6 Fuel Containment System

6.1 Goal

The goal of this chapter is to provide that gas storage is adequate so as to minimize the risk to personnel, the ship and the environment to a level that is equivalent to a conventional oil fuelled ship.

6.2 Functional requirements

This chapter relates to functional requirements in 3.2.1, 3.2.2, 3.2.5 and 3.2.8 to 3.2.17. In particular the following apply:

.1 the fuel containment system shall be so designed that a leak from the tank or its connections does not endanger the ship, persons on board or the environment. Potential dangers to be avoided include:
- .1 exposure of ship materials to temperatures below acceptable limits;
- .2 flammable fuels spreading to locations with ignition sources;
- .3 toxicity potential and risk of oxygen deficiency due to fuels and inert gases;
- .4 restriction of access to muster stations, escape routes and life-saving appliances (LSA); and
- .5 reduction in availability of LSA.
.2 the pressure and temperature in the fuel tank shall be kept within the design limits of the containment system and possible carriage requirements of the fuel;
.3 the fuel containment arrangement shall be so designed that safety actions after any gas leakage do not lead to an unacceptable loss of power; and
.4 if portable tanks are used for fuel storage, the design of the fuel containment system shall be equivalent to permanent installed tanks as described in this chapter.

6.3 Regulations – General

6.3.1 Natural gas in a liquid state may be stored with a maximum allowable relief valve setting (MARVS) of up to 1.0 MPa.

6.3.2 The Maximum Allowable Working Pressure (MAWP) of the gas fuel tank shall not exceed 90% of the Maximum Allowable Relief Valve Setting (MARVS).

6.3.3 A fuel containment system located below deck shall be gas tight towards adjacent spaces.

6.3.4 All tank connections, fittings, flanges and tank valves must be enclosed in gas tight tank connection spaces, unless the tank connections are on open deck. The space shall be able to safely contain leakage from the tank in case of leakage from the tank connections.

LR 6.3-01 To safely contain leakage, the tank connection space is to be designed to withstand the maximum calculated pressure within the space, the lowest temperature it could be subjected to, and the weight of accumulated liquid. This is to consider the rate and volume of release, relief venting to a safe location, and thermal isolation of tank connection space supports from the fuel storage tank and deck. The calculations to determine the possible leakage rate are to be submitted.

6.3.5 Pipe connections to the fuel storage tank shall be mounted above the highest liquid level in the tanks, except for fuel storage tanks of type C. Connections below the highest liquid level may however also be accepted for other tank types after special consideration by the Administration.

6.3.6 Piping between the tank and the first valve which release liquid in case of pipe failure shall have equivalent safety as the type C tank, with dynamic stress not exceeding the values given in 6.4.15.3.1.2.

6.3.7 The material of the bulkheads of the tank connection space shall have a design temperature corresponding with the lowest temperature it can be subject to in a probable maximum leakage scenario. The tank connection space shall be designed to withstand the maximum pressure build up during such a leakage. Alternatively, pressure relief venting to a safe location (mast) can be provided.

6.3.8 The probable maximum leakage into the tank connection space shall be determined based on detail design, detection and shutdown systems.

LR 6.3-02 The probable maximum leakage is to be agreed with LR.

6.3.9 If piping is connected below the liquid level of the tank it has to be protected by a secondary barrier up to the first valve.

6.3.10 If liquefied gas fuel storage tanks are located on open deck the ship steel shall be protected from potential leakages from tank connections and other sources of leakage by use of drip trays. The material is to have a design temperature corresponding to the temperature of the fuel carried at atmospheric pressure. The normal operation pressure of the tanks shall be taken into consideration for protecting the steel structure of the ship.

LR 6.3-03 Where the storage tank is located below the open deck, but the tank connections are on the open deck, drip trays are to be provided to protect the deck from leakages from tank connections and other sources of leakage.

LR 6.3-04 Where the storage tank and the tank connections are located below the deck, all tank connections are to be located in a tank connection space. Drip trays are not required in this case.

6.3.11 Means shall be provided whereby liquefied gas in the storage tanks can be safely emptied.

6.3.12 It shall be possible to empty, purge and vent fuel storage tanks with fuel piping systems. Instructions for carrying out these procedures must be available on board. Inerting shall be performed with an inert gas prior to venting with dry air to avoid an explosion hazardous atmosphere in tanks and fuel pipes. See detailed regulations in 6.10.

6.4 Regulations for liquefied gas fuel containment

6.4.1 General

6.4.1.1 The risk assessment required in 4.2 shall include evaluation of the ship's liquefied gas fuel containment system, and may lead to additional safety measures for integration into the overall vessel design.

LR 6.4-01 Details of the proposed design of containment systems are to be submitted for consideration, and it is recommended this is done at the earliest stage possible. For a description of LR’s system of approval, refer to the ShipRight Procedure Additional Design Procedures - Approval Scheme for Gas Ship Containment Systems.

6.4.1.2 The design life of fixed liquefied gas fuel containment system shall not be less than the design life of the ship or 20 years, whichever is greater.

6.4.1.3 The design life of portable tanks shall not be less than 20 years.

6.4.1.4 Liquefied gas fuel containment systems shall be designed in accordance with North Atlantic environmental conditions and relevant long-term sea state scatter diagrams for unrestricted navigation. Less demanding environmental conditions, consistent with the expected usage, may be accepted by the Administration for liquefied gas fuel containment systems used exclusively for restricted navigation. More demanding environmental conditions may be required for liquefied gas fuel containment systems operated in conditions more severe than the North Atlantic environment. ^footnote^,^footnote

6.4.1.5 Liquefied gas fuel containment systems shall be designed with suitable safety margins:

.1 to withstand, in the intact condition, the environmental conditions anticipated for the liquefied gas fuel containment system's design life and the loading conditions appropriate for them, which shall include full homogeneous and partial load conditions and partial filling to any intermediate levels; and
.2 being appropriate for uncertainties in loads, structural modelling, fatigue, corrosion, thermal effects, material variability, aging and construction tolerances.

LR 6.4-02 Except as otherwise mentioned, the suitable safety margin is to be considered as 2,0. A lower safety margin may be proposed, provided that a technical justification is submitted and justified.

6.4.1.6 The liquefied gas fuel containment system structural strength shall be assessed against failure modes, including but not limited to plastic deformation, buckling and fatigue. The specific design conditions that shall be considered for the design of each liquefied gas fuel containment system are given in 6.4.15. There are three main categories of design conditions:

.1 Ultimate Design Conditions – The liquefied gas fuel containment system structure and its structural components shall withstand loads liable to occur during its construction, testing and anticipated use in service, without loss of structural integrity. The design shall take into account proper combinations of the following loads:
- .1 internal pressure;
- .2 external pressure;
- .3 dynamic loads due to the motion of the ship in all loading conditions;
- .4 thermal loads;
- .5 sloshing loads;
- .6 loads corresponding to ship deflections;
- .7 tank and liquefied gas fuel weight with the corresponding reaction in way of supports;
- .8 insulation weight;
- .9 loads in way of towers and other attachments; and
- .10 test loads.
.2 Fatigue Design Conditions – The liquefied gas fuel containment system structure and its structural components shall not fail under accumulated cyclic loading.

LR.6.4-03 Unless it can be demonstrated that partial fill conditions have a negligible contribution to fatigue life, loading conditions to be considered for fatigue design need to include partial fill conditions selected to maximise the dynamic load on internal tank members, including sloshing induced loads, see also 6.4.9.4.1.3 and 6.4.12.2.3.

.3 Accidental Design Conditions – The liquefied gas fuel containment system shall meet each of the following accident design conditions (accidental or abnormal events), addressed in this Code:
- .1 Collision – The liquefied gas fuel containment system shall withstand the collision loads specified in 6.4.9.5.1 without deformation of the supports or the tank structure in way of the supports likely to endanger the tank and its supporting structure.
- .2 Fire – The liquefied gas fuel containment systems shall sustain without rupture the rise in internal pressure specified in 6.7.3.1 under the fire scenarios envisaged therein.
- .3 Flooded compartment causing buoyancy on tank – the anti-flotation arrangements shall sustain the upward force, specified in 6.4.9.5.2 and there shall be no endangering plastic deformation to the hull. Plastic deformation may occur in the fuel containment system provided it does not endanger the safe evacuation of the ship.

6.4.1.7 Measures shall be applied to ensure that scantlings required meet the structural strength provisions and are maintained throughout the design life. Measures may include, but are not limited to, material selection, coatings, corrosion additions, cathodic protection and inerting.

6.4.1.8 An inspection/survey plan for the liquefied gas fuel containment system shall be developed and approved by the Administration. The inspection/survey plan shall identify aspects to be examined and/or validated during surveys throughout the liquefied gas fuel containment system's life and, in particular, any necessary in-service survey, maintenance and testing that was assumed when selecting liquefied gas fuel containment system design parameters. The inspection/survey plan may include specific critical locations as per 6.4.12.2.8 or 6.4.12.2.9.

LR 6.4-04 Due consideration is to be given to the design parameters and construction of the fuel containment system, when developing the inspection/survey plan of the fuel containment system.

6.4.1.9 Liquefied gas fuel containment systems shall be designed, constructed and equipped to provide adequate means of access to areas that need inspection as specified in the inspection/survey plan. Liquefied gas fuel containment systems, including all associated internal equipment shall be designed and built to ensure safety during operations, inspection and maintenance.

6.4.2 Liquefied gas fuel containment safety principles

6.4.2.1 The containment systems shall be provided with a complete secondary liquid-tight barrier capable of safely containing all potential leakages through the primary barrier and, in conjunction with the thermal insulation system, of preventing lowering of the temperature of the ship structure to an unsafe level.

6.4.2.2 The size and configuration or arrangement of the secondary barrier may be reduced or omitted where an equivalent level of safety can be demonstrated in accordance with 6.4.2.3 to 6.4.2.5 as applicable.

6.4.2.3 Liquefied gas fuel containment systems for which the probability for structural failures to develop into a critical state has been determined to be extremely low but where the possibility of leakages through the primary barrier cannot be excluded, shall be equipped with a partial secondary barrier and small leak protection system capable of safely handling and disposing of the leakages (a critical state means that the crack develops into unstable condition).

The arrangements shall comply with the following:

.1 failure developments that can be reliably detected before reaching a critical state (e.g. by gas detection or inspection) shall have a sufficiently long development time for remedial actions to be taken; and
.2 failure developments that cannot be safely detected before reaching a critical state shall have a predicted development time that is much longer than the expected lifetime of the tank.

6.4.2.4 No secondary barrier is required for liquefied gas fuel containment systems, e.g. type C independent tanks, where the probability for structural failures and leakages through the primary barrier is extremely low and can be neglected.

6.4.2.5 For independent tanks requiring full or partial secondary barrier, means for safely disposing of leakages from the tank shall be arranged.

6.4.3 Secondary barriers in relation to tank types

Secondary barriers in relation to the tank types defined in 6.4.15 shall be provided in accordance with the following table.

Basic tank type	Secondary barrier requirements
Membrane	Complete secondary barrier

Independent
Type A	Complete secondary barrier
Type B	Partial secondary barrier
Type C	No secondary barrier required

6.4.4 Design of secondary barriers

The design of the secondary barrier, including spray shield if fitted, shall be such that:

.1 it is capable of containing any envisaged leakage of liquefied gas fuel for a period of 15 days unless different criteria apply for particular voyages, taking into account the load spectrum referred to in 6.4.12.2.6;
.2 physical, mechanical or operational events within the liquefied gas fuel tank that could cause failure of the primary barrier shall not impair the due function of the secondary barrier, or vice versa;
.3 failure of a support or an attachment to the hull structure will not lead to loss of liquid tightness of both the primary and secondary barriers;
.4 it is capable of being periodically checked for its effectiveness by means of a visual inspection or other suitable means acceptable to the Administration;
.
5 the methods required in 6.4.4.4 shall be approved by the Administration and shall include, as a minimum:
- .1 details on the size of defect acceptable and the location within the secondary barrier, before its liquid tight effectiveness is compromised;
- .2 accuracy and range of values of the proposed method for detecting defects in .1 above;
- .3 scaling factors to be used in determining the acceptance criteria if full-scale model testing is not undertaken; and
- .4 effects of thermal and mechanical cyclic loading on the effectiveness of the proposed test.
.6 the secondary barrier shall fulfil its functional requirements at a static angle of heel of 30°.

