Section
8 Anchor windlass design and testing
8.1 General
8.1.1 A windlass used for handling anchors, suitable for the size of chain
cable required by Pt 3, Ch 13, 7 Equipment and complying with the following criteria is to
be fitted. Where Owners require equipment significantly in excess of Rule
requirements, it is their responsibility to specify increased windlass power.
8.1.2 The design, construction and testing of windlasses are to conform with a relevant
National or International Standard or code of practice acceptable to LR. To be
considered acceptable, the standard, or code of practice, is to specify criteria for
evaluation of stresses, performance and testing.
8.1.3 Operation and maintenance procedures for the anchor windlass are to be incorporated
in the vessel operations manual.
8.2 Plans and particulars to be submitted
8.2.1 The following plans showing the design specifications, the standard of compliance,
engineering analyses and details of construction, as applicable, are to be submitted
for evaluation:
- Windlass design specifications, anchor and chain cable
particulars, performance criteria, and standard of compliance.
- Windlass foundation drawings including the supporting
structure below deck. The details shall include bolts, chocks, shear
stoppers etc., along with the foot print loads for the specified windlass
ratings.
- Chain stopper foundation drawings including the
supporting structure below deck. The details shall include bolts, chocks,
shear stoppers etc., along with the foot print loads for the specified
rating.
- Windlass arrangement plans showing all the components of
the anchoring/mooring system such as the prime mover, shafting, cable
lifter, anchors and chain cables; mooring winches, wires and fairleads, if
they form part of the windlass machinery, brakes, controls, etc.
- Dimensions, materials, welding details, as applicable,
of all torque-transmitting components (shafts, gears, clutches, couplings,
coupling bolts, etc.) and all load-bearing components (shaft bearings, cable
lifter, sheaves, drums, bed-frames, etc.) of the windlass and of the winch,
where applicable, including brakes, chain stopper (if fitted), and
foundation.
- Hydraulic system, to include:
- piping diagram along with system design
pressure;
- safety valves arrangement and settings;
- material specifications for pipes and
equipment;
- typical pipe joints, as applicable;
- technical data and details for hydraulic
motors;
- cooling systems arrangements for hydraulic
system oil.
- Electrical one-line diagram along with cable
specification and size, motor controller, protective device rating or
setting, as applicable.
- Control, monitoring and instrumentation
arrangements.
- Engineering analyses for torque-transmitting and
load-bearing components demonstrating their compliance with recognised
standards or codes of practice. Analyses for gears are to be in accordance
with a recognised standard.
- Calculations proving satisfactory inertia loads for the
intended windlass, see
Pt 3, Ch 13, 8.4 Windlass design 8.4.1.(b).
- Plans and data for windlass electric motors including
associated gears rated 100 kW and over.
- Calculations demonstrating that the windlass prime mover
is capable of attaining the hoisting speed, the required continuous duty
pull, and the overload capacity are to be submitted if the ‘load testing’
including ‘overload’ capacity of the entire windlass unit is not carried out
at the shop (see
Pt 3, Ch 13, 8.9 Shop inspection and testing 8.9.1.(b)).
8.3 Materials and fabrication
8.3.1 Materials used in the construction of torque-transmitting and
load-bearing parts of windlasses are to comply with LR's Rules for the Manufacture, Testing and Certification of Materials, July 2022 or an
appropriate National or International Standard acceptable to LR, provided that the
Standard gives reasonable equivalence to the requirements of LR. The proposed
materials are to be indicated in the construction plans and are to be approved in
connection with the design. All such materials are to be certified by the material
manufacturers and are to be traceable to the manufacturers’ certificates.
8.3.2 Weld joint designs are to be shown in the submitted construction plans and are to be
appraised in association with the approval of the windlass design in accordance with
an appropriate National or International Standard acceptable to LR. .
8.3.4 The degree of non-destructive examination of welds and post-weld heat treatment, if
any, are to be specified and submitted for consideration.
8.4 Windlass design
8.4.1 In addition to the requirements of the National or International Standard
or code of practice acceptable to LR (see
Pt 3, Ch 13, 8.1 General 8.1.2) the following performance
requirements are to be complied with:
- Holding Loads: Calculations are to be made to show that, in the
holding condition (single anchor, brake fully applied and chain cable lifter
declutched) and under a load equal to 80 per cent of the specified minimum breaking
strength of the chain cable, the maximum stress in each load bearing component will
not exceed the maximum permissible yield. For installations fitted with a chain cable
stopper, 45 per cent of the specified minimum breaking strength of the chain cable
may instead be used for the calculation.
