Section
2 Loading and design criteria
2.1 General
2.1.1 This Section
applies to Ro-Ro equipment operated whilst the ship is in a harbour
or sheltered water environment, and where cargo or vehicles may be
stowed on it in its seagoing condition whilst the ship is at sea,
i.e. Standard Service Category.
2.1.2 Where the
equipment is designed to operate in conditions other than those defined
in Ch 6, 2.1 General 2.1.1, the design is to be subject
to special consideration, i.e. Specified Service Category.
2.1.3 The operating
and stowed loading conditions are to be clearly specified in all submissions
together with hoisting speeds and braking times.
2.1.4 For the operating
condition, the equipment is to be considered with respect to the following
forces and loads:
-
Self-weight.
-
Applied loading.
-
Dynamic forces due to
hoisting/lowering.
-
Forces due to static
inclination of the ship.
2.1.5 The structure,
its support and locking mechanism are also to be examined with respect
to the sea-going condition for the following criteria, appropriate
to the ship’s characteristics:
-
Self-weight.
-
Applied load due to
vehicle or cargo loading.
-
Forces due to ship motion
and static inclination.
-
Weather loading, where
appropriate.
2.2 Basic loads
2.2.1 The self-weight
load, L
w, is the load imposed on the hoisting
mechanism by the weight of the structure and machinery.
2.2.2 The applied
load, L
c, is the loading imposed on the structure
by the cargo or vehicles.
2.2.3 The safe working
load (SWL) is the maximum load for which the equipment is certified
and is equal to the maximum value of L
c. For
equipment that is manoeuvred unloaded, the SWL shall be taken as the
self-weight of the structure for the determination of the required
safety factors, where applicable.
2.3 Dynamic forces due to hoisting
2.3.1 To take account
of acceleration and shock loading, the self-weight and applied load
are to be multiplied by 1,20.
2.4 Forces due to ship motion
2.4.1 In general,
Ro-Ro equipment is to be designed to operate in a harbour or sheltered
water environment where there is no significant motion of the ship
due to wave action.
2.4.2 For the operational
condition, the Ro-Ro equipment is to be designed to operate safely
and efficiently at an angle of heel of the ship of 5° and an angle
of trim of 2°, acting simultaneously. If it is the intention to
operate the Ro-Ro equipment at angles differing from the foregoing,
it is to be designed for these angles and the certificate marked accordingly.
2.4.3 In addition
to the loading/unloading conditions, the Ro-Ro equipment and its locking
mechanisms are also to be designed to withstand the following forces
in the sea-going condition:
-
Acceleration normal
to deck of ±1,0 g
Acceleration
parallel to deck in fore and aft directions of ±0,5 g
Static heel of 30°.
-
Acceleration normal
to deck of ±1,0 g
Accelerations
parallel to deck in transverse directions of ±0,5 g
Static heel of 30°.
2.5 Design loads
2.5.1 The design
loads are to be consistent with the ship’s loading manual and
are to include the details of the number and spacing of vehicles the
Ro-Ro equipment is designed to accommodate, the type of vehicles,
their weight, axle loading, tyre print dimensions, and number and
spacing of wheels and supports.
2.5.2 Due account
is to be taken of asymmetric loading where applicable. Where it is
intended to restrict the position of a load, such that the Ro-Ro equipment
is equally loaded, physical barriers are to be used. Other proposals
will be specially considered.
2.5.3 In addition
to vehicle loading, the Ro-Ro equipment is to be considered with respect
to minimum uniform deck loading (UDL) of 2,5 kN/m2 appropriate
to the deck or decks. In cases where the vehicle load is higher than
the given minimum value, the UDL is to be increased accordingly.
2.5.5 Where the
Ro-Ro equipment forms part of the ship’s watertight structure,
it is to comply with the requirements of the Rules for Ships as appropriate.
2.5.6 Where the
external Ro-Ro equipment is affected by wind load during the manoeuvring
or in stowed position, it is to be considered and load combinations
have to include the additional load as appropriate.