6.4.5 Partial secondary barriers and primary barrier small leak protection system

6.4.5.1 Partial secondary barriers as permitted in 6.4.2.3 shall be used with a small leak protection system and meet all the regulations in 6.4.4.

The small leak protection system shall include means to detect a leak in the primary barrier, provision such as a spray shield to deflect any liquefied gas fuel down into the partial secondary barrier, and means to dispose of the liquid, which may be by natural evaporation.

6.4.5.2 The capacity of the partial secondary barrier shall be determined, based on the liquefied gas fuel leakage corresponding to the extent of failure resulting from the load spectrum referred to in 6.4.12.2.6, after the initial detection of a primary leak. Due account may be taken of liquid evaporation, rate of leakage, pumping capacity and other relevant factors.

6.4.5.3 The required liquid leakage detection may be by means of liquid sensors, or by an effective use of pressure, temperature or gas detection systems, or any combination thereof.

6.4.5.4 For independent tanks for which the geometry does not present obvious locations for leakage to collect, the partial secondary barrier shall also fulfil its functional requirements at a nominal static angle of trim.

6.4.6 Supporting arrangements

6.4.6.1 The liquefied gas fuel tanks shall be supported by the hull in a manner that prevents bodily movement of the tank under the static and dynamic loads defined in 6.4.9.2 to 6.4.9.5, where applicable, while allowing contraction and expansion of the tank under temperature variations and hull deflections without undue stressing of the tank and the hull.

6.4.6.2 Anti-flotation arrangements shall be provided for independent tanks and capable of withstanding the loads defined in 6.4.9.5.2 without plastic deformation likely to endanger the hull structure.

LR 6.4-05 An adequate clearance is to be provided between the anti-flotation chocks and the ship’s hull in all operational conditions. Details of the calculations of the clearances between anti-flotation chocks are to be submitted for approval. The inspection/survey plan indicated in 6.4.1.8 is to include details for the verification of these clearances during construction and periodical surveys.

6.4.6.3 Supports and supporting arrangements shall withstand the loads defined in 6.4.9.3.3.8 and 6.4.9.5, but these loads need not be combined with each other or with wave-induced loads.

LR 6.4-06 Tank supports are generally to be located in way of the primary support structure of the tank and the ship’s hull. Steel seatings are to be arranged, so as to ensure an effective distribution of the transmitted load and reactions into the fuel tank and the supporting structure.

LR 6.4-07 Where deemed necessary by LR and depending upon the type and size of the fuel tank(s), the strength of the supporting arrangements may be required to be verified by direct calculations.

6.4.7 Associated structure and equipment

6.4.7.1 Liquefied gas fuel containment systems shall be designed for the loads imposed by associated structure and equipment. This includes pump towers, liquefied gas fuel domes, liquefied gas fuel pumps and piping, stripping pumps and piping, nitrogen piping, access hatches, ladders, piping penetrations, liquid level gauges, independent level alarm gauges, spray nozzles, and instrumentation systems (such as pressure, temperature and strain gauges).

6.4.8 Thermal insulation

6.4.8.1 Thermal insulation shall be provided as required to protect the hull from temperatures below those allowable (see 6.4.13.1.1) and limit the heat flux into the tank to the levels that can be maintained by the pressure and temperature control system applied in 6.9.

LR 6.4-08 Thermal insulation shall also comply with the requirements of 6.4.13.3.

6.4.9 Design loads

6.4.9.1 General

6.4.9.1.1 This section defines the design loads that shall be considered with regard to regulations in 6.4.10 to 6.4.12. This includes load categories (permanent, functional, environmental and accidental) and the description of the loads.

6.4.9.1.2 The extent to which these loads shall be considered depends on the type of tank, and is more fully detailed in the following paragraphs.

6.4.9.1.3 Tanks, together with their supporting structure and other fixtures, shall be designed taking into account relevant combinations of the loads described below.

6.4.9.2 Permanent loads

6.4.9.2.1 Gravity loads

The weight of tank, thermal insulation, loads caused by towers and other attachments shall be considered.

6.4.9.2.2 Permanent external loads

Gravity loads of structures and equipment acting externally on the tank shall be considered.

6.4.9.3 Functional loads

6.4.9.3.1 Loads arising from the operational use of the tank system shall be classified as functional loads.

6.4.9.3.2 All functional loads that are essential for ensuring the integrity of the tank system, during all design conditions, shall be considered.

6.4.9.3.3 As a minimum, the effects from the following criteria, as applicable, shall be considered when establishing functional loads:

(a) internal pressure
(b) external pressure
(c) thermally induced loads
(d) vibration
(e) interaction loads
(f) loads associated with construction and installation
(g) test loads
(h) static heel loads
(i) weight of liquefied gas fuel
(j) sloshing
(k) wind impact, wave impacts and green sea effect for tanks installed on open deck.

6.4.9.3.3.1 Internal pressure

.1 In all cases, including 6.4.9.3.3.1.2, P₀ shall not be less than MARVS.
.2 For liquefied gas fuel tanks where there is no temperature control and where the pressure of the liquefied gas fuel is dictated only by the ambient temperature, P₀ shall not be less than the gauge vapour pressure of the liquefied gas fuel at a temperature of 45°C except as follows:
- .1 Lower values of ambient temperature may be accepted by the Administration for ships operating in restricted areas. Conversely, higher values of ambient temperature may be required.
- .2 For ships on voyages of restricted duration, P₀ may be calculated based on the actual pressure rise during the voyage and account may be taken of any thermal insulation of the tank.

LR 6.4-09 Consideration will be given to the use of a higher or lower ambient temperature where appropriate. In such cases, the temperature which has been used will be included in the class notation.

.3 Subject to special consideration by the Administration and to the limitations given in 6.4.15 for the various tank types, a vapour pressure P_h higher than P₀ may be accepted for site specific conditions (harbour or other locations), where dynamic loads are reduced.

LR 6.4-10 Where a vapour pressure, P_h, higher than P_o, is accepted in accordance with 6.4.9.3.3.1.3, such conditions are to be clearly indicated in the ship’s Loading Manual.

.4 Pressure used for determining the internal pressure shall be:
- .1 (P_gd)max is the associated liquid pressure determined using the maximum design accelerations.
- .2 (P_{gd site})max is the associated liquid pressure determined using site specific accelerations.
- .3 P_eq should be the greater of P_eq1 and P_eq2 calculated as follows:
  - P_eq1 = P₀ + (P_gd)max (MPa),
  - P_eq2 = P_h + (P_{gd site})max (MPa).
.5 The internal liquid pressures are those created by the resulting acceleration of the centre of gravity of the liquefied gas fuel due to the motions of the ship referred to in 6.4.9.4.1.1. The value of internal liquid pressure P_gd resulting from combined effects of gravity and dynamic accelerations shall be calculated as follows:
- P_gd = α_βZ_β(ρ/(1.02 X 10⁵)) (MPa)
- where:
  - α_β = dimensionless acceleration (i.e. relative to the acceleration of gravity), resulting from gravitational and dynamic loads, in an arbitrary direction β; (see figure 6.4.1).
    
    For large tanks, an acceleration ellipsoid, taking account of transverse vertical and longitudinal accelerations, should be used.
  - Z_β = largest liquid height (m) above the point where the pressure is to be determined measured from the tank shell in the β direction (see figure 6.4.2).
    
    Tank domes considered to be part of the accepted total tank volume shall be taken into account when determining Z_β unless the total volume of tank domes V_d does not exceed the following value:
    
    where:
    - V_t = tank volume without any domes; and
    - FL = filling limit according to 6.8.
  - ρ = maximum liquefied gas fuel density (kg/m³) at the design temperature.
- The direction that gives the maximum value (P_gd)max or (P_{gd
  site})max shall be considered. Where acceleration components in three directions need to be considered, an ellipsoid shall be used instead of the ellipse in figure 6.4.1. The above formula applies only to full tanks.

Figure 6.4.1 – Acceleration ellipsoid

Figure 6.4.2 – Determination of internal pressure heads

6.4.9.3.3.2 External pressure

External design pressure loads shall be based on the difference between the minimum internal pressure and the maximum external pressure to which any portion of the tank may be simultaneously subjected.

6.4.9.3.3.3 Thermally induced loads

6.4.9.3.3.3.1 Transient thermally induced loads during cooling down periods shall be considered for tanks intended for liquefied gas fuel temperatures below minus 55°C.

6.4.9.3.3.3.2 Stationary thermally induced loads shall be considered for liquefied gas fuel containment systems where the design supporting arrangements or attachments and operating temperature may give rise to significant thermal stresses (see paragraph 6.9.2).

6.4.9.3.3.4 Vibration

The potentially damaging effects of vibration on the liquefied gas fuel containment system shall be considered.

LR 6.4-11 Vibration analysis of the pump tower is to be carried out where appropriate, i.e. considering the dimensions of the containment system in accordance with LR’s ShipRight Procedure Additional Design Procedures - Procedure for Analysis of pump tower and pump tower base. The designer may propose an alternative equivalent procedure subject to agreement with LR.

6.4.9.3.3.5 Interaction loads

The static component of loads resulting from interaction between liquefied gas fuel containment system and the hull structure, as well as loads from associated structure and equipment, shall be considered.

6.4.9.3.3.6 Loads associated with construction and installation

Loads or conditions associated with construction and installation shall be considered, e.g. lifting.

6.4.9.3.3.7 Test loads

Account shall be taken of the loads corresponding to the testing of the liquefied gas fuel containment system referred to in 16.5.

6.4.9.3.3.8 Static heel loads

Loads corresponding to the most unfavourable static heel angle within the range 0° to 30°shall be considered.

6.4.9.3.3.9 Other loads

Any other loads not specifically addressed, which could have an effect on the liquefied gas fuel containment system, shall be taken into account.

6.4.9.4 Environmental loads

6.4.9.4.1 Environmental loads are defined as those loads on the liquefied gas fuel containment system that are caused by the surrounding environment and that are not otherwise classified as a permanent, functional or accidental load.

6.4.9.4.1.1 Loads due to ship motion

The determination of dynamic loads shall take into account the long-term distribution of ship motion in irregular seas, which the ship will experience during its operating life. Account may be taken of the reduction in dynamic loads due to necessary speed reduction and variation of heading. The ship's motion shall include surge, sway, heave, roll, pitch and yaw. The accelerations acting on tanks shall be estimated at their centre of gravity and include the following components:

.1 vertical acceleration: motion accelerations of heave, pitch and, possibly roll (normal to the ship base);
.2 transverse acceleration: motion accelerations of sway, yaw and roll and gravity component of roll; and
.3 longitudinal acceleration: motion accelerations of surge and pitch and gravity component of pitch.

Methods to predict accelerations due to ship motion shall be proposed and approved by the Administration^footnote.

Ships for restricted service may be given special consideration.

LR 6.4-12 Direct calculation procedures capable of deriving the dynamic loads due to ship motions, are to take into account the ship’s actual form and weight distribution. LR’s direct calculation method involves derivation of response to regular waves by appropriate sea-keeping software, short-term response to irregular waves using the sea spectrum concept, and long-term response predictions using statistical distributions of sea states. Other direct calculation methods submitted for approval are expected to contain these three elements and produce similar and consistent results when compared with LR’s method. Simplified dynamic loading spectra, where proposed, are to be submitted for consideration.

6.4.9.4.1.2 Dynamic interaction loads

Account shall be taken of the dynamic component of loads resulting from interaction between liquefied gas fuel containment systems and the hull structure, including loads from associated structures and equipment.

6.4.9.4.1.3 Sloshing loads

The sloshing loads on a liquefied gas fuel containment system and internal components shall be evaluated for the full range of intended filling levels.

