
12300
124
116
19.8
3.2
7.4
1150
1410
355
403
10000
16900
138
130
22.0
3.8
8.2
1430
1750
432
490
15000
24100
157
147
24.8
4.6
9.3
1840
2240
541
612
20000
31100
171
161
27.1
5.4
10.0
2190
2660
634
716
30000
44400
194
183
30.5
6.1
11.7
2810
3400
794
894
50000
69700
227
216
35.5
9.6
11.7
3850
4630
1050
1180
70000
94000
252
240
39.3
12.3
11.7
4730
5670
1270
1420
100000
128000
282
268
43.7
15.6
11.7
5880
7030
1550
1730
Ferry
Gas carrier
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SHIP TABLES smaller
Type
General cargo ship
Bulk carrier
Container ship
Oil tanker
DWT/GRT
Displacement M75
LOA
LBP
B
FL
DL
larger
Wind area Lateral Front Full Load Ballast Full Load Ballast
1000
1690
67
62
10.8
1.9
3.9
278
342
63
93
2000
3250
83
77
13.1
2.3
4.9
426
541
101
142
3000
4750
95
88
14.7
2.5
5.6
547
708
132
182
5000
7690
111
104
16.9
2.8
6.6
750
993
185
249
7000
10600
123
115
18.6
3.0
7.4
922
1240
232
307
10000
14800
137
129
20.5
3.3
8.3
1150
1570
294
382
15000
21600
156
147
23.0
3.6
9.5
1480
2060
385
490
20000
28400
170
161
24.9
3.9
10.4
1760
2490
466
585
30000
41600
193
183
27.8
4.3
11.9
2260
3250
611
750
40000
54500
211
200
30.2
4.6
13.0
2700
3940
740
895
5000
6920
109
101
15.5
2.4
6.2
689
910
221
245
7000
9520
120
111
17.2
2.6
6.9
795
1090
250
287
10000
13300
132
124
19.2
2.9
7.7
930
1320
286
340
15000
19600
149
140
21.8
3.3
8.6
1100
1630
332
411
20000
25700
161
152
23.8
3.6
9.4
1240
1900
369
470
30000
37700
181
172
27.0
4.1
10.6
1480
2360
428
569
50000
61100
209
200
32.3
4.7
12.4
1830
3090
518
723
70000
84000
231
221
32.3
5.2
13.7
2110
3690
586
846
100000
118000
255
246
39.2
5.9
15.2
2460
4460
669
1000
150000
173000
287
278
44.5
6.7
17.1
2920
5520
777
1210
200000
227000
311
303
48.7
7.3
18.6
3300
6430
864
1380
250000
280000
332
324
52.2
7.8
19.9
3630
7240
938
1540
7000
10700
123
115
20.3
2.6
7.2
1460
1590
330
444
10000
15100
141
132
22.4
3.3
8.0
1880
1990
410
535
15000
22200
166
156
25.0
4.3
9.0
2490
2560
524
663
20000
29200
186
175
27.1
5.0
9.9
3050
3070
625
771
25000
36100
203
191
28.8
5.7
10.6
3570
3520
716
870
30000
43000
218
205
30.2
6.4
11.1
4060
3950
800
950
40000
56500
244
231
32.3
7.4
12.2
4970
4730
950
1110
50000
69900
266
252
32.3
8.4
13.0
5810
5430
1090
1250
60000
83200
286
271
36.5
9.2
13.8
6610
6090
1220
1370
1000
1580
61
58
10.2
0.5
4.0
190
280
86
85
2000
3070
76
72
12.6
0.8
4.9
280
422
119
125
3000
4520
87
82
14.3
1.1
5.5
351
536
144
156
5000
7360
102
97
16.8
1.5
6.4
467
726
184
207
7000
10200
114
108
18.6
1.8
7.1
564
885
216
249
10000
14300
127
121
20.8
2.1
7.9
688
1090
255
303
15000
21000
144
138
23.6
2.7
8.9
860
1390
309
378
20000
27700
158
151
25.8
3.2
9.6
1010
1650
355
443
30000
40800
180
173
29.2
3.9
10.9
1270
2090
430
554
50000
66400
211
204
32.3
5.0
12.6
1690
2830
548
734
70000
91600
235
227
38.0
6.0
13.9
2040
3460
642
884
100000
129000
263
254
42.5
7.1
15.4
2490
4270
761
1080
150000
190000
298
290
48.1
8.5
17.4
3120
5430
920
1340
200000
250000