- Inertia Loads: The design of the drive train, including prime
mover, reduction gears, bearings, clutches, shafts, cable lifter and bolting is to
consider the dynamic effects of sudden stopping and starting of the prime mover or
chain cable, so as to limit inertial load.
- Continuous Duty Pull: The windlass is to
have sufficient power to exert a continuous duty pull , Zcont1,
over a period of 30 minutes corresponding to the grade and diameter,
dc, of the chain cables as follows:
- for specified design anchorage depths up to 82,5 m when using
ordinary stockless anchors: :
Chain cable
grade
|
Zcont1 (N)
|
U1
|
37,5d
c
2
|
U2
|
42,5d
c
2
|
U3
|
47,5d
c
2
|
- for specified design anchorage depths greater
than 82,5 m a continuous duty pull Zcont2 is:
- where
dc |
= |
is the chain diameter, in mm |
Da |
= |
is the specified design anchorage depth, in metres |
The anchor masses are assumed to be the masses as given in Table 13.7.2 Equipment - Bower anchors and
chain cables. The value of Zcont is based on the
hoisting of one anchor at a time, and assumes that the effects of buoyancy and
hawse pipe efficiency (assumed to be 70 per cent) have been accounted for. In
general, stresses in each torque-transmitting component are not to exceed 40 per
cent of yield strength (or 0,2 per cent proof stress) of the material under these
loading conditions.
-
Overload Capability: The windlass prime mover is to be able to
provide, for a period of at least two minutes, the necessary temporary overload
capacity for breaking out the anchor. This temporary overload capacity is to be a
pull equal to the greater of:
-
short term pull:
1,5 times the continuous duty pull as defined in
Pt 3, Ch 13, 8.4 Windlass design 8.4.1.(c), or
-
anchor breakout pull:
Note The speed in this period may be lower than normal.
- Hoisting Speed: The mean speed of the chain cable
during hoisting of the anchor and cable is to be 0,15 m/s.
- Brake Capacity: The capacity of the windlass brake is
to be sufficient to stop the anchor and chain cable when paying out the chain cable
in a controlled manner. Where a chain cable stopper is not fitted, the brake is to
produce a torque capable of withstanding a pull equal to 80 per cent of the specified
minimum breaking strength of the chain cable without any permanent deformation of
strength members and without brake slip. Where a chain cable stopper is fitted, 45
per cent of the breaking strength may instead be applied. The following simplified
formula is to be used to calculate the required brake capacity:
K
b
d
c
2 (44 − 0,08d
c) N
where K
b is given in Table 13.8.1 Values of Kb
.
Table 13.8.1 Values of Kb
|
K
b
|
Cable grade
|
Windlass used in conjunction with chain
stopper
|
Chain stopper not fitted
|
U1
|
4,41
|
7,85
|
|
U2
|
6,18
|
11,0
|
|
U3
|
8,83
|
15,7
|
|
8.4.2 As an alternative to conducting the engineering analyses required by Pt 3, Ch 13, 8.4 Windlass design 8.4.1, approval of the windlass
mechanical design can be based on a type test, in which case the testing procedure is to
be submitted for consideration.
8.4.3 Calculations for torque transmitting components are to be based on 1500
hours of operation with a nominal load spectrum factor of Km = 1,0.
Alternatively unlimited hours with Km = 0,8 can be applied.
8.4.4 The following criteria are to be used for gearing design:
-
Torque is to be based on the performance criteria specified in Pt 3, Ch 13, 8.4 Windlass design 8.4.1.
-
The use of an equivalent torque, T
eq, for dynamic strength calculations is acceptable but the derivation
is to be submitted to LR for consideration.
-
The application factor for dynamic strength calculation, K
A, is to be 1,15.
-
Calculations are to be based on 1500 hours of operation.
-
The static torque is to be 1,5 x T
n where T
n is the nominal torque.
-
The minimum factors of safety for load capacity of spur and helical
gears, as derived using ISO 6336 or a relevant National or International standard
acceptable to LR, are to be 1,5 for bending stress and 0,6 for contact stress.
Gears intended to transmit power greater than 100 kW are to be certified by
LR, and the gears are to meet the requirements of Pt 5, Ch 5 Gearing.