LR 6.4-13 Where loading conditions are proposed including one or more partially filled tanks, calculations or model tests will be required to show that the resulting loads and pressure are within acceptable limits for the scantlings of the tanks. In general, calculations are to be carried out in accordance with LR’s ShipRight Procedure Design and Construction Procedure, Structural Design Assessment, Sloshing Loads and Scantling Assessment. Alternative procedures may be specially considered.

LR 6.4-14 Investigations to ensure that the internal structure, equipment and pipework exposed to fluid motion are of adequate strength are also to be carried out. The assessment of pump tower and pump tower base due to fluid motion is in general to be carried out in accordance with LR’s ShipRight Procedure Additional Design Procedures, Procedure for Analysis of Pump Tower and Pump Tower Base.

6.4.9.4.1.4 Snow and ice loads

Snow and icing shall be considered, if relevant.

LR 6.4-15 Where a vessel is intended to operate in cold climates, the temperature on exposed surfaces is to be considered. See the Rules for the Winterisation of Ships.

6.4.9.4.1.5 Loads due to navigation in ice

Loads due to navigation in ice shall be considered for ships intended for such service.

LR 6.4-16 Where a vessel is intended to navigate through ice, the vessel’s interaction with ice is to be considered. See Pt 8 of the Rules for Ships.

6.4.9.4.1.6 Green sea loading

Account shall be taken to loads due to water on deck.

6.4.9.4.1.7 Wind loads

Account shall be taken to wind generated loads as relevant.

6.4.9.5 Accidental loads

Accidental loads are defined as loads that are imposed on a liquefied gas fuel containment system and it's supporting arrangements under abnormal and unplanned conditions.

6.4.9.5.1 Collision load

The collision load shall be determined based on the fuel containment system under fully loaded condition with an inertial force corresponding to "a" in the table below in forward direction and "a/2" in the aft direction, where "g" is gravitational acceleration.

Ship length (L)	Design acceleration (a)
L > 100 m	0,5 g
60 < L ≤ 100 m
L ≤ 60 m	2g

Special consideration should be given to ships with Froude number (Fn) > 0,4.

6.4.9.5.2 Loads due to flooding on ship

For independent tanks, loads caused by the buoyancy of a fully submerged empty tank shall be considered in the design of anti-flotation chocks and the supporting structure in both the adjacent hull and tank structure.

LR 6.4-17 Subject to agreement by the National Administration, anti-flotation chocks and supporting structure may be designed based on the tank being empty and submerged up to the damaged water line obtained when the tank compartment is flooded, or the scantling draft, whichever is deeper.

6.4.10 Structural integrity

6.4.10.1 General

6.4.10.1.1 The structural design shall ensure that tanks have an adequate capacity to sustain all relevant loads with an adequate margin of safety. This shall take into account the possibility of plastic deformation, buckling, fatigue and loss of liquid and gas tightness.

6.4.10.1.2 The structural integrity of liquefied gas fuel containment systems can be demonstrated by compliance with 6.4.15, as appropriate for the liquefied gas fuel containment system type.

6.4.10.1.3 For other liquefied gas fuel containment system types, that are of novel design or differ significantly from those covered by 6.4.15, the structural integrity shall be demonstrated by compliance with 6.4.16.

6.4.11 Structural analysis

6.4.11.1 Analysis

6.4.11.1.1 The design analyses shall be based on accepted principles of statics, dynamics and strength of materials.

6.4.11.1.2 Simplified methods or simplified analyses may be used to calculate the load effects, provided that they are conservative. Model tests may be used in combination with, or instead of, theoretical calculations. In cases where theoretical methods are inadequate, model or full-scale tests may be required.

LR 6.4-18 Where simplified methods or simplified analyses are proposed, their details are to be agreed with LR before commencement of application.

6.4.11.1.3 When determining responses to dynamic loads, the dynamic effect shall be taken into account where it may affect structural integrity.

6.4.11.2 Load scenarios

6.4.11.2.1 For each location or part of the liquefied gas fuel containment system to be considered and for each possible mode of failure to be analysed, all relevant combinations of loads that may act simultaneously shall be considered.

LR 6.4-19 LR is to be consulted for guidance on the relevant combination of loads to be taken into account in the analysis at as early a stage as possible.

6.4.11.2.2 The most unfavourable scenarios for all relevant phases during construction, handling, testing and in service conditions shall be considered.

6.4.11.2.3 When the static and dynamic stresses are calculated separately and unless other methods of calculation are justified, the total stresses shall be calculated according to:

where:

σ_x.st, σ_y.st, σ_z.st, τ_xy.st, τ_xz.st and τ_yz.st are static stresses; and
σ_x.dyn, σ_y.dyn, σ_z.dyn, τ_xy.dyn, τ_xz.dyn and τ_yz.dyn are dynamic stresses,

each shall be determined separately from acceleration components and hull strain components due to deflection and torsion.

6.4.12 Design conditions

All relevant failure modes shall be considered in the design for all relevant load scenarios and design conditions. The design conditions are given in the earlier part of this chapter, and the load scenarios are covered by 6.4.11.2.

6.4.12.1 Ultimate design condition

6.4.12.1.1 Structural capacity may be determined by testing, or by analysis, taking into account both the elastic and plastic material properties, by simplified linear elastic analysis or by the provisions of this Code:

.1 Plastic deformation and buckling shall be considered.

LR 6.4-20 Plastic deformation analyses is to be conducted in accordance with an agreed recognised Standard.

.2 Analysis shall be based on characteristic load values as follows:

Permanent loads	Expected values
Functional loads	Specified values
Environmental loads	For wave loads: most probable largest load encountered during 10⁸ wave encounters.

.3 For the purpose of ultimate strength assessment the following material parameters apply:
- .1 R_e = specified minimum yield stress at room temperature (N/mm²). If the stress-strain curve does not show a defined yield stress, the 0.2% proof stress applies.
- .2 R_m = specified minimum tensile strength at room temperature (N/mm²).
  - For welded connections where under-matched welds, i.e. where the weld metal has lower tensile strength than the parent metal, are unavoidable, such as in some aluminium alloys, the respective R_e and R_m of the welds, after any applied heat treatment, shall be used. In such cases the transverse weld tensile strength shall not be less than the actual yield strength of the parent metal. If this cannot be achieved, welded structures made from such materials shall not be incorporated in liquefied gas fuel containment systems.
- The above properties shall correspond to the minimum specified mechanical properties of the material, including the weld metal in the as fabricated condition. Subject to special consideration by the Administration, account may be taken of the enhanced yield stress and tensile strength at low temperature.
.4 The equivalent stress σ_c (von Mises, Huber) shall be determined by:
- where:
  - σ_x = total normal stress in x-direction;
  - σ_y = total normal stress in y-direction;
  - σ_z = total normal stress in z-direction;
  - τ_xy = total shear stress in x-y plane;
  - τ_xz = total shear stress in x-z plane; and
  - τ_yz = total shear stress in y-z plane.
- The above values shall be calculated as described in 6.4.11.2.3.
.5 Allowable stresses for materials other than those covered by 7.4 shall be subject to approval by the Administration in each case.

LR 6.4-21 For materials other than those covered by Ch 7, details of the allowable stresses are to be submitted for consideration.

.6 Stresses may be further limited by fatigue analysis, crack propagation analysis and buckling criteria.

6.4.12.2 Fatigue Design Condition

.1 The fatigue design condition is the design condition with respect to accumulated cyclic loading.
.2 Where a fatigue analysis is required the cumulative effect of the fatigue load shall comply with:
where:
- n_i = number of stress cycles at each stress level during the life of the tank;
- N_i = number of cycles to fracture for the respective stress level according to the Wohler (S-N) curve;
- n_Loading = number of loading and unloading cycles during the life of the tank not to be less than 1000. Loading and unloading cycles include a complete pressure and thermal cycle;
- N_Loading = number of cycles to fracture for the fatigue loads due to loading and unloading; and
- C_w = maximum allowable cumulative fatigue damage ratio.
The fatigue damage shall be based on the design life of the tank but not less than 10⁸ wave encounters.
.3 Where required, the liquefied gas fuel containment system shall be subject to fatigue analysis, considering all fatigue loads and their appropriate combinations for the expected life of the liquefied gas fuel containment system. Consideration shall be given to various filling conditions.
.4 Design S-N curves used in the analysis shall be applicable to the materials and weldments, construction details, fabrication procedures and applicable state of the stress envisioned.

The S-N curves shall be based on a 97.6% probability of survival corresponding to the mean-minus-two-standard-deviation curves of relevant experimental data up to final failure. Use of S-N curves derived in a different way requires adjustments to the acceptable Cw values specified in 6.4.12.2.7 to 6.4.12.2.9.

.5 Analysis shall be based on characteristic load values as follows:

Permanent loads	Expected values
Functional loads	Specified values or specified history
Environmental loads	Expected load history, but not less than 10⁸ cycles

If simplified dynamic loading spectra are used for the estimation of the fatigue life, those shall be specially considered by the Administration.

.6 Where the size of the secondary barrier is reduced, as is provided for in 6.4.2.3, fracture mechanics analyses of fatigue crack growth shall be carried out to determine:
- .1 crack propagation paths in the structure, where necessitated by 6.4.12.2.7 to 6.4.12.2.9, as applicable;
- .2 crack growth rate;
- .3 the time required for a crack to propagate to cause a leakage from the tank;
- .4 the size and shape of through thickness cracks; and
- .5 the time required for detectable cracks to reach a critical state after penetration through the thickness.
- The fracture mechanics are in general based on crack growth data taken as a mean value plus two standard deviations of the test data. Methods for fatigue crack growth analysis and fracture mechanics shall be based on recognized standards.
- In analysing crack propagation the largest initial crack not detectable by the inspection method applied shall be assumed, taking into account the allowable non-destructive testing and visual inspection criterion as applicable.
- Crack propagation analysis specified in 6.4.12.2.7 the simplified load distribution and sequence over a period of 15 days may be used. Such distributions may be obtained as indicated in figure 6.4.3. Load distribution and sequence for longer periods, such as in 6.4.12.2.8 and 6.4.12.2.9 shall be approved by the Administration.
- The arrangements shall comply with 6.4.12.2.7 to 6.4.12.2.9 as applicable.
.7 For failures that can be reliably detected by means of leakage detection:
- C_w shall be less than or equal to 0.5.
- Predicted remaining failure development time, from the point of detection of leakage till reaching a critical state, shall not be less than 15 days unless different regulations apply for ships engaged in particular voyages.
.
8 For failures that cannot be detected by leakage but that can be reliably detected at the time of in-service inspections:
- C_w shall be less than or equal to 0.5.
- Predicted remaining failure development time, from the largest crack not detectable by in-service inspection methods until reaching a critical state, shall not be less than three (3) times the inspection interval.
.9 In particular locations of the tank where effective defect or crack development detection cannot be assured, the following, more stringent, fatigue acceptance criteria shall be applied as a minimum:
- C_w shall be less than or equal to 0.1.
- Predicted failure development time, from the assumed initial defect until reaching a critical state, shall not be less than three (3) times the lifetime of the tank.

Figure 6.4.3 – Simplified load distribution

6.4.12.3 Accidental design condition

6.4.12.3.1 The accidental design condition is a design condition for accidental loads with extremely low probability of occurrence.

6.4.12.3.2 Analysis shall be based on the characteristic values as follows:

Permanent loads	Expected values
Functional loads	Specified values
Environmental loads	Specified values
Accidental loads	Specified values or expected values

Loads mentioned in 6.4.9.3.3.8 and 6.4.9.5 need not be combined with each other or with wave-induced loads.