327
318
42.6
9.8
18.9
3670
6430
1060
1570
300000
368000
371
363
59.7
11.9
21.2
4600
8180
1280
1970
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SHIP TABLES smaller
larger
Type
RoRo ship
Passenger (cruise) ship
DWT/GRT
Displacement M75
Wind area Lateral Front Full Load Ballast Full Load Ballast
LOA
LBP
B
FL
DL
73
66
14.0
2.7
3.5
880
970
232
232
1000
2190
2000
4150
94
86
16.6
3.9
4.5
1210
1320
314
323
3000
6030
109
99
18.3
4.7
5.3
1460
1590
374
391
5000
9670
131
120
20.7
6.1
6.4
1850
2010
467
497
7000
13200
148
136
22.5
7.3
7.2
2170
2350
541
583
10000
18300
169
155
24.6
8.8
8.2
2560
2760
632
690
15000
26700
196
180
27.2
10.7
9.6
3090
3320
754
836
20000
34800
218
201
29.1
12.4
10.7
3530
3780
854
960
30000
50600
252
233
32.2
15.2
12.4
4260
4550
1020
1160
1000
1030
64
60
12.1
2.3
2.6
464
486
187
197
2000
1910
81
75
14.4
2.9
3.4
744
770
251
263
3000
2740
93
86
16.0
3.4
4.0
980
1010
298
311
5000
4320
112
102
18.2
4.2
4.8
1390
1420
371
386
7000
5830
125
114
19.8
4.7
5.5
1740
1780
428
444
10000
8010
142
128
21.6
5.3
6.4
2220
2250
498
516
15000
11500
163
146
23.9
6.2
7.5
2930
2950
592
611
20000
14900
180
160
25.7
7.3
8.0
3560
3570
669
690
30000
21300
207
183
28.4
9.8
8.0
4690
4680
795
818
50000
33600
248
217
32.3
13.7
8.0
6640
6580
990
1010
70000
45300
278
243
35.2
16.6
8.0
8350
8230
1140
1170
1000
1230
67
61
14.3
2.1
3.4
411
428
154
158
2000
2430
86
78
17.0
2.6
4.2
656
685
214
221
3000
3620
99
91
18.8
2.9
4.8
862
903
259
269
5000
5970
119
110
21.4
3.5
5.5
1220
1280
330
344
7000
8310
134
124
23.2
3.9
6.1
1530
1600
387
405
10000
11800
153
142
25.4
4.3
6.8
1940
2040
458
482
15000
17500
177
164
28.1
5.0
7.6
2550
2690
555
586
20000
23300
196
183
30.2
5.5
8.3
3100
3270
636
673
30000
34600
227
212
33.4
6.2
9.4
4070
4310
771
819
40000
45900
252
236
35.9
6.9
10.2
4950
5240
880
940
1000
2480
71
66
11.7
1.1
4.6
390
465
133
150
2000
4560
88
82
14.3
1.5
5.7
597
707
195
219
3000
6530
100
93
16.1
2.0
6.4
765
903
244
273
5000
10200
117
109
18.8
2.6
7.4
1050
1230
323
361
7000
13800
129
121
20.8
3.2
8.1
1290
1510
389
434
10000
18900
144
136
23.1
3.9
9.0
1600
1870
474
527
15000
27000
164
154
26.0
4.8
10.1
2050
2390
593
658
20000
34800
179
169
28.4
5.5
11.0
2450
2840
696
770
30000
49700
203
192
32.0
6.7
12.3
3140
3630
870
961
50000
78000
237
226
37.2
10.5
12.3
4290
4940
1150
1270
70000
105000
263
251
41.2
13.4
12.3
5270
6050
1390
1530
100000
144000
294
281
45.8
16.9
12.3
6560
7510
1690
1860
Ferry
Gas carrier
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APPROACH VELOCITY (VB) Berthing speeds depend on the ease or difficulty of the approach, the exposure of the berth and the vessel’s size. Conditions are normally divided into five categories as shown in the chart’s key table. The most widely used guide to approach speeds is the Brolsma table, adopted by BS1, PIANC2 and other standards. For ease of use, speeds for the main vessel sizes are shown at the bottom of this page.