8.5 Hydraulic systems
8.6 Electrical systems
8.7 Control arrangements
8.7.1 All
control devices are to be capable of being controlled from readily
accessible positions and protected against unintentional operation.
8.7.2 The
maximum travel of the levers is not to exceed 600 mm if movable in
one direction only, or 300 mm to either side from a central position
if movable in both directions. They are to move toward the right when
hauling and toward the left when paying out. Alternatively, they are
to move backward when hauling and forward when paying out.
8.7.3 Wherever
practical, the lever is to move in the direction of the intended movement.
8.7.4 For
lever-operated brakes, the brake is to engage when the lever is pulled
and disengage when the lever is pushed. The physical effort on the
brake for the operator is not to exceed 160 N.
8.7.5 For
pedal-operated brakes the maximum travel is not to exceed 250 mm and
the physical effort for the operator is not to exceed 320 N.
8.7.6 The
handwheel or crankhandle is to actuate the brake when turned clockwise
and release it when turned counterclockwise. The physical effort for
the operator is not to exceed 250 N for speed regulation and 500 N
at any moment.
8.7.7 When
not provided with automatic sequential control, separate push-buttons
are to be provided for each direction of operation.
8.7.8 The
push-buttons are to actuate the machinery when depressed and stop
and effectively brake the machinery when released.
8.7.9 The
above mentioned individual push-buttons may be replaced by two ‘start’
and ‘stop’ push-buttons.
8.8 Protection arrangements
8.8.1 Where applicable, moving parts of windlass machinery are to be provided with
suitable railings and/or guards to prevent injury to personnel.
8.8.2 Protection is to be provided for preventing persons from coming into contact
with surfaces having temperatures over 50°C.
8.8.3 Steel surfaces not protected by lubricant are to be protected by a coating
in accordance with the requirements of a relevant National or International Standard
acceptable to LR.
8.8.5 Electrical cables installed in exposed locations on open deck are to be provided with
effective mechanical protection.
8.8.6 Means are to be provided to contain potential debris resulting from severe damage of the
prime mover due to over-speed in the event of uncontrolled rendering of the cable,
particularly when an axial piston type hydraulic motor forms the prime mover.
8.8.7 An arrangement to release the anchor and chain in the event of windlass
power failure is to be provided. Windlasses are to be fitted with couplings which are
capable of disengaging between the cable lifter and the drive shaft. Hydraulically or
electrically operated couplings are to be capable of being disengaged manually.
8.8.8 The design of the windlass is to be such that the following requirements or
equivalent arrangements will minimise the probability of the chain locker or forecastle
being flooded in bad weather:
-
a weathertight connection can be made between the windlass bedplate,
or its equivalent, and the upper end of the chain pipe by means of a cover or
seal, and
-
access to the chain pipe is adequate to permit the fitting of a cover
or seal, of sufficient strength and proper design, over the chain pipe while the
ship is at sea.
8.9 Shop inspection and testing
8.9.1 Windlasses are to be inspected during fabrication at the manufacturers’ facilities by
a Surveyor for conformance with the approved plans. Acceptance tests, as specified
in the specified Standard (see
Pt 3, Ch 13, 8.1 General 8.1.2), are to be witnessed by the
Surveyor and include the following tests, as a minimum:
- No-load test. The windlass is to be run without load at
nominal speed in each direction for a total of 30 minutes. If the windlass is
provided with a gear change, an additional run in each direction for 5 minutes
at each gear change is required.
- Load test. The windlass is to be tested to verify that the
continuous duty pull, overload capacity and hoisting speed as specified in Pt 3, Ch 13, 8.4 Windlass design 8.4.1 can
be achieved.
Where the manufacturer’s works does not have adequate
facilities, these tests, including the adjustment of the overload
protection, can be carried out on board ship. In these cases, functional
testing in the manufacturer’s works is to be performed under no-load
conditions.
- Brake capacity test. The holding power of the brake is to be
verified through testing if not verified by calculation.
8.9.2 Windlass performance characteristics specified in Pt 3, Ch 13, 8.9 Shop inspection and testing 8.9.1
are based on the following assumptions:
-
one cable lifter only is connected to the drive shaft;
-
continuous duty and short term pulls are measured at the cable
lifter;
-
hawse pipe efficiency assumed to be 70 per cent.