6.4.13 Materials and construction

6.4.13.1 Materials

6.4.13.1.1 Materials forming ship structure

6.4.13.1.1.1 To determine the grade of plate and sections used in the hull structure, a temperature calculation shall be performed for all tank types. The following assumptions shall be made in this calculation:

.1 The primary barrier of all tanks shall be assumed to be at the liquefied gas fuel temperature.
.2 In addition to .1 above, where a complete or partial secondary barrier is required it shall be assumed to be at the liquefied gas fuel temperature at atmospheric pressure for any one tank only.
.3 For worldwide service, ambient temperatures shall be taken as 5°C for air and 0°C for seawater. Higher values may be accepted for ships operating in restricted areas and conversely, lower values may be imposed by the Administration for ships trading to areas where lower temperatures are expected during the winter months.
.4 Still air and sea water conditions shall be assumed, i.e. no adjustment for forced convection.
.5 Degradation of the thermal insulation properties over the life of the ship due to factors such as thermal and mechanical ageing, compaction, ship motions and tank vibrations as defined in 6.4.13.3.6 and 6.4.13.3.7 shall be assumed.
.6 The cooling effect of the rising boil-off vapour from the leaked liquefied gas fuel shall be taken into account where applicable.
.7 Credit for hull heating may be taken in accordance with 6.4.13.1.1.3, provided the heating arrangements are in compliance with 6.4.13.1.1.4.
.8 No credit shall be given for any means of heating, except as described in 6.4.13.1.1.3.
.9 For members connecting inner and outer hulls, the mean temperature may be taken for determining the steel grade.

LR 6.4-22 The minimum temperatures used in determining the required grade of materials are to be calculated using the boundary conditions given in 6.4.13.1.1.1. Where a higher or lower ambient temperature is to be used in accordance with 6.4.13.1.1.1.3, this is to be included in the class notation. The revised ambient temperatures are to be considered when determining the required hull material grades, both within and outside the cargo area.

LR 6.4-23 The temperatures of members connecting the inner and outer hulls where applicable are to be obtained from the calculations.

LR 6.4-24 The heat balance method may be used to carry out the temperature calculations required in 6.4.13.1.1.1.

6.4.13.1.1.2 The materials of all hull structures for which the calculated temperature in the design condition is below 0°C, due to the influence of liquefied gas fuel temperature, shall be in accordance with table 7.5. This includes hull structure supporting the liquefied gas fuel tanks, inner bottom plating, longitudinal bulkhead plating, transverse bulkhead plating, floors, webs, stringers and all attached stiffening members.

LR 6.4-25 The material of the hull structure, other than that forming part of, or adjoining, the fuel containment system, is to comply with the requirements given in LR 7.4-02 and subsequent paragraphs.

6.4.13.1.1.3 Means of heating structural materials may be used to ensure that the material temperature does not fall below the minimum allowed for the grade of material specified in table 7.5. In the calculations required in 6.4.13.1.1.1, credit for such heating may be taken in accordance with the following principles:

.1 for any transverse hull structure;
.2 for longitudinal hull structure referred to in 6.4.13.1.1.2 where colder ambient temperatures are specified, provided the material remains suitable for the ambient temperature conditions of plus 5°C for air and 0°C for seawater with no credit taken in the calculations for heating; and
.3 as an alternative to 6.4.13.1.1.3.2, for longitudinal bulkhead between liquefied gas fuel tanks, credit may be taken for heating provided the material remain suitable for a minimum design temperature of minus 30°C, or a temperature 30°C lower than that determined by 6.4.13.1.1.1 with the heating considered, whichever is less. In this case, the ship's longitudinal strength shall comply with SOLAS regulation II-1/3-1 for both when those bulkhead(s) are considered effective and not.

LR 6.4-26 Details of proposed systems for the means of heating structural members to ensure that the material temperature does not fall below the minimum temperature allowed for the grade of material specified in Table 7.5 are to be submitted.

6.4.13.1.1.4 The means of heating referred to in 6.4.13.1.1.3 shall comply with the following:

.1 the heating system shall be arranged so that, in the event of failure in any part of the system, standby heating can be maintained equal to no less than 100% of the theoretical heat requirement;
.2 the heating system shall be considered as an essential auxiliary. All electrical components of at least one of the systems provided in accordance with 6.4.13.1.1.3.1 shall be supplied from the emergency source of electrical power; and
.3 the design and construction of the heating system shall be included in the approval of the containment system by the Administration.

6.4.13.2 Materials of primary and secondary barriers

LR 6.4-27 The specification and plans of the fuel containment system, including the insulation, are to be submitted for approval. The materials used are to be approved by LR.

6.4.13.2.1 Metallic materials used in the construction of primary and secondary barriers not forming the hull, shall be suitable for the design loads that they may be subjected to, and be in accordance with table 7.1, 7.2 or 7.3.

6.4.13.2.2 Materials, either non-metallic or metallic but not covered by tables 7.1, 7.2 and 7.3, used in the primary and secondary barriers may be approved by the Administration considering the design loads that they may be subjected to, their properties and their intended use.

6.4.13.2.3 Where non-metallic materials,^footnote including composites, are used for or incorporated in the primary or secondary barriers, they shall be tested for the following properties, as applicable, to ensure that they are adequate for the intended service:

.1 compatibility with the liquefied gas fuels;
.2 ageing;
.3 mechanical properties;
.4 thermal expansion and contraction;
.5 abrasion;
.6 cohesion;
.7 resistance to vibrations;
.8 resistance to fire and flame spread; and
.9 resistance to fatigue failure and crack propagation.

LR 6.4-28 Guidance on the use of non-metallic materials in the construction of primary and secondary barriers is provided in Appendix 4 of Rules for Ships for Liquefied Gases.

LR 6.4-29 Details of the extent of ageing of the insulation material used in the fuel containment system are to be submitted to LR for consideration.

6.4.13.2.4 The above properties, where applicable, shall be tested for the range between the expected maximum temperature in service and 5°C below the minimum design temperature, but not lower than minus196°C.

LR 6.4-30 In addition to the requirements given in 6.4.13.2.3, fatigue and crack propagation properties for insulation in membrane systems are also to be submitted. Insulation materials are to be approved by LR. Where applicable, these requirements also apply to any adhesive, sealers, vapour barriers, coatings or similar products used in the insulation system, any material used to give strength to the insulation system, components used to hold the insulation in place and any non-metallic membrane materials. Such products are to be compatible with the insulation.

6.4.13.2.5 Where non-metallic materials, including composites, are used for the primary and secondary barriers, the joining processes shall also be tested as described above.

6.4.13.2.6 Consideration may be given to the use of materials in the primary and secondary barrier, which are not resistant to fire and flame spread, provided they are protected by a suitable system such as a permanent inert gas environment, or are provided with a fire retardant barrier.

6.4.13.3 Thermal insulation and other materials used in liquefied gas fuel containment systems

6.4.13.3.1 Load-bearing thermal insulation and other materials used in liquefied gas fuel containment systems shall be suitable for the design loads.

6.4.13.3.2 Thermal insulation and other materials used in liquefied gas fuel containment systems shall have the following properties, as applicable, to ensure that they are adequate for the intended service:

.1 compatibility with the liquefied gas fuels;
.2 solubility in the liquefied gas fuel;
.3 absorption of the liquefied gas fuel;
.4 shrinkage;
.5 ageing;
.6 closed cell content;
.7 density;
.8 mechanical properties, to the extent that they are subjected to liquefied gas fuel and other loading effects, thermal expansion and contraction;
.9 abrasion;
.10 cohesion;
.11 thermal conductivity;
.12 resistance to vibrations;
.13 resistance to fire and flame spread; and
.14 resistance to fatigue failure and crack propagation.

6.4.13.3.3 The above properties, where applicable, shall be tested for the range between the expected maximum temperature in service and 5°C below the minimum design temperature, but not lower than minus 196°C.

6.4.13.3.4 Due to location or environmental conditions, thermal insulation materials shall have suitable properties of resistance to fire and flame spread and shall be adequately protected against penetration of water vapour and mechanical damage. Where the thermal insulation is located on or above the exposed deck, and in way of tank cover penetrations, it shall have suitable fire resistance properties in accordance with a recognized standard or be covered with a material having low flame spread characteristics and forming an efficient approved vapour seal.

6.4.13.3.5 Thermal insulation that does not meet recognized standards for fire resistance may be used in fuel storage hold spaces that are not kept permanently inerted, provided its surfaces are covered with material with low flame spread characteristics and that forms an efficient approved vapour seal.

6.4.13.3.6 Testing for thermal conductivity of thermal insulation shall be carried out on suitably aged samples.

LR 6.4-31 Proposals for the thermal conductivity tests of aged samples of the insulation are to be submitted by the designer and/or insulation makers, and are to be agreed with LR based on the physical and chemical characteristics of the insulation.

6.4.13.3.7 Where powder or granulated thermal insulation is used, measures shall be taken to reduce compaction in service and to maintain the required thermal conductivity and also prevent any undue increase of pressure on the liquefied gas fuel containment system.

LR 6.4-32 Particular attention is to be paid to the cleaning of the steelwork prior to the application of the insulation. Where insulation is to be foamed or sprayed in situ, the minimum steelwork temperature at the time of application is to be indicated in the specification in addition to environmental conditions.

6.4.14 Construction processes

LR 6.4-33 In addition to an inspection/survey plan as specified in 6.4.1.8 for the through life maintenance of the fuel containment system, a construction, testing and inspection (CTI) plan for the installation of the containment system is to be submitted for approval. This plan is to list the following sequentially for each stage of installation, testing and inspection:

(a) The method to be used;

(b) The acceptance criteria;

(c) The form of record to be made;

(d) The involvement of the shipyard, containment system designer where relevant, and LR Surveyor.

Further detailed documents, which may be cross-referenced by the CTI plan, are to be submitted for approval as applicable.

6.4.14.1 Weld joint design

LR 6.4-34 The requirements of this Section are to be applied in association with the relevant Chapters of the Rules for Ships. For welding joint details of pressure vessels, see Pt 5, Ch 10,14 of the Rules for Ships.

6.4.14.1.1 All welded joints of the shells of independent tanks shall be of the in-plane butt weld full penetration type. For dome-to-shell connections only, tee welds of the full penetration type may be used depending on the results of the tests carried out at the approval of the welding procedure. Except for small penetrations on domes, nozzle welds are also to be designed with full penetration.

LR 6.4-35 In the context of 6.4.14.1.1, small penetrations may generally be considered as penetrations of diameter not greater than 50 mm. Penetrations of diameter not greater than 150 mm may also be considered as being small, provided the service temperature is not lower than -110ºC, and the tank design pressure is not greater than 0,07MPa.

LR 6.4-36 In accordance with 6.4.14.1.1 full penetration T-butt welds may be used for dome-to-shell connections. Full penetration T-butt welds between shell and longitudinal bulkhead for bi-lobe tanks may also be accepted subject to agreement from the National Administration, see also 6.4.14.1.2.1.

6.4.14.1.2 Welding joint details for type C independent tanks, and for the liquid-tight primary barriers of type B independent tanks primarily constructed of curved surfaces, shall be as follows:

.1 All longitudinal and circumferential joints shall be of butt welded, full penetration, double vee or single vee type. Full penetration butt welds shall be obtained by double welding or by the use of backing rings. If used, backing rings shall be removed except from very small process pressure vessels.^footnote Other edge preparations may be permitted, depending on the results of the tests carried out at the approval of the welding procedure. For connections of tank shell to a longitudinal bulkhead of type C bilobe tanks, tee welds of the full penetration type may be accepted.
.2 The bevel preparation of the joints between the tank body and domes and between domes and relevant fittings shall be designed according to a standard acceptable to the Administration. All welds connecting nozzles, domes or other penetrations of the vessel and all welds connecting flanges to the vessel or nozzles shall be full penetration welds.

6.4.14.2 Design for gluing and other joining processes

6.4.14.2.1 The design of the joint to be glued (or joined by some other process except welding) shall take account of the strength characteristics of the joining process.

6.4.15 Tank types

6.4.15.1 Type A independent tanks

6.4.15.1.1 Design basis

6.4.15.1.1.1 Type A independent tanks are tanks primarily designed using classical ship-structural analysis procedures in accordance with the requirements of the Administration. Where such tanks are primarily constructed of plane surfaces, the design vapour pressure P₀ shall be less than 0.07 MPa.

6.4.15.1.1.2 A complete secondary barrier is required as defined in 6.4.3. The secondary barrier shall be designed in accordance with 6.4.4.

6.4.15.1.2 Structural analysis

6.4.15.1.2.1 A structural analysis shall be performed taking into account the internal pressure as indicated in 6.4.9.3.3.1, and the interaction loads with the supporting and keying system as well as a reasonable part of the ship's hull.