0.8 a b c d e
0.7
VB
Approach velocity, VB (m/s)
e 0.6
Berthing condition Easy berthing, sheltered Difficult berthing, sheltered Easy berthing, exposed Good berthing, exposed Difficult berthing, exposed
d 0.5 c
0.4
most commonly used conditions
0.3 b 0.2 a 0.1 USE WITH CAUTION 0 1,000
10,000
100,000
500,000
Deadweight (DWT)* * PIANC suggests using DWT from 50% or 75% confidence limit ship tables.
Velocity, VB (m/s) DWT
a
b
c
d
e
1,000
0.179
0.343
0.517
0.669
0.865
2,000
0.151
0.296
0.445
0.577
0.726
3,000
0.136
0.269
0.404
0.524
0.649
4,000
0.125
0.250
0.374
0.487
0.597
5,000
0.117
0.236
0.352
0.459
0.558
10,000
0.094
0.192
0.287
0.377
0.448
20,000
0.074
0.153
0.228
0.303
0.355
30,000
0.064
0.133
0.198
0.264
0.308
40,000
0.057
0.119
0.178
0.239
0.279 0.258
50,000
0.052
0.110
0.164
0.221
100,000
0.039
0.083
0.126
0.171
0.201
200,000
0.028
0.062
0.095
0.131
0.158
300,000
0.022
0.052
0.080
0.111
0.137
400,000
0.019
0.045
0.071
0.099
0.124
500,000
0.017
0.041
0.064
0.090
0.115
B Approach velocities less than 0.1m/s should be used with caution. B Values are for tug-assisted berthing. B Spreadsheets for calculating the approach velocity and berthing energy are available at www.trelleborg.com/marine . B Actual berthing velocities can be measured, displayed and recorded using a SmartDock Docking Aid System (DAS) by Harbour Marine.† †
Harbour Marine is part of Trelleborg Marine Systems.
Caution: low berthing speeds are easily exceeded.
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BLOCK COEFFICIENT (CB) The block coefficient (CB) is a function of the hull shape and is expressed as follows:
CB =
Typical block coefficients (CB)
MD LBP × B × D × ρSW
Container vessels General cargo and bulk carriers Tankers Ferries RoRo vessels
where, MD = displacement of vessel (t) LBP = length between perpendiculars (m) B = beam (m) D = draft (m) ρSW = seawater density ≈ 1.025t/m3
0.6–0.8 0.72–0.85 0.85 0.55–0.65 0.7–0.8
Source: PIANC 2002; Table 4.2.2
Given ship dimensions and using typical block coefficients, the displacement can be estimated:
LBP
D
MD ≈ CB × LBP × B × D × ρSW
B
ADDED MASS COEFFICIENT (CM) B The added mass coefficient allows for the body of water carried along with the ship as it moves sideways through the water. As the ship is stopped by the fender, the entrained water continues to push against the ship, effectively increasing its overall mass. The Vasco Costa method is adopted by most design codes for ship-to-shore berthing where water depths are not substantially greater than vessel drafts. Shigera Ueda (1981)
PIANC (2002)
for
KC
≤ 0.1
for
KC D
KC D
≥ 0.5
VB
D KC
Vasco Costa* (1964)
CM = 1.8
D
for 0.1 ≤
Quay
≤ 0.5
KC D
CM = 1.875 – 0.75
CM = 1.5
CM =
π×D 2 × CB × B
2D CM = 1 +
B
where, D = draft of vessel (m) B = beam of vessel (m) LBP = length between perpendiculars (m) KC = under keel clearance (m)
* valid where VB ≥ 0.08m/s, KC ≥ 0.1D
Special case – longitudinal approach
V
CM = 1.1 Recommended by PIANC.
12–19
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ECCENTRICITY COEFFICIENT (CE) The Eccentricity Coefficient allows for the energy dissipated by rotation of the ship about its point of impact with the fenders. The correct point of impact, berthing angle and velocity vector angle are all important for accurate calculation of the eccentricity coefficient. In practice, CE often varies between 0.3 and 1.0 for different berthing cases. Velocity (V) is not always perpendicular to the berthing line.