8.10 On-board testing
8.10.1 Each windlass is to be tested under working conditions after installation
on board to demonstrate satisfactory operation. Each unit is to be independently tested
for braking, clutch functioning, lowering and hoisting of the chain cable and anchor,
proper riding of the chain over the cable lifter, proper transit of the chain through
the hawse pipe and the chain pipe, and effecting proper stowage of the chain and the
anchor. It is to be confirmed that anchors properly seat in the stored position and that
chain stoppers function as designed, if fitted. The braking capacity is to be tested by
intermittently paying out and holding the chain cable by means of the application of the
brake.
8.10.2 During trials on board ship, the windlass is to be shown to be capable of:
- For all specified design anchorage depths, the mean hoisting
speed, as specified in Pt 3, Ch 13, 8.4 Windlass design 8.4.1.(e) is to be measured
and verified. For testing purposes, the speed is to be measured over two shots of
chain cable and initially with at least three shots of chain (82,5 m or 45 fathoms in
length) and the anchor submerged and hanging free.
- For specified design anchorage depths greater than 82,5 m: in
addition to Pt 3, Ch 13, 8.10 On-board testing 8.10.2.(a), raising
the anchor from the specified design anchorage depth to a depth of 82,5 m at a mean
speed of 3 m/min.
Following trials, the ship will be eligible to be assigned a descriptive
note specified design anchorage depth . . . metres, which will be entered in
column 6 of the Register Book.
8.10.4 Where the depth of water in the trial area is inadequate, suitable equivalent simulating
conditions will be considered as an alternative.
8.11 Marking and identification
8.11.1 The windlass is to be permanently marked with the following information:
- The size designation of the windlass (e.g. 100/3/45, where
100 is the nominal diameter of the chain cable in mm, 3 is the numeral in the
chain cable steel grade U3, and 45 refers to the holding load expressed as a
percentage of the chain cable breaking load).
- Maximum anchorage depth, in metres.
8.12 Structural requirements associated with anchoring
8.12.1 The windlass or winch is to be efficiently bedded and secured to the deck.
The thickness of the deck in way of the windlass or winch is to be increased and the
supporting structure for the anchor windlass is to be examined for the brake holding
loads specified by Pt 3, Ch 13, 8.4 Windlass design. The allowable stresses specified in
Table 13.8.2 Allowable stresses in windlass and
chain stopper supporting structure
are to be used to derive the net scantlings of the supporting structure. The capability
of the supporting structure to withstand buckling is also to be assessed. A corrosion
addition of 2 mm is to be added to the net thickness derived. The structural design
integrity of the bedplate is the responsibility of the Shipbuilder and windlass or winch
manufacturer.
8.12.2 Where cables pass through stoppers, these stoppers are to be manufactured
from ductile material and be designed to minimise the possibility of damage to, or
snagging of, the cable. They are to be capable of withstanding without permanent
deformation a load equal to 80 per cent of the Rule breaking load of the cable passing
over them. The allowable stresses specified in Table 13.8.2 Allowable stresses in windlass and
chain stopper supporting structure
are to be used to derive the net scantlings of the supporting structure. The capability
of the supporting structure to withstand buckling is also to be assessed. A corrosion
addition of 2 mm is to be added to the net thickness derived.
Table 13.8.2 Allowable stresses in windlass and
chain stopper supporting structure
|
Permissible
stress
N/mm2
|
(a)
For strength assessment by means of beam theory or grillage analysis
(see Note 1):
|
|
Normal
stress
Shear stress
Von Mises stress
|
1,00
σ0
0,60 σ0
1,00
σ0
|
(b) For
strength assessment by means of finite element analysis (see Note
2):
|
|
Von
Mises stress
|
1,00
σ0
|
Symbols
|
σ0 = specified minimum yield stress,
N/mm2
|
Note 1 Normal stress is
defined as the sum of bending and axial stresses. The shear stress to be
considered corresponds to the shear stress acting perpendicular to the
normal stress. No stress concentration factors are to be taken into
account.