6.4.15.1.2.2 For parts, such as structure in way of supports, not otherwise covered by the regulations in this Code, stresses shall be determined by direct calculations, taking into account the loads referred to in 6.4.9.2 to 6.4.9.5 as far as applicable, and the ship deflection in way of supports.

LR 6.4-37 Symbols:

b	=	width of plating supported, in metres
f	=	but need not exceed 1,0
f_s	=	2,7 for nickel steels and carbon manganese steels
f_s	=	3,9 for austenitic steels and aluminium alloys
h	=	load head, in metres measured as follows: (a) for plating, the distance vertically from a point one-third of the height of the plate above its lower edge to the top of the tank (b) for stiffeners, the distance from the middle of the effective length to the top of the tank.
l	=	effective span or girder or web, in metres, see Pt 3, Ch 3,3.3
l_e	=	effective length of stiffening member, in metres, see Pt 3, Ch 3,3.3

l_t, l_s, l_b, l_c are effective spans measured according to Fig. LR 6.1

ρ	=	maximum density of the fuel, in kg/m³, at the design temperature
k	=	higher tensile steel factor, see Pt 3, Ch 2,1.2 of the Rules for Ships
t_p	=	thickness, in mm, of the attached load bearing plating. Where this varies over the effective width of plating, the mean thickness is to be used.
P	=	harbour relief valve pressure, in MPa
P_eq	=	the internal pressure head, in MPa, as derived from 6.4.9.3.3.1.4 and measured at a point on the plate one-third of the depth of the plate above its lower edge
s	=	spacing of bulkhead stiffeners, in mm
S	=	spacing of primary members, in metres

S_w and s1 are as defined in Pt 3, Ch 10, Table 10.5.1 of the Rules for Ships

The lateral and torsional stability of stiffeners is to comply with the requirements of Pt 4, Ch 9,5.6 of the Rules for Ships.

LR 6.4-38 The scantlings of the fuel tanks are to comply with the requirements of LR 6.4-39 and the following:

(a) Minimum thickness.

No part of the fuel tank structure is to be less than 7,5 mm in thickness.

(b) Boundary plating.

The thickness of plating forming the boundaries of fuel tanks is to be not less than 7,5 mm, nor less than:

NOTE
Additional corrosion allowance of 1 mm is to be added to the thickness derived if the fuel is of corrosive nature, see also 6.4.1.7.
where

(c) Rolled or built stiffeners.

The section modulus of rolled or built stiffeners on plating forming tank boundaries is to be not less than:

(d) Transverses.

The scantlings of transverse members are normally to be derived using direct calculation methods. The structural analysis is to take account of the internal pressure defined in 6.4.9.3.3.1.4 and also those resulting from structural test loading conditions. Proper account is also to be taken of structural model end constraints, shear and axial forces present and any interaction from the double bottom structure through the fuel tank supports. As an initial estimate the scantlings of the primary transverses may be taken as:

Top transverse
Topside transverse
Side transverse
Bottom transverse
Centreline bulkhead transverse

The depth of the bottom transverse web is generally to be not less than .

Web stiffening is to be in accordance with Pt 4, Ch 9,10.5 of the Rules for Ships with the application of the stiffening requirements as shown in Fig. LR 6.1.

(e) Tank end webs and girders.

The section modulus of vertical webs and horizontal girders is to be not less than:

(f) Internal bulkheads (Perforated).

The thickness of plating is to be not less than 7,5 mm, but may require to be increased at the tank boundaries in regions of high local loading. The section modulus of stiffeners, girders and webs is to be in accordance with Pt 4, Ch 9,8 and Ch 9,9.8 of the Rules for Ships.

(g) Internal bulkheads (Non-perforated).

(i) Where a bulkhead may be subjected to an internal pressure head, P_eq, resulting from loading on one side only, the scantlings of plating and stiffeners are to be determined from (b) and (c), see also (j).
(ii) Where no such loading condition is envisaged, and where the arrangement of the centreline bulkhead in way of the tank dome creates a common vapour space between the port and starboard sides of the tank, the scantlings may be derived as follows:
The thickness of plating and the section modulus of stiffeners are to be derived from (b) and (c) respectively, but P_eq (in MPa) need not exceed the greater of:
where
b_t = maximum breadth from centreline bulkhead to tank side
a_y = maximum dimensionless accelerations in transverse direction
In such instances, due consideration is to be given to the tank testing procedures and the Loading Manual is to include the following note:
‘Centreline bulkhead scantlings of fuel tanks are approved for symmetrical filling levels either side of the centreline bulkhead in sea-going conditions.’

(h) Tank crown structure.

Where the minimum thickness of tank boundary plating (7,5 mm) has been adopted, the section modulus of associated stiffeners and transverses are to be derived as above, but P_eq is to be not less than:

The tank crown plating and stiffeners are also to be suitable for a head equivalent to the greater of:

the harbour relief valve pressure; or
the tank test air pressure where the tank is to be hydropneumatically tested.

(i) Connection of stiffeners to primary supporting members.

In assessing the arrangement at intersections of continuous secondary and primary members, the requirements of Pt 3, Ch 10,5.2 are to be complied with using the requirements for other ship types. The total load, P, in kN, is to be derived using the internal pressure head, P_eq, in MPa as given in 6.4.9.3.3.1.4 and the following formulae:

(i) In general:
P = 1000 (S_w - 0,5s₁) s₁ P_eq kN
(ii) For wash bulkheads:
P = 1200 (S_w - 0,5s₁) s₁ P_eq kN

(j) Where the fuel tank boundary scantlings are based on the internal pressure head, Z_β, measured with respect to the non-perforated internal bulkhead such as centreline bulkhead, the valve(s) fitted in the bulkhead are to normally be kept closed and only be used for levelling operations. This is to be indicated in the operational manual required in 18.2.

6.4.15.1.2.3 The tanks with supports shall be designed for the accidental loads specified in 6.4.9.5. These loads need not be combined with each other or with environmental loads.

LR 6.4-39 In accordance with 6.4.15.1.2.3 tank boundaries and transverse wash bulkheads, where fitted, shall be able to withstand a collision force acting on the tank supports in the forward and aft directions without deformation likely to endanger the tank structure, see 6.4.9.5.1

Fig. LR 6.1 Measurement of spans

6.4.15.1.3 Ultimate design condition

6.4.15.1.3.1 For tanks primarily constructed of plane surfaces, the nominal membrane stresses for primary and secondary members (stiffeners, web frames, stringers, girders), when calculated by classical analysis procedures, shall not exceed the lower of R_m/2.66 or R_e/1.33 for nickel steels, carbon-manganese steels, austenitic steels and aluminium alloys, where R_m and R_e are defined in 6.4.12.1.1.3. However, if detailed calculations are carried out for the primary members, the equivalent stress σc, as defined in 6.4.12.1.1.4, may be increased over that indicated above to a stress acceptable to the Administration. Calculations shall take into account the effects of bending, shear, axial and torsional deformation as well as the hull/liquefied gas fuel tank interaction forces due to the deflection of the hull structure and liquefied gas fuel tank bottoms.

6.4.15.1.3.2 Tank boundary scantlings shall meet at least the requirements of the Administration for deep tanks taking into account the internal pressure as indicated in 6.4.9.3.3.1 and any corrosion allowance required by 6.4.1.7.

6.4.15.1.3.3 The liquefied gas fuel tank structure shall be reviewed against potential buckling.

6.4.15.1.4 Accidental design condition

6.4.15.1.4.1 The tanks and the tank supports shall be designed for the accidental loads and design conditions specified in 6.4.9.5 and 6.4.1.6.3 as relevant.

6.4.15.1.4.2 When subjected to the accidental loads specified in 6.4.9.5, the stress shall comply with the acceptance criteria specified in 6.4.15.1.3, modified as appropriate taking into account their lower probability of occurrence.

6.4.15.2 Type B independent tanks

6.4.15.2.1 Design basis

6.4.15.2.1.1 Type B independent tanks are tanks designed using model tests, refined analytical tools and analysis methods to determine stress levels, fatigue life and crack propagation characteristics. Where such tanks are primarily constructed of plane surfaces (prismatic tanks) the design vapour pressure P₀ shall be less than 0.07 MPa.

6.4.15.2.1.2 A partial secondary barrier with a protection system is required as defined in 6.4.3. The small leak protection system shall be designed according to 6.4.5.

6.4.15.2.2 Structural analysis

6.4.15.2.2.1 The effects of all dynamic and static loads shall be used to determine the suitability of the structure with respect to:

.1 plastic deformation;
.2 buckling;
.3 fatigue failure; and
.4 crack propagation.

Finite element analysis or similar methods and fracture mechanics analysis or an equivalent approach, shall be carried out.

6.4.15.2.2.2 A three-dimensional analysis shall be carried out to evaluate the stress levels, including interaction with the ship's hull. The model for this analysis shall include the liquefied gas fuel tank with its supporting and keying system, as well as a reasonable part of the hull.

6.4.15.2.2.3 A complete analysis of the particular ship accelerations and motions in irregular waves, and of the response of the ship and its liquefied gas fuel tanks to these forces and motions, shall be performed unless the data is available from similar ships.

6.4.15.2.3 Ultimate design condition

6.4.15.2.3.1 Plastic deformation

For type B independent tanks, primarily constructed of bodies of revolution, the allowable stresses shall not exceed:

σ_m ≤ f
σ_L ≤ 1.5f
σ_b ≤ 1.5F
σ_L + σ_b ≤ 1.5F
σ_m + σ_b ≤ 1.5F
σ_m + σ_b + σ_g ≤ 3.0F
σ_L + σ_b + σ_g ≤ 3.0F

where:

σ_m = equivalent primary general membrane stress;
σ_L = equivalent primary local membrane stress;
σ_b = equivalent primary bending stress;
σ_g = equivalent secondary stress;
f = the lesser of (Rm / A) or (Re / B); and
F = the lesser of (Rm / C) or (Re / D),

with R_mand R_e as defined in 6.4.12.1.1.3. With regard to the stresses σ_m, σ_{L ,} σ_g and σ_b see also the definition of stress categories in 6.4.15.2.3.6.

The values A and B shall have at least the following minimum values:

	Nickel steels and carbon manganese steels	Austenitic steel	Aluminium alloys
A	3	3.5	4
B	2	1.6	1.5
C	3	3	3
D	1.5	1.5	1.5

The above figures may be altered considering the design condition considered in acceptance with the Administration. For type B independent tanks, primarily constructed of plane surfaces, the allowable membrane equivalent stresses applied for finite element analysis shall not exceed:

.1 for nickel steels and carbon-manganese steels, the lesser of R_m/2 or R_e/1.2;
.2 for austenitic steels, the lesser of R_m/2.5 or R_e/1.2; and
.3 for aluminium alloys, the lesser of R_m/2.5 or R_e/1.2.

The above figures may be amended considering the locality of the stress, stress analysis methods and design condition considered in acceptance with the Administration.

The thickness of the skin plate and the size of the stiffener shall not be less than those required for type A independent tanks.

LR 6.4-40 Type B independent tanks constructed of bodies of revolution are to be designed to comply with the allowable stresses given in 6.4.15.2.3.1.

LR 6.4-41 The stress levels to be complied with for Type B independent tanks primarily constructed of plane surfaces will be specially considered.

LR 6.4-42 Type B independent tanks are to be subjected to a structural analysis by direct calculation procedures at a high confidence level. It is recommended that the assumptions made and the proposed calculation procedures be agreed with LR at an early stage. Where necessary, model or other tests may be required. Generally the scantlings of fuel tanks primarily constructed of plane surfaces are not to be less than required by LR 6.4-37 and LR 6.4-39 for Type A independent tanks.

6.4.15.2.3.2 Buckling

Buckling strength analyses of liquefied gas fuel tanks subject to external pressure and other loads causing compressive stresses shall be carried out in accordance with recognized standards. The method shall adequately account for the difference in theoretical and actual buckling stress as a result of plate edge misalignment, lack of straightness or flatness, ovality and deviation from true circular form over a specified arc or chord length, as applicable.