LBP y x B 2
ϕ
R
α berthing line VB
V VL VL = longitudinal velocity component (forward or astern)
x+y=
R=
LBP 2
y2 +
(assuming the centre of mass is at mid-length of the ship)
B 2
Common berthing cases
2
Quarter-point berthing K = (0.19 × CB + 0.11) × LBP x=
K + R cos ϕ 2
CE =
2
LBP 4
CE ≈ 0.4–0.6
2
Third-point berthing
K2 + R2
x= where, B = beam (m) CB = block coefficient LBP = length between perpendiculars (m) R = centre of mass to point of impact (m) K = radius of gyration (m)
LBP 3
CE ≈ 0.6–0.8
Midships berthing x=
LBP 2
CE ≈ 1.0
Caution: for ϕ < 10º, CE J 1.0 Lock entrances and guiding fenders
Tug
ϕ V R
Dolphin berths ϕ
α R
α V a
Where the ship has a significant forward motion, PIANC suggests that the ship’s speed parallel to the berthing face (Vcosα) is not decreased by berthing impacts, and it is the transverse velocity component (Vsinα) which much be resisted by the fenders. When calculating the eccentricity coefficient, the velocity vector angle (ϕ) is taken between V and R.
Ships rarely berth exactly midway between dolphins. ROM 0.2-90 suggests a=0.1L, with a minimum of 10m and maximum of 15m between the midpoint and the vessel’s centre of mass. This offset reduces the vector angle (ϕ) and increases the eccentricity coefficient.
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ECCENTRICITY COEFFICIENT (CE) Special cases for RoRo Terminals Modern RoRo terminals commonly use two different approach modes during berthing. PIANC defines these as mode b) and mode c). It is important to decide whether one or both approach modes will be used, as the berthing energies which must be absorbed by the fenders can differ considerably.
Mode b)
Mode c)
α ≤ 15º
Breasting dolphins
Outer end
A A
R
V1
Breasting dolphins
≤0.25LS
R
ϕ
Approach
ϕ
V1
≥ 1.05LL
≤0.25LS
α ≤ 15º
V2
≤0.25LS
V2
B
B
≤0.25LS Inner end
V3
V3
≤0.25LS
≤0.25LS
End fender and shore based ramp
A
Fender Side
B C
Side End
C
Typical values 100mm/s ≤ V1 ≤ 300mm/s 60° ≤ ϕ ≤ 90° N/A 300mm/s ≤ V2 ≤ 500mm/s 200mm/s ≤ V3 ≤ 500mm/s 0° ≤ ϕ ≤ 10°
RoRo vessels with bow and/or stern ramps make a transverse approach to the berth. The ships then move along the quay or dolphins using the side fenders for guidance until they are the required distance from the shore ramp structure. B Lower berthing energy B Reduced speeds may affect ship manoeuvrability B Increased turn-around time B CE is smaller (typically 0.4–0.7)
α
End fender and shore based ramp
C
A
Fender Side
Typical values 1000mm/s ≤ V1 ≤ 3000mm/s
0° ≤ ϕ ≤ 50°
B C
Side End
500mm/s ≤ V2 ≤ 1000mm/s 200mm/s ≤ V3 ≤ 500mm/s
0° ≤ ϕ ≤ 50° 0° ≤ ϕ ≤ 10°
RoRo vessels approach either head-on or stern-on with a large longitudinal velocity. Side fenders guide the vessel but ships berth directly against the shore ramp structure or dedicated end fenders. B Quicker berthing and more controllable in strong winds B High berthing energies B Risk of vessel hitting inside of fenders or even the dolphins B CE can be large (typically 0.6–0.9)
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BERTH CONFIGURATION COEFFICIENT (CC) When ships berth at small angles against solid structures, the water between hull and quay acts as a cushion and dissipates a small part of the berthing energy. The extent to which this factor contributes will depend upon several factors: B B B B B
Closed structure
Quay structure design Underkeel clearance Velocity and angle of approach Projection of fender Vessel hull shape
Semi-closed structure PIANC recommends the following values:
CC = 1.0
B B B B
CC = 0.9
B Solid quay structures B Berthing angles > 5º
Open structures including berth corners Berthing angles > 5º Very low berthing velocities Large underkeel clearance
Note: where the under keel clearance has already been considered for added mass (CM), the berth configuration coefficient CC =1 is usually assumed.