Note 2 For strength
assessment by means of finite element analysis, the mesh is to be fine
enough to represent the geometry as realistically as possible. The aspect
ratios of elements are not to exceed 3. Girders are to be modelled using
shell or plane stress elements. Symmetric girder flanges may be modelled
by beam or truss elements. The element height of girder webs must not
exceed one-third of the web height. In way of small openings in girder
webs, the web thickness is to be reduced to an appropriate mean thickness
over the web height. Large openings are to be modelled. Stiffeners may be
modelled using shell or plane stress elements. The mesh size of
stiffeners is to be fine enough to obtain proper bending stress. If flat
bars are modelled using shell or plane stress elements, then dummy rod
elements are to be modelled at the free edge of the flat bars and the
stresses of the dummy elements are to be evaluated. Stresses are to be
read from the centre of the individual element. For shell elements the
stresses are to be evaluated at the mid plane of the element.
|
8.12.3 Hawse
pipes and anchor pockets are to be of ample thickness and of a suitable
size and form to house the anchors efficiently, preventing, as much
as practicable, slackening of the cable or movements of the anchor
being caused by wave action. The shell plating and framing in way
of the hawse pipes are to be reinforced as necessary. Reinforcing
is also to be arranged in way of those parts of bulbous bows liable
to be damaged by anchors or cables. Substantial chafing lips are to
be provided at shell and deck. These are to have sufficiently large,
radiused faces to minimise the probability of cable links being subjected
to high bending stresses. Alternatively, roller fairleads of suitable
design may be fitted. Where unpocketed rollers are used, it is recommended
that the roller diameter be not less than eleven times the chain diameter.
Where hawse pipes are not fitted, alternative arrangements will be
specially considered.
8.12.4 The
chain locker is to be of a capacity and depth adequate to provide
an easy direct lead for the cable into the chain pipes, when the cable
is fully stowed. Chain or spurling pipes are to be of suitable size
and provided with chafing lips. The port and starboard cables are
to be separated by a division in the locker.
8.12.5 Where
means of access is provided to the chain locker it is to be closed
by a substantial cover and secured by closely spaced bolts. Where
a means of access to spurling pipes or cable lockers is located below
the weather deck, the access cover and its securing arrangements are
to be in accordance with ISO 5894-1999, or an equivalent National
Standard acceptable to LR, recognised standards or equivalent for
watertight manhole covers. Butterfly nuts and/or hinged bolts are
prohibited as the securing mechanism for the access cover.
8.12.6 Chain
lockers and spurling pipes are to be watertight up to the exposed
weather deck and the space is to be efficiently drained. However,
bulkheads between separate chain lockers, or which form a common boundary
of chain lockers, need not be watertight.
8.12.7 Spurling
pipes are to be provided with permanently attached closing appliances
to minimise water ingress. Examples of acceptable arrangements are:
-
steel plates
with cutouts to accommodate chain links, or
-
canvas hoods
with a lashing arrangement that maintains the cover in the secured
position.
8.12.8 Provision is to be made for securing the bitter end of the chain cable to
the ship structure. The fastening for securing the bitter end is to be capable of
withstanding a force of not less than 15 per cent and not greater than 30 per cent of
the minimum breaking strength of the as fitted chain cable. It is to be provided with
suitable means such that, in case of emergency, the chain cable may be easily slipped to
sea from an accessible position outside the chain cable locker. Where the mechanism for
slipping the chain cable to sea penetrates the chain locker bulkhead, this penetration
is to be made watertight.
8.12.9 Alternatively the cable end connection may be accepted where it has been designed and
constructed to a recognised National or International Standard.
8.12.10 The cable clench supporting structure is to be adequately stiffened in accordance with
the breaking strength of the fastening provided.
8.12.11 Satisfactory
arrangements are to be made for the stowage and working of the stream
anchor, if provided.
8.12.12 On
dredging and reclamation craft the following are to be complied with:
-
On unpowered
ships, the windlass may be hand operated.
-
On split type
vessels, the arrangements are to be such that jamming of the anchor
cable during opening and closing operations of the hull will not occur.
8.12.13 When
wire rope instead of chain is used for the anchor cable, it is to
be stored on a suitably designed drum or reel. Fairleads intended
for use with wire rope cable are to be designed to minimise wear and
to avoid kinking or other damage occurring to the rope. Fairleads
should, in general, be fitted with rollers having a diameter not less
than eleven times the diameter of the anchor cable or as specified/
recommended by the rope manufacturer.
8.13 Structural requirements for windlasses on exposed fore decks
8.13.1 Windlasses
located on the exposed deck over the forward 0,25L of
the rule length, of ships of sea-going service of length 80 m or more,
where the height of the exposed deck in way of the item is less than
0,1L or 22 m above the summer load waterline, whichever
is the lesser, are to comply with the following requirements. Where
mooring winches are integral with the anchor windlass, they are to
be considered as part of the windlass.