6.4.15.2.3.3 Fatigue design condition

6.4.15.2.3.3.1 Fatigue and crack propagation assessment shall be performed in accordance with the provisions of 6.4.12.2. The acceptance criteria shall comply with 6.4.12.2.7, 6.4.12.2.8 or 6.4.12.2.9, depending on the detectability of the defect.

6.4.15.2.3.3.2 Fatigue analysis shall consider construction tolerances.

6.4.15.2.3.3.3 Where deemed necessary by the Administration, model tests may be required to determine stress concentration factors and fatigue life of structural elements.

LR 6.4-43 Fatigue and crack propagation assessment shall be performed in accordance with 6.4.12.2. The acceptance criteria shall comply with 6.4.12.2.7, 6.4.12.2.8 or 6.4.12.2.9, depending on the detectability of the defect. Due consideration of quality control aspects such as misalignment, distortion, fit-up and weld shape are also to be taken into account. In general, and in addition to the C_w values dependent on detectability specified in 6.4.12.2.7, 6.4.12.2.8 and 6.4.12.2.9, a C_w value of 0,1 is to be used for all primary members. Alternative proposals will be specially considered.

6.4.15.2.3.4 Accidental design condition

6.4.15.2.3.4.1 The tanks and the tank supports shall be designed for the accidental loads and design conditions specified in 6.4.9.5 and 6.4.1.6.3, as relevant.

6.4.15.2.3.4.2 When subjected to the accidental loads specified in 6.4.9.5, the stress shall comply with the acceptance criteria specified in 6.4.15.2.3, modified as appropriate, taking into account their lower probability of occurrence.

6.4.15.2.3.5 Marking

Any marking of the pressure vessel shall be achieved by a method that does not cause unacceptable local stress raisers.

6.4.15.2.3.6 Stress categories

For the purpose of stress evaluation, stress categories are defined in this section as follows:

.1 Normal stress is the component of stress normal to the plane of reference.
.2 Membrane stress is the component of normal stress that is uniformly distributed and equal to the average value of the stress across the thickness of the section under consideration.
.3 Bending stress is the variable stress across the thickness of the section under consideration, after the subtraction of the membrane stress.
.4 Shear stress is the component of the stress acting in the plane of reference.
.5 Primary stress is a stress produced by the imposed loading, which is necessary to balance the external forces and moments. The basic characteristic of a primary stress is that it is not self-limiting. Primary stresses that considerably exceed the yield strength will result in failure or at least in gross deformations.
.6 Primary general membrane stress is a primary membrane stress that is so distributed in the structure that no redistribution of load occurs as a result of yielding.
.7 Primary local membrane stress arises where a membrane stress produced by pressure or other mechanical loading and associated with a primary or a discontinuity effect produces excessive distortion in the transfer of loads for other portions of the structure. Such a stress is classified as a primary local membrane stress, although it has some characteristics of a secondary stress. A stress region may be considered as local, if:
where:
- S₁ = distance in the meridional direction over which the equivalent stress exceeds 1.1f;
- S₂ = distance in the meridional direction to another region where the limits for primary general membrane stress are exceeded;
- R = mean radius of the vessel;
- t = wall thickness of the vessel at the location where the primary general membrane stress limit is exceeded; and
- f = allowable primary general membrane stress.
.8 Secondary stress is a normal stress or shear stress developed by constraints of adjacent parts or by self-constraint of a structure. The basic characteristic of a secondary stress is that it is self-limiting. Local yielding and minor distortions can satisfy the conditions that cause the stress to occur.

6.4.15.3 Type C independent tanks

6.4.15.3.1 Design basis

6.4.15.3.1.1 The design basis for type C independent tanks is based on pressure vessel criteria modified to include fracture mechanics and crack propagation criteria. The minimum design pressure defined in 6.4.15.3.1.2 is intended to ensure that the dynamic stress is sufficiently low so that an initial surface flaw will not propagate more than half the thickness of the shell during the lifetime of the tank.

6.4.15.3.1.2 The design vapour pressure shall not be less than:

P₀ = 0.2 + AC(ρ_r)^1.5 (MPa)

where:

with:
- σ_m = design primary membrane stress;
- Δσ_A= allowable dynamic membrane stress (double amplitude at probability level Q = 10^-8) and equal to:
  - - 55 N/mm² for ferritic-perlitic, martensitic and austenitic steel;
  - - 25 N/mm² for aluminium alloy (5083-O);
C = a characteristic tank dimension to be taken as the greatest of the following:
- h, 0.75b or 0.45ℓ,
with:
- h = height of tank (dimension in ship's vertical direction) (m);
- b = width of tank (dimension in ship's transverse direction) (m);
- ℓ = length of tank (dimension in ship's longitudinal direction) (m);
ρ_r = the relative density of the cargo (ρ_r = 1 for fresh water) at the design temperature.

LR 6.4-44 Alternative means of calculating the design vapour pressure referred to in 6.4.15.3.1.2 may be specially considered and are to be acceptable to the National Administration.

LR 6.4-45 Before construction of the pressure vessels is commenced, the following particulars, where applicable, and plans are to be submitted for approval:

(a) Nature of fuel, together with maximum vapour pressures and minimum liquid temperature for which the pressure vessels are to be approved, and proposed hydraulic test pressure.

(b) Particulars of materials proposed for the construction of the vessels.

(c) Particulars of refrigeration equipment.

(d) General arrangement plan showing location of pressure vessels in the ship.

(e) Plans of pressure vessels showing attachments, openings, dimensions, details of welded joints and particulars of proposed stress relief heat treatment.

(f) Plans of seatings, securing arrangements and deck sealing arrangements.

(g) Plans showing arrangement of mountings, level gauges and number, type and size of safety valves.

(h) In the case of vacuum insulated tanks, plans detailing the supports/mountings for anchoring and supporting the inner tank taking account of static and dynamic loads, thermal changes to inner tank and materials used.

6.4.15.3.2 Shell thickness

6.4.15.3.2.1 In considering the shell thickness the following apply:

.1 for pressure vessels, the thickness calculated according to 6.4.15.3.2.4 shall be considered as a minimum thickness after forming, without any negative tolerance;
.2 for pressure vessels, the minimum thickness of shell and heads including corrosion allowance, after forming, shall not be less than 5 mm for carbon manganese steels and nickel steels, 3 mm for austenitic steels or 7 mm for aluminium alloys; and
.3 the welded joint efficiency factor to be used in the calculation according to 6.4.15.3.2.4 shall be 0.95 when the inspection and the non-destructive testing referred to in 16.3.6.4 are carried out. This figure may be increased up to 1.0 when account is taken of other considerations, such as the material used, type of joints, welding procedure and type of loading. For process pressure vessels the Administration may accept partial non-destructive examinations, but not less than those of 16.3.6.4, depending on such factors as the material used, the design temperature, the nil ductility transition temperature of the material as fabricated and the type of joint and welding procedure, but in this case an efficiency factor of not more than 0.85 shall be adopted. For special materials the above-mentioned factors shall be reduced, depending on the specified mechanical properties of the welded joint.

6.4.15.3.2.2 The design liquid pressure defined in 6.4.9.3.3.1 shall be taken into account in the internal pressure calculations.

6.4.15.3.2.3 The design external pressure P_e, used for verifying the buckling of the pressure vessels, shall not be less than that given by:

P_e = P₁ + P₂ + P₃ + P₄ (MPa)

where:

P₁ = setting value of vacuum relief valves. For vessels not fitted with vacuum relief valves P₁shall be specially considered, but shall not in general be taken as less than 0.025 MPa.
P₂ = the set pressure of the pressure relief valves (PRVs) for completely closed spaces containing pressure vessels or parts of pressure vessels; elsewhere P₂= 0.
P₃ = compressive actions in or on the shell due to the weight and contraction of thermal insulation, weight of shell including corrosion allowance and other miscellaneous external pressure loads to which the pressure vessel may be subjected. These include, but are not limited to, weight of domes, weight of towers and piping, effect of product in the partially filled condition, accelerations and hull deflection. In addition, the local effect of external or internal pressures or both shall be taken into account.
P₄ = external pressure due to head of water for pressure vessels or part of pressure vessels on exposed decks; elsewhere P₄= 0.

6.4.15.3.2.4 Scantlings based on internal pressure shall be calculated as follows:

The thickness and form of pressure-containing parts of pressure vessels, under internal pressure, as defined in 6.4.9.3.3.1, including flanges, shall be determined. These calculations shall in all cases be based on accepted pressure vessel design theory. Openings in pressure-containing parts of pressure vessels shall be reinforced in accordance with a recognized standard acceptable to the Administration.

LR 6.4-46 The thickness of pressure parts subject to internal pressure is to be in accordance with Pt 5, Ch 11 of the Rules for Ships except that:

(a) the welded joint efficiency factor, J, is to be as defined in 6.4.15.3.2.1.3;

(b) the allowable stress is to be in accordance with 6.4.15.3.3.1;

(c) the corrosion allowance (c) included in the formulae in Pt 5, Ch 11,2 of the Rules for Ships may require to be increased in accordance with 6.4.1.7.

6.4.15.3.2.5 Stress analysis in respect of static and dynamic loads shall be performed as follows:

.1 pressure vessel scantlings shall be determined in accordance with 6.4.15.3.2.1 to 6.4.15.3.2.4 and 6.4.15.3.3;
.2 calculations of the loads and stresses in way of the supports and the shell attachment of the support shall be made. Loads referred to in 6.4.9.2 to 6.4.9.5 shall be used, as applicable. Stresses in way of the supports shall be to a recognized standard acceptable to the Administration. In special cases a fatigue analysis may be required by the Administration; and
.3 if required by the Administration, secondary stresses and thermal stresses shall be specially considered.

LR 6.4-47 Where the inner hull directly supports the containment system, it is to comply with the requirements of LR 3.18-02 of the Rules for Ships for Liquefied Gases.

6.4.15.3.3 Ultimate design condition

6.4.15.3.3.1 Plastic deformation

For type C independent tanks, the allowable stresses shall not exceed:

σ_m ≤ f
σ_L ≤ 1.5f
σ_b ≤ 1.5f
σ_L + σ_b ≤ 1.5f
σ_m + σ_b ≤ 1.5f
σ_m + σ_b + σ_g≤ 3.0f
σ_L + σ_b + σ_g≤ 3.0f

where:

σ_m= equivalent primary general membrane stress;
σ_L= equivalent primary local membrane stress;
σ_b= equivalent primary bending stress;
σ_g= equivalent secondary stress; and
f = the lesser of R_m/A or R_e/B,
with R_m and R_eas defined in 6.4.12.1.1.3. With regard to the stresses σ_m, σ_L,σ_gand σ_b see also the definition of stress categories in 6.4.15.2.3.6. The values A and B shall have at least the following minimum values:

	Nickel steels and carbon-manganese steels	Austenitic steels	Aluminium alloys
A	3	3.5	4
B	1.5	1.5	1.5

6.4.15.3.3.2 Buckling criteria shall be as follows:

The thickness and form of pressure vessels subject to external pressure and other loads causing compressive stresses shall be based on calculations using accepted pressure vessel buckling theory and shall adequately account for the difference in theoretical and actual buckling stress as a result of plate edge misalignment, ovality and deviation from true circular form over a specified arc or chord length.

6.4.15.3.4 Fatigue design condition

6.4.15.3.4.1 For type C independent tanks where the liquefied gas fuel at atmospheric pressure is below minus 55°C, the Administration may require additional verification to check their compliance with 6.4.15.3.1.1, regarding static and dynamic stress depending on the tank size, the configuration of the tank and arrangement of its supports and attachments.

6.4.15.3.4.2 For vacuum insulated tanks, special attention shall be made to the fatigue strength of the support design and special considerations shall also be made to the limited inspection possibilities between the inside and outer shell.

6.4.15.3.5 Accidental design condition

6.4.15.3.5.1 The tanks and the tank supports shall be designed for the accidental loads and design conditions specified in 6.4.9.5 and 6.4.1.6.3, as relevant.