SOFTNESS COEFFICIENT (CS) Where fenders are hard relative to the flexibility of the ship hull, some of the berthing energy is absorbed by elastic deformation of the hull. In most cases this contribution is limited and ignored (CS =1). PIANC recommends the following values: CS = 1.0
Soft fenders (δf > 150mm)
CS = 0.9
Hard fenders (δf ≤ 150mm)
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Every type and size of fender has different performance characteristics. Whatever type of fenders are used, they must have sufficient capacity to absorb the normal and abnormal energies of berthing ships. When selecting fenders the designer must consider many factors including: B B B B B B
Single or multiple fender contacts The effects of angular compressions Approach speeds Extremes of temperature Berthing frequency Fender efficiency
Reaction
FENDER SELECTION
ENERGY = area under curve
Deflection
Comparing efficiency Fender efficiency is defined as the ratio of the energy absorbed to the reaction force generated. This method allows fenders of many sizes and types to be compared as the example shows. Comparisons should also be made at other compression angles, speeds and temperatures when applicable.
R
R
E
E
D
This comparison shows Super Cone and SeaGuard fenders with similar energy, reaction and hull pressure, but different height, deflection and initial stiffness (curve gradient).
D
Super Cone SCN 1050 (E2)
SeaGuard SG 2000 × 3500 (STD)
E = 458kNm R = 843kN D = 768mm P = 187kN/m2 *
E = 454kNm R = 845kN D = 1200mm P = 172kN/m2
E = 0.543 kNm/kN R
E = 0.537 kNm/kN R
* for a 4.5m2 panel
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FENDER PITCH
B Smaller ships have smaller bow radius but usually cause smaller fender deflection. B Clearance distances should take account of bow flare angles. B Bow flares are greater near to the bow and stern. B Where ship drawings are available, these should be used to estimate bow radius.
Bow radiu
s, RB
Fenders spaced too far apart may allow ships to hit the structure. A positive clearance (C) should always be maintained, usually between 5–15% of the uncompressed fender height (H). A minimum clearance of 300mm inclusive of bow flare is commonly specified.
α
θ
δF
H
θ
P/ 2
Fender pitch
1
B
2
2
+
LOA2 8B
where, RB = bow radius (m) B = beam of vessel (m) LOA = vessel length overall (m) The bow radius formula is approximate and should be checked against actual ship dimensions where possible.
Caution Large fender spacings may work in theory but in practice a maximum spacing of 12–15m is more realistic.
As a guide to suitable distance between fenders on a continuous wharf, the formula below indicates the maximum fender pitch. Small, intermediate and large vessels should be checked.
P ≤ 2 RB2 – (RB – h + C)2 where, P = pitch of fender RB = bow radius (m) h = fender projection when compressed, measured at centreline of fender a = berthing angle C = clearance between vessel and dock (C should be 5–15% of the undeflected fender projection, including panel) θ = hull contact angle with fender According to BS 6349: Part 4: 1994, it is also recommended that the fender spacing does not exceed 0.15 × L S, where L S is the length of the smallest ship. Bow radius (metres)
RB ≈
P/ 2
h = H – δF
h
C
P
Bow radius
θ
Cruise liner
Container ship
200
Bulk carrier/ general cargo
150 100 50 0 0
65 Displacement (1000 t)
0
140 0 425 Displacement (1000 t) Displacement (1000 t)
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MULTIPLE CONTACT CASES 3-fender contact
RB
δF2
RB
RB
δF1
P
B B B B
2-fender contact
δF2
P
RB
δF
Berthing H line
P
P
B B B B
Energy absorbed by three (or more) fenders Larger fender deflection likely Bow flare is important 1-fender contact also possible for ships with small bow radius
P/ 2
P/ 2
Berthing line
P
Energy divided over 2 (or more) fenders Smaller fender deflections Greater total reaction into structure Clearance depends on bow radius and bow flare
ANGULAR BERTHING The berthing angle between the fender and the ship’s hull may result in some loss of energy absorption. Angular berthing means the horizontal and/or vertical angle between the ship’s hull and the berthing structure at the point of contact. There are three possible conditions for the effects of angular berthing: flare, bow radius and dolphin.