8.13.2 The
following pressures and associated areas are to be applied, see
Figure 13.8.1 Windlass loading:
- 200 kN/m2 normal to the shaft axis and away from the
forward perpendicular, over the projected area in this direction;
- 150 kN/m2 parallel to the shaft axis and acting both
inboard and outboard separately, over the multiple of f times
the projected area in this direction;
where
f
|
= |
1+ B/H, but not greater than 2,5
|
B
|
= |
width
of windlass measured parallel to the shaft axis, in metres |
H
|
= |
overall
height of windlass, in metres. |
Figure 13.8.1 Windlass loading
8.13.3 Forces
in the bolts, chocks and stoppers securing the windlass to the deck
are to be calculated. The windlass is supported by N bolt
groups, each containing one or more bolts, see
Figure 13.8.2 Direction of forces and weight.
Figure 13.8.2 Direction of forces and weight
8.13.4 The
axial force R
i in bolt group (or bolt) i,
positive in tension, may be calculated from:
R
xi
|
= |
P
x
h
x
i
A
i/ x in kN
|
R
yi
|
= |
P
y
h
y
i
A
i/ y in kN, and
|
R
i
|
= |
R
xi + R
yi – R
si in kN
|
where
P
x
|
= |
force acting normal to the shaft axis, in kN |
P
y
|
= |
force acting parallel to the shaft axis, either inboard or outboard
whichever gives the greater force in bolt group i, in
kN
|
h
|
= |
shaft
height above the windlass mounting, in cm |
x
i, y
i
|
= |
x and y coordinates
of bolt group i from the centroid of all N bolt
groups, positive in the direction opposite to that of the applied
force, in cm
|
A
i
|
= |
cross sectional area of all bolts in group i, in
cm2
|
x
|
= |
Σ A
i
x
i
2 for N bolt
groups, in cm4
|
y
|
= |
Σ A
i
y
i
2 for N bolt
groups, in cm4
|
R
si
|
= |
static reaction at bolt group i, due to weight
of windlass, in kN.
|
8.13.5 Shear
forces F
xi, F
yi applied
to the bolt group i, and the resultant combined force F
i may be calculated from:
F
xi
|
= |
(Px – μ g
M)/N in kN |
F
yi
|
= |
(Py – μ g
M)/N in kN |
F
i
|
= |
|
where
α
|
= |
coefficient
of friction (0,5) |
M
|
= |
mass
of windlass, in tonnes |
g
|
= |
gravity
acceleration (9,81 m/sec2)
|
N
|
= |
number
of bolt groups. |
8.13.6 Tensile
axial stresses in the individual bolts in each bolt group i are
to be calculated. The horizontal forces F
xi and F
yi are normally to be reacted by shear chocks.
Where ‘fitted’ bolts are designed to support these shear
forces in one or both directions, the von Mises equivalent stresses
in the individual bolts are to be calculated, and compared to the
stress under proof load. Where pourable resins are incorporated in
the holding down arrangements, due account is to be taken in the calculations.
8.13.7 The
safety factor against bolt proof strength is to be not less than 2,0.
8.13.8 Bolts
are to be of lSO 898/1 material Grade 8.8, 10.9 or 12.9 or equivalent
and are to be pretensioned by controlled means to 70 to 90 per cent
of their yield stress. Pretensioning is to be in accordance with the
manufacturer’s instructions and, in general, pretensioning by
bolt torqueing up to bolt size M30 may be used. Beyond this, pretensioning
is to be carried out by an hydraulic tensioning device and the elongation
of the bolts measured to determine pre-load. Where resin chocks are
proposed plans and calculations are to be submitted for consideration.
8.13.9 The
windlass is to be efficiently bedded and secured to the deck. The
thickness of the deck in way of the windlass is to be increased. Adequate
stiffening of the deck in way of the windlass is to be provided. The
scantlings of the supporting structure and deck are to be determined
by additional calculations applying the weight of the windlass combined
with the resultant force on the seat due to the application of the
following design loads:
The allowable stresses specified in Table 13.8.2 Allowable stresses in windlass and
chain stopper supporting structure are to be used to derive the net scantlings of the
supporting structure. The capability of the supporting structure to withstand buckling
is also to be assessed. A corrosion addition of 2 mm is to be added to the net thickness
derived.
|