6.4.15.3.5.2 When subjected to the accidental loads specified in 6.4.9.5, the stress shall comply with the acceptance criteria specified in 6.4.15.3.3.1, modified as appropriate taking into account their lower probability of occurrence.

6.4.15.3.6 Marking

The required marking of the pressure vessel shall be achieved by a method that does not cause unacceptable local stress raisers.

6.4.15.4 Membrane tanks

6.4.15.4.1 Design basis

6.4.15.4.1.1 The design basis for membrane containment systems is that thermal and other expansion or contraction is compensated for without undue risk of losing the tightness of the membrane.

6.4.15.4.1.2 A systematic approach, based on analysis and testing, shall be used to demonstrate that the system will provide its intended function in consideration of the identified in service events as specified in 6.4.15.4.2.1.

6.4.15.4.1.3 A complete secondary barrier is required as defined in 6.4.3. The secondary barrier shall be designed according to 6.4.4.

6.4.15.4.1.4 The design vapour pressure P₀ shall not normally exceed 0.025 MPa. If the hull scantlings are increased accordingly and consideration is given, where appropriate, to the strength of the supporting thermal insulation, P₀ may be increased to a higher value but less than 0.070 MPa.

6.4.15.4.1.5 The definition of membrane tanks does not exclude designs such as those in which non-metallic membranes are used or where membranes are included or incorporated into the thermal insulation.

6.4.15.4.1.6 The thickness of the membranes shall normally not exceed 10 mm.

6.4.15.4.1.7 The circulation of inert gas throughout the primary and the secondary insulation spaces, in accordance with 6.11.1 shall be sufficient to allow for effective means of gas detection.

6.4.15.4.2 Design considerations

6.4.15.4.2.1 Potential incidents that could lead to loss of fluid tightness over the life of the membranes shall be evaluated. These include, but are not limited to:

.1 Ultimate design events:
- .1 tensile failure of membranes;
- .2 compressive collapse of thermal insulation;
- .3 thermal ageing;
- .4 loss of attachment between thermal insulation and hull structure;
- .5 loss of attachment of membranes to thermal insulation system;
- .6 structural integrity of internal structures and their associated supporting structures; and
- .7 failure of the supporting hull structure.
.2 Fatigue design events:
- .1 fatigue of membranes including joints and attachments to hull structure;
- .2 fatigue cracking of thermal insulation;
- .3 fatigue of internal structures and their associated supporting structures; and
- .4 fatigue cracking of inner hull leading to ballast water ingress.
.3 Accident design events:
- .1 accidental mechanical damage (such as dropped objects inside the tank while in service);
- .2 accidental over pressurization of thermal insulation spaces;
- .3 accidental vacuum in the tank; and
- .4 water ingress through the inner hull structure.

Designs where a single internal event could cause simultaneous or cascading failure of both membranes are unacceptable.

6.4.15.4.2.2 The necessary physical properties (mechanical, thermal, chemical, etc.) of the materials used in the construction of the liquefied gas fuel containment system shall be established during the design development in accordance with 6.4.15.4.1.2.

6.4.15.4.3 Loads, load combinations

Particular consideration shall be paid to the possible loss of tank integrity due to either an overpressure in the interbarrier space, a possible vacuum in the liquefied gas fuel tank, the sloshing effects, to hull vibration effects, or any combination of these events.

6.4.15.4.4 Structural analyses

6.4.15.4.4.1 Structural analyses and/or testing for the purpose of determining the ultimate strength and fatigue assessments of the liquefied gas fuel containment and associated structures and equipment noted in 6.4.7 shall be performed. The structural analysis shall provide the data required to assess each failure mode that has been identified as critical for the liquefied gas fuel containment system.

6.4.15.4.4.2 Structural analyses of the hull shall take into account the internal pressure as indicated in 6.4.9.3.3.1. Special attention shall be paid to deflections of the hull and their compatibility with the membrane and associated thermal insulation.

6.4.15.4.4.3 The analyses referred to in 6.4.15.4.4.1 and 6.4.15.4.4.2 shall be based on the particular motions, accelerations and response of ships and liquefied gas fuel containment systems.

LR 6.4-48 The hull structure supporting the membrane tank is to be incorporated into the ship structure finite element model. The scantlings of the inner hull are to be not less than required by LR 3.21-04 of the Rules for Ships for Liquefied Gases, see also LR 3.22-01 of the Rules for Ships for Liquefied Gases.

6.4.15.4.5 Ultimate design condition

6.4.15.4.5.1 The structural resistance of every critical component, sub-system, or assembly, shall be established, in accordance with 6.4.15.4.1.2, for in-service conditions.

6.4.15.4.5.2 The choice of strength acceptance criteria for the failure modes of the liquefied gas fuel containment system, its attachments to the hull structure and internal tank structures, shall reflect the consequences associated with the considered mode of failure.

6.4.15.4.5.3 The inner hull scantlings shall meet the regulations for deep tanks, taking into account the internal pressure as indicated in 6.4.9.3.3.1 and the specified appropriate regulations for sloshing load as defined in 6.4.9.4.1.3.

6.4.15.4.6 Fatigue design condition

6.4.15.4.6.1 Fatigue analysis shall be carried out for structures inside the tank, i.e. pump towers, and for parts of membrane and pump tower attachments, where failure development cannot be reliably detected by continuous monitoring.

6.4.15.4.6.2 The fatigue calculations shall be carried out in accordance with 6.4.12.2, with relevant regulations depending on:

.1 the significance of the structural components with respect to structural integrity; and
.2 availability for inspection.

6.4.15.4.6.3 For structural elements for which it can be demonstrated by tests and/or analyses that a crack will not develop to cause simultaneous or cascading failure of both membranes, C_wshall be less than or equal to 0.5.

6.4.15.4.6.4 Structural elements subject to periodic inspection, and where an unattended fatigue crack can develop to cause simultaneous or cascading failure of both membranes, shall satisfy the fatigue and fracture mechanics regulations stated in 6.4.12.2.8.

6.4.15.4.6.5 Structural element not accessible for in-service inspection, and where a fatigue crack can develop without warning to cause simultaneous or cascading failure of both membranes, shall satisfy the fatigue and fracture mechanics regulations stated in 6.4.12.2.9.

LR 6.4-49 Containment system details to be investigated by fatigue analysis are to be submitted to LR for consideration, and it is recommended that this be done at as early a stage as possible.

6.4.15.4.7 Accidental design condition

6.4.15.4.7.1 The containment system and the supporting hull structure shall be designed for the accidental loads specified in 6.4.9.5. These loads need not be combined with each other or with environmental loads.

6.4.15.4.7.2 Additional relevant accidental scenarios shall be determined based on a risk analysis. Particular attention shall be paid to securing devices inside of tanks.

6.4.16 Limit state design for novel concepts

6.4.16.1 Fuel containment systems that are of a novel configuration that cannot be designed using section 6.4.15 shall be designed using this section and 6.4.1 to 6.4.14, as applicable. Fuel containment system design according to this section shall be based on the principles of limit state design which is an approach to structural design that can be applied to established design solutions as well as novel designs. This more generic approach maintains a level of safety similar to that achieved for known containment systems as designed using 6.4.15.

6.4.16.2 The limit state design is a systematic approach where each structural element is evaluated with respect to possible failure modes related to the design conditions identified in 6.4.1.6. A limit state can be defined as a condition beyond which the structure, or part of a structure, no longer satisfies the regulations.

6.4.16.3 For each failure mode, one or more limit states may be relevant. By consideration of all relevant limit states, the limit load for the structural element is found as the minimum limit load resulting from all the relevant limit states. The limit states are divided into the three following categories:

.1 Ultimate limit states (ULS), which correspond to the maximum load-carrying capacity or, in some cases, to the maximum applicable strain or deformation; under intact (undamaged) conditions.
.2 Fatigue limit states (FLS), which correspond to degradation due to the effect of time varying (cyclic) loading.
.3 Accident limit states (ALS), which concern the ability of the structure to resist accidental situations.

6.4.16.4 The procedure and relevant design parameters of the limit state design shall comply with the Standards for the Use of limit state methodologies in the design of fuel containment systems of novel configuration (LSD Standard), as set out in the annex to part A-1.

6.5 Regulations for portable liquefied gas fuel tanks

6.5.1 The design of the tank shall comply with 6.4.15.3. The tank support (container frame or truck chassis) shall be designed for the intended purpose.

6.5.2 Portable fuel tanks shall be located in dedicated areas fitted with:

.1 mechanical protection of the tanks depending on location and cargo operations;
.2 if located on open deck: spill protection and water spray systems for cooling; and
.3 if located in an enclosed space: the space is to be considered as a tank connection space.

6.5.3 Portable fuel tanks shall be secured to the deck while connected to the ship systems. The arrangement for supporting and fixing the tanks shall be designed for the maximum expected static and dynamic inclinations, as well as the maximum expected values of acceleration, taking into account the ship characteristics and the position of the tanks.

6.5.4 Consideration shall be given to the strength and the effect of the portable fuel tanks on the ship's stability.

6.5.5 Connections to the ship's fuel piping systems shall be made by means of approved flexible hoses or other suitable means designed to provide sufficient flexibility.

6.5.6 Arrangements shall be provided to limit the quantity of fuel spilled in case of inadvertent disconnection or rupture of the non-permanent connections.

6.5.7 The pressure relief system of portable tanks shall be connected to a fixed venting system.

6.5.8 Control and monitoring systems for portable fuel tanks shall be integrated in the ship's control and monitoring system. Safety system for portable fuel tanks shall be integrated in the ship's safety system (e.g. shutdown systems for tank valves, leak/gas detection systems).

6.5.9 Safe access to tank connections for the purpose of inspection and maintenance shall be ensured.

6.5.10 After connection to the ship's fuel piping system,

.1 with the exception of the pressure relief system in 6.5.6 each portable tank shall be capable of being isolated at any time;
.2 isolation of one tank shall not impair the availability of the remaining portable tanks; and
.3 the tank shall not exceed its filling limits as given in 6.8.

6.6 Regulations for CNG fuel containment

6.6.1 The storage tanks to be used for CNG shall be certified and approved by the Administration.

6.6.2 Tanks for CNG shall be fitted with pressure relief valves with a set point below the design pressure of the tank and with outlet located as required in 6.7.2.7 and 6.7.2.8.

6.6.3 Adequate means shall be provided to depressurize the tank in case of a fire which can affect the tank.

6.6.4 Storage of CNG in enclosed spaces is normally not acceptable, but may be permitted after special consideration and approval by the Administration provided the following is fulfilled in addition to 6.3.4 to 6.3.6:

.1 adequate means are provided to depressurize and inert the tank in case of a fire which can affect the tank;
.2 all surfaces within such enclosed spaces containing the CNG storage are provided with suitable thermal protection against any lost high-pressure gas and resulting condensation unless the bulkheads are designed for the lowest temperature that can arise from gas expansion leakage; and
.3 a fixed fire-extinguishing system is installed in the enclosed spaces containing the CNG storage. Special consideration should be given to the extinguishing of jet-fires.

6.7 Regulations for pressure relief system

6.7.1 General

6.7.1.1 All fuel storage tanks shall be provided with a pressure relief system appropriate to the design of the fuel containment system and the fuel being carried. Fuel storage hold spaces, interbarrier spaces, tank connection spaces and tank cofferdams, which may be subject to pressures beyond their design capabilities, shall also be provided with a suitable pressure relief system. Pressure control systems specified in 6.9 shall be independent of the pressure relief systems.

6.7.1.2 Fuel storage tanks which may be subject to external pressures above their design pressure shall be fitted with vacuum protection systems.

6.7.2 Pressure relief systems for liquefied gas fuel tanks

6.7.2.1 If fuel release into the vacuum space of a vacuum insulated tank cannot be excluded, the vacuum space shall be protected by a pressure relief device which shall be connected to a vent system if the tanks are located below deck. On open deck a direct release into the atmosphere may be accepted by the Administration for tanks not exceeding the size of a 40 ft container if the released gas cannot enter safe areas.

6.7.2.2 Liquefied gas fuel tanks shall be fitted with a minimum of 2 pressure relief valves (PRVs) allowing for disconnection of one PRV in case of malfunction or leakage.