Flare
Bow radius
Dolphin
Bow
α us,
radi RB
θ
α
β P sin θ =
P 2RB
where RB = bow radius
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FENDER PANEL DESIGN 3 design cases
Fender panels are used to distribute reaction forces into the hulls of berthing vessels. The panel design should consider many factors including: B B B B B B B B B B B B B B B B B
Full-face contact
Hull pressures and tidal range Lead-in bevels and chamfers Bending moment and shear Local buckling Limit state load factors Steel grade Permissible stresses Weld sizes and types Effects of fatigue and cyclic loads Pressure test method Rubber fender connections UHMW-PE attachment Chain connections Lifting points Paint systems Corrosion allowance Maintenance and service life
Low-level impact
Double contact
n×T F
F1
R
R
R1
F
R2
F2
Steel Properties PIANC steel thicknesses Standard
EN 10025
JIS G-3101
Grade
Yield Strength (min)
Tensile Strength (min)
Temperature
N/mm²
psi
N/mm²
psi
°C
°F
S235JR (1.0038)
235
34 000
360
52 000
–
–
S275JR (1.0044)
275
40 000
420
61 000
–
–
S355J2 (1.0570)
355
51 000
510
74 000
-20
-4
S355J0 (1.0553)
355
51 000
510
74 000
0
32
SS41
235
34 000
402
58 000
0
32
SS50
275
40 000
402
58 000
0
32
SM50
314
46 000
490
71 000
0
32
A-36
250
36 000
400
58 000
0
32
A-572
345
50 000
450
65 000
0
32
PIANC recommends the following minimum steel thicknesses for fender panel construction: Exposed both faces Exposed one face Internal (not exposed)
≥ 12mm ≥ 9mm ≥ 8mm
Source: PIANC 2002; Section 4.1.6. Corresponding minimum panel thickness will be 140–160mm (excluding UHMW-PE face pads) and often much greater.
Typical panel weights ASTM
The national standards of France and Germany have been replaced by EN 10025. In the UK, BS4360 has been replaced by BS EN 10025. The table above is for guidance only and is not comprehensive. Actual specifications should be consulted in all cases for the full specifications of steel grades listed and other similar grades.
The table can be used as a guide to minimum average panel weight (excluding UHMW-PE face pads) for different service conditions: Light duty Medium duty Heavy duty Extreme duty
200–250kg/m2 250–300kg/m2 300–400kg/m2 ≥400kg/m2
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HULL PRESSURES W
Allowable hull pressures depend on hull plate thickness and frame spacing. These vary according to the type of ship. PIANC gives the following advice on hull pressures: Size/class
Hull pressure (kN/m2)
< 1 000 teu (1st/2nd generation) < 3 000 teu (3rd generation) < 8 000 teu (4th generation) > 8 000 teu (5th/6th generation)
< 400 < 300 < 250 < 200
General cargo
≤ 20 000 DWT > 20 000 DWT
400–700 < 400
Oil tankers
≤ 20 000 DWT ≤ 60 000 DWT > 60 000 DWT
< 250 < 300 150–200
Gas carriers
LNG/LPG
< 200
Vessel type
R P=
H
Container ships
W×H
P = average hull pressure (kN/m2) R = total fender reaction (kN) W = panel width, excluding bevels (m) H = panel height, excluding bevels (m)
Bulk carriers
< 200
RoRo Passenger/cruise SWATH
Usually fitted with beltings (strakes)
Source: PIANC 2002; Table 4.4.1
BELTINGS
Belting types
Most ships have beltings (sometimes called belts or strakes). These come in many shapes and sizes – some are well-designed, others can be poorly maintained or modified. Care is needed when designing fender panels to cope with beltings and prevent snagging or catching which may damage the system. Belting line loads exert crushing forces on the fender panel which must be considered in the structural design. Application Light duty Medium duty Heavy duty
Vessels
Belting Load (kN/m)
Aluminium hulls
150–300
Container RoRo/Cruise
Belting range
1
2
h 3
500–1 000 1 000–1 500
Belting range is often greater than tidal range due to ship design, heave, roll, and changes in draft.
≥h
1
2
Common on RoRo/Cruise ships. Projection 200–400mm (typical).
3
Common on LNG/Oil tankers, barges, offshore supply vessels and some container ships. Projection 100–250mm (typical).
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FRICTION Typical friction design values
Friction has a large influence on the fender design, particularly for restraint chains. Low friction facing materials (UHMW-PE) are often used to reduce friction. Other materials, like polyurethanes (PU) used for the skin of foam fenders, have lower friction coefficients than rubber against steel or concrete. The table can be used as a guide to typical design values. Friction coefficients may vary due to wet or dry conditions, local temperatures, static and dynamic load cases, as well as surface roughness.