2.6 Allowable stress – Elastic failure
2.6.1 The allowable
stress, σa is to be taken as the failure stress of
the component concerned multiplied by a stress factor, F,
which depends on the load case considered. The allowable stress is
given by the general expression:
where
σa
|
= |
allowable stress |
F
|
= |
stress factor |
σ |
= |
failure stress. |
2.6.2 The stress factor, F, for steels in which
σy/σu ≤ 0,85 are given in Table 6.2.1 Stress factor, F
:
where
σy
|
= |
yield stress of material |
σu
|
= |
ultimate tensile stress of the material. |
Table 6.2.1 Stress factor, F
Load case
|
Case
1
|
Case 2
|
Case 3
|
Stress factor, F
|
0,60
|
0,75
|
0,85
|
Note Where an item forms
part of the hull structure, the scantlings are to comply with the
requirements of the Rules for Ships
|
Case 1:
|
Harbour
condition, loading and unloading
|
Case 2:
|
Sea-going
condition, loaded in-deck position or stowed unloaded
|
Case 3:
|
Manoeuvring operation or test load
|
2.6.3 For steel
with σy/σu > 0,85, the allowable stress
is to be derived from the following expression:
σa
|
= |
0,459F (σu + σy) |
τa
|
= |
0,266F (σu + σy) |
where
τa
|
= |
allowable shear stress. |
2.6.4 Steels with
σy/σu > 0,94 are not generally acceptable
and need to be specially considered.
2.6.5 The failure
stress for the elastic modes of failure are given in Table 6.2.2 Failure stress.
Table 6.2.2 Failure stress
Mode of failure
|
Symbol
|
Failure stress
|
Tension
|
σt
|
1,0σy
|
Compression
|
σc
|
1,0σy
|
Shear
|
τ
|
0,58σy
|
Bearing
|
σbr
|
1,0σy
|
2.6.6 For components
subjected to combined stresses, the following allowable stress criteria
are to be used:
-
σxx ≤
σa
-
σyy ≤
σa
-
το≤
τa
-
where
σxx
|
= |
applied
stress in x direction |
σyy
|
= |
applied
stress in y direction |
το
|
= |
applied
shear stress. |
2.6.7 The allowable
bearing stress is to be calculated as follows for all load cases 1
to 3:
2.6.8 In case the
structural analysis is carried out by means of detailed finite element
models, higher allowable stresses can be applied as follows:
-
σ1.FE ≤
1,1σa
-
σ2.FE ≤
1,1σa
-
τo.FE ≤
1,1τa
-
σe.FE ≤
1,12σa
where
σ2.FE
|
= |
second principal stress |
σe.FE
|
= |
equivalent stress |
σ1.FE
|
= |
first principal stress |
Higher allowable stresses, as defined above, may only be applied
if the actual stresses are localised. In case the actual stresses
can also be calculated by means of analytical methods, the above higher
allowable stresses are not applicable and Ch 6, 2.6 Allowable stress – Elastic failure 2.6.1 are to be applied.
2.7 Allowable stress – Plate buckling failure
2.8 Required deck plating thickness
2.9 Deflection criteria
2.9.1 The deflection
of the Ro-Ro equipment or of any individual member with respect to
Case 1 and 2, see
Table 6.2.1 Stress factor, F
,
is to be limited to:
l |
= |
distance
between supports, in mm. |
2.9.2 Where applicable,
the deflection is to be further limited to ensure the watertight integrity
of the ship is maintained.
2.10 Guide rails
2.10.1 Arrangements
are to be provided to restrict horizontal movements of Ro-Ro equipment
during operation, by guide rails or other means as applicable.
2.10.2 Where guide
rails are fitted, they are to be such that the maximum deflection,
resulting from horizontal components of load, is not greater than
6,0 mm. The working clearance between the Ro-Ro equipment and guide
rail is to be such as to allow free vertical movement of the Ro-Ro
equipment.
2.11 Stowage locks
2.11.1 Stowage
locks are to be provided to resist the vertical, forward/aft and lateral
loads as defined in Ch 6, 2.5 Design loads 2.5.1.
Arrangements are to be such that the locks do not loosen and impair
the watertight integrity of the ship. Reference is made to the applicable
requirements of the Rules for Ships.
2.12 Hoisting arrangements and items of loose gear
2.12.1 Where chains
are used as part of the hoisting arrangement, they are to have a minimum
safety factor of 4,0.
2.12.2 Where wire
ropes are used as part of the hoisting arrangement as well as items
of loose gear used therein, they are to have a safety factor given
by:
but not less than 4,0 nor greater than 5,0
where
SF |
= |
minimum safety
factor required |
L
|
= |
safe
working load [tonne] |
For the calculation of the safety factor, SF, only static forces need to be considered,
with a friction allowance of 2 per cent for roller bearings.
2.12.3 In cases
where the dynamic factor in sea-going conditions is greater than 1,6,
the safety factor may be derived as follows:
SF |
= |
SF(Harbour) x
Dynamic factor/1,6. |
2.13 Materials
|