Materials UHMW-PE HD-PE Polyurethane Rubber Timber Steel
Steel Steel Steel Steel Steel Steel
Friction Coefficient (μ) 0.2 0.3 0.4 0.7 0.4 0.5
CHAIN DESIGN Chains can be used to restrain the movements of fenders during compression or to support static loads. Chains may serve four main functions: B Weight chains support the steel panel and prevent excessive drooping of the system. They may also resist vertical shear forces caused by ship movements or changing draft. B Shear chains resist horizontal forces caused during longitudinal approaches or warping operations. B Tension chains restrict tension on the fender rubber. Correct location can optimise the deflection geometry. B Keep chains are used to moor floating fenders or to prevent loss of fixed fenders in the event of accidents.
1 3
Factors to be considered when designing fender chains: B Corrosion reduces link diameter and weakens the chain. B Corrosion allowances and periodic replacement should be allowed for. B A ‘weak link’ in the chain system is desirable to prevent damage to more costly components in an accident.
SWL =
2
μR + W n cosθ
MBL ≥ FC × SWL θ
where, SWL = safe working load (kN) FC = safety factor μ = coefficient of friction R = fender reaction (kN) W = gross panel weight (kg) (for shear chains, W = 0) n = number of chains θ = effective chain angle (degrees)
μR
1
Tension chains
2
Weight chains
3
Shear chains
W
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UHMW-PE FACING The contact face of a fender panel helps to determine the lifetime maintenance costs of a fender installation. UHMW-PE (FQ1000) is the best material available for such applications. It uniquely combines low friction, impact strength, non-marking characteristics and resistance to wear, temperature extremes, seawater and marine borers. Sinter moulded into plates at extremely high pressure, UHMW-PE is a totally homogeneous material which is available in many sizes and thicknesses. These plates can be cut, machined and drilled to suit any type of panel or shield.
Fastening example
W t
Always use oversize washers to spread the load.
Application Light duty Medium duty
Heavy duty
Extreme duty
t (mm)
W* (mm)
Bolt
30
3–5
M16
40
7–10
50
10–15
60
15–19
70
18–25
80
22–32
90
25–36
100
28–40
M16–M20
M24–M30
M30–M36
* Where allowances are typical values, actual wear allowance may vary due fixing detail.
The standard colour is black, but UHMW-PE is available in many other colours if required.
Large pads vs small pads Larger pads are usually more robust but smaller pads are easier and cheaper to replace.
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CORROSION PREVENTION Fenders are usually installed in corrosive environments, sometimes made worse by high temperature and humidity. Corrosion of fender accessories can be reduced with specialist paint coatings, by galvanising or with selective use of stainless steels. Paint coatings and galvanising have a finite life. Coating must be reapplied at intervals during the life of the fender. Galvanised components like chains or bolts may need periodic re-galvanising or replacement. Stainless steels should be carefully selected for their performance in seawater.
Paint coatings ISO EN 12944 is a widely used international standard defining the durability of corrosion protection systems in various environments. The C5-M class applies to marine coastal, offshore and high salinity locations and is considered to be the most applicable to fenders. The life expectancy or ‘durability’ of coatings is divided into three categories which estimate the time to first major maintenance: Low Medium High
2–5 years 5–15 years >15 years
Durability range is not a guarantee. It is to help operators estimate sensible maintenance times.
The table gives some typical C5-M class paint systems which provide high durability in marine environments. Note that coal tar epoxy paints are not available in some countries. Priming Coat(s)
Top Coats
Paint System
Paint Surface System Preparation
Binder
Primer
No. coats
NDFT
Binder
No. coats
NDFT
No. coats
NDFT
Expected durability (C5-M corrosivity)
S7.09
Sa 2.5
EP, PUR
Zn (R)
1
40
EP, PUR
3-4
280
4-5
320
High (>15y)
S7.11
Sa 2.5
EP, PUR
Zn (R)
1
40
CTE
3
360
4
400
High (>15y)
S7.16
Sa 2.5
CTE
Misc
1
100
CTE
2
200
3
300
Medium (5-15y)
Sa 2.5 is defined in ISO 8501-1 NDFT = Nominal dry film thickness Zn (R) = Zinc rich primer
Misc = miscellaneous types of anticorrosive pigments EP = 2-pack epoxy
PUR = 1-pack or 2-pack polyurethane CTE = 2-pack coal tar epoxy
Design considerations Other paint systems may also satisfy the C5-M requirements but in choosing any coating the designer should carefully consider the following: B B B B B B B
Corrosion protection systems are not a substitute for poor design details such as re-entrant shapes and corrosion traps. Minimum dry film thickness >80% of NDFT (typical) Maximum film thickness
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