6.7.2.3 Interbarrier spaces shall be provided with pressure relief devices.^footnote For membrane systems, the designer shall demonstrate adequate sizing of interbarrier space PRVs.

6.7.2.4 The setting of the PRVs shall not be higher than the vapour pressure that has been used in the design of the tank. Valves comprising not more than 50% of the total relieving capacity may be set at a pressure up to 5% above MARVS to allow sequential lifting, minimizing unnecessary release of vapour.

6.7.2.5 The following temperature regulations apply to PRVs fitted to pressure relief systems:

.1 PRVs on fuel tanks with a design temperature below 0°C shall be designed and arranged to prevent their becoming inoperative due to ice formation;
.2 the effects of ice formation due to ambient temperatures shall be considered in the construction and arrangement of PRVs;
.3 PRVs shall be constructed of materials with a melting point above 925°C. Lower melting point materials for internal parts and seals may be accepted provided that fail-safe operation of the PRV is not compromised; and
.4 sensing and exhaust lines on pilot operated relief valves shall be of suitably robust construction to prevent damage.

6.7.2.6 In the event of a failure of a fuel tank PRV a safe means of emergency isolation shall be available.

.1 procedures shall be provided and included in the operation manual (refer to chapter 18);
.2 the procedures shall allow only one of the installed PRVs for the liquefied gas fuel tanks to be isolated, physical interlocks shall be included to this effect; and
.3 isolation of the PRV shall be carried out under the supervision of the master. This action shall be recorded in the ship's log, and at the PRV.

6.7.2.7 Each pressure relief valve installed on a liquefied gas fuel tank shall be connected to a venting system, which shall be:

.1 so constructed that the discharge will be unimpeded and normally be directed vertically upwards at the exit;
.2 arranged to minimize the possibility of water or snow entering the vent system; and
.3 arranged such that the height of vent exits shall normally not be less than B/3 or 6 m, whichever is the greater, above the weather deck and 6 m above working areas and walkways. However, vent mast height could be limited to lower value according to special consideration by the Administration.

6.7.2.8 The outlet from the pressure relief valves shall normally be located at least 10 m from the nearest:

.1 air intake, air outlet or opening to accommodation, service and control spaces, or other non-hazardous area; and
.2 exhaust outlet from machinery installations.

6.7.2.9 All other fuel gas vent outlets shall also be arranged in accordance with 6.7.2.7 and 6.7.2.8. Means shall be provided to prevent liquid overflow from gas vent outlets, due to hydrostatic pressure from spaces to which they are connected.

6.7.2.10 In the vent piping system, means for draining liquid from places where it may accumulate shall be provided. The PRVs and piping shall be arranged so that liquid can, under no circumstances, accumulate in or near the PRVs.

6.7.2.11 Suitable protection screens of not more than 13 mm square mesh shall be fitted on vent outlets to prevent the ingress of foreign objects without adversely affecting the flow.

6.7.2.12 All vent piping shall be designed and arranged not to be damaged by the temperature variations to which it may be exposed, forces due to flow or the ship's motions.

6.7.2.13 PRVs shall be connected to the highest part of the fuel tank. PRVs shall be positioned on the fuel tank so that they will remain in the vapour phase at the filling limit (FL) as given in 6.8, under conditions of 15° list and 0.015L trim, where L is defined in 2.2.25.

LR 6.7-01 Pressure relief valves are also to remain operable with the ship flooded to a final athwartships inclination to a maximum angle of 30°.

6.7.3 Sizing of pressure relieving system

6.7.3.1 Sizing of pressure relief valves

6.7.3.1.1 PRVs shall have a combined relieving capacity for each liquefied gas fuel tank to discharge the greater of the following, with not more than a 20% rise in liquefied gas fuel tank pressure above the MARVS:

.1 the maximum capacity of the liquefied gas fuel tank inerting system if the maximum attainable working pressure of the liquefied gas fuel tank inerting system exceeds the MARVS of the liquefied gas fuel tanks; or
.2 vapours generated under fire exposure computed using the following formula:
- Q = FGA^0.82(m³/s)
- where:
- Q = minimum required rate of discharge of air at standard conditions of 273.15 Kelvin (K) and 0.1013 MPa.
- F = fire exposure factor for different liquefied gas fuel types:
  - F = 1.0 for tanks without insulation located on deck;
  - F = 0.5 for tanks above the deck when insulation is approved by the Administration. (Approval will be based on the use of a fireproofing material, the thermal conductance of insulation, and its stability under fire exposure);
  - F = 0.5 for uninsulated independent tanks installed in holds;
  - F = 0.2 for insulated independent tanks in holds (or uninsulated independent tanks in insulated holds);
  - F = 0.1 for insulated independent tanks in inerted holds (or uninsulated independent tanks in inerted, insulated holds); and
  - F = 0.1 for membrane tanks.
  - For independent tanks partly protruding through the weather decks, the fire exposure factor shall be determined on the basis of the surface areas above and below deck.
- G = gas factor according to formula:
  - where:
  - T = temperature in Kelvin at relieving conditions, i.e. 120% of the pressure at which the pressure relief valve is set;
  - L = latent heat of the material being vaporized at relieving conditions, in kJ/kg;
  - D = a constant based on relation of specific heats k and is calculated as follows:
    - where:
      - k = ratio of specific heats at relieving conditions, and the value of which is between 1.0 and 2.2. If k is not known, D = 0.606 shall be used;
  - Z = compressibility factor of the gas at relieving conditions; if not known, Z = 1.0 shall be used;
  - M = molecular mass of the product.
- The gas factor of each liquefied gas fuel to be carried is to be determined and the highest value shall be used for PRV sizing.
- A = external surface area of the tank (m²), as for different tank types, as shown in figure 6.7.1.

Figure 6.7.1

LR 6.7-01 Pressure relief valves are also to remain operable with the ship flooded to a final athwartships inclination to a maximum angle of 30°.

LR 6.7-02 For non-tapered prismatic tanks, L_min, is the smaller of the horizontal dimensions of the flat bottom of the tank. For tapered prismatic tanks, as would be used for the forward tank, L_min is the smaller of the length and the average width.

LR 6.7-03 For prismatic tanks whose distance between the flat bottom of the tank and bottom of the hold space is equal to or less than L_min/10:

A = external surface area minus flat bottom surface area.

LR 6.7-04 For prismatic tanks whose distance between the flat bottom of the tank and bottom of the hold space is greater than L_min/10:

A = external surface area.

6.7.3.1.2 For vacuum insulated tanks in fuel storage hold spaces and for tanks in fuel storage hold spaces separated from potential fire loads by coffer dams or surrounded by ship spaces with no fire load the following applies:

If the pressure relief valves have to be sized for fire loads the fire factors according may be reduced to the following values:
- F = 0.5 to F = 0.25
- F = 0.2 to F = 0.1
The minimum fire factor is F = 0.1

6.7.3.1.3 The required mass flow of air at relieving conditions is given by:

M_air = Q ^* ρ_air (kg/s)

where density of air (ρ_air) = 1.293 kg/m³ (air at 273.15 K, 0.1013 MPa).

6.7.3.2 Sizing of vent pipe system

6.7.3.2.1 Pressure losses upstream and downstream of the PRVs, shall be taken into account when determining their size to ensure the flow capacity required by 6.7.3.1.

6.7.3.2.2 Upstream pressure losses

.1 the pressure drop in the vent line from the tank to the PRV inlet shall not exceed 3% of the valve set pressure at the calculated flow rate, in accordance with 6.7.3.1;
.2 pilot-operated PRVs shall be unaffected by inlet pipe pressure losses when the pilot senses directly from the tank dome; and
.3 pressure losses in remotely sensed pilot lines shall be considered for flowing type pilots.

6.7.3.2.3 Downstream pressure losses

.1 Where common vent headers and vent masts are fitted, calculations shall include flow from all attached PRVs.
.2 The built-up back pressure in the vent piping from the PRV outlet to the location of discharge to the atmosphere, and including any vent pipe interconnections that join other tanks, shall not exceed the following values:
- .1 for unbalanced PRVs: 10% of MARVS;
- .2 for balanced PRVs: 30% of MARVS; and
- .3 for pilot operated PRVs: 50% of MARVS.
- Alternative values provided by the PRV manufacturer may be accepted.

6.7.3.2.4 To ensure stable PRV operation, the blow-down shall not be less than the sum of the inlet pressure loss and 0.02 MARVS at the rated capacity.

LR 6.7-05 The vent piping downstream of relief valves is to be designed and constructed taking into account potential two phase flow. Pressure drop calculations are to be undertaken in accordance with IMO Res. A829(19).

6.8 Regulations on loading limit for liquefied gas fuel tanks

6.8.1 Storage tanks for liquefied gas shall not be filled to more than a volume equivalent to 98% full at the reference temperature as defined in 2.2.36.

A loading limit curve for actual fuel loading temperatures shall be prepared from the following formula:

LL = FL ρ_R/ρ_L

where:

LL = loading limit as defined in 2.2.27, expressed in per cent;
FL = filling limit as defined in 2.2.16 expressed in per cent, here 98%;
ρ_R = relative density of fuel at the reference temperature; and
ρ_L = relative density of fuel at the loading temperature.

6.8.2 In cases where the tank insulation and tank location make the probability very small for the tank contents to be heated up due to an external fire, special considerations may be made to allow a higher loading limit than calculated using the reference temperature, but never above 95%. This also applies in cases where a second system for pressure maintenance is installed, (refer to 6.9). However, if the pressure can only be maintained / controlled by fuel consumers, the loading limit as calculated in 6.8.1 shall be used.

LR 6.8-01 The alternative loading limit option given under 6.8.2 is an alternative to 6.8.1 and shall only be applicable when the calculated loading limit using the formulae in 6.8.1 gives a lower value than 95 per cent.

6.9 Regulations for the maintaining of fuel storage condition

6.9.1 Control of tank pressure and temperature

6.9.1.1 With the exception of liquefied gas fuel tanks designed to withstand the full gauge vapour pressure of the fuel under conditions of the upper ambient design temperature, liquefied gas fuel tanks' pressure and temperature shall be maintained at all times within their design range by means acceptable to the Administration, e.g. by one of the following methods:

.1 reliquefaction of vapours;
.2 thermal oxidation of vapours;
.3 pressure accumulation; or
.4 liquefied gas fuel cooling.

The method chosen shall be capable of maintaining tank pressure below the set pressure of the tank pressure relief valves for a period of 15 days assuming full tank at normal service pressure and the ship in idle condition, i.e. only power for domestic load is generated.

LR 6.9-01 Liquefied gas fuel tank pressure and temperature shall be controlled and maintained within the design range at all times including after activation of the safety system required in 15.2.2 for a period of minimum 15 days. The activation of the safety system alone is not deemed as an emergency situation.

6.9.1.2 Venting of fuel vapour for control of the tank pressure is not acceptable except in emergency situations.

6.9.2 Design of systems

6.9.2.1 For worldwide service, the upper ambient design temperature shall be sea 32°C and air 45°C. For service in particularly hot or cold zones, these design temperatures shall be increased or decreased, to the satisfaction of the Administration.

6.9.2.2 The overall capacity of the system shall be such that it can control the pressure within the design conditions without venting to atmosphere.

6.9.3 Reliquefaction systems

6.9.3.1 The reliquefaction system shall be designed and calculated according to 6.9.3.2. The system has to be sized in a sufficient way also in case of no or low consumption.

6.9.3.2 The reliquefaction system shall be arranged in one of the following ways:

.1 a direct system where evaporated fuel is compressed, condensed and returned to the fuel tanks;
.2 an indirect system where fuel or evaporated fuel is cooled or condensed by refrigerant without being compressed;
.3 a combined system where evaporated fuel is compressed and condensed in a fuel/refrigerant heat exchanger and returned to the fuel tanks; or
.4 if the reliquefaction system produces a waste stream containing methane during pressure control operations within the design conditions, these waste gases shall, as far as reasonably practicable, be disposed of without venting to atmosphere.

LR 6.9-02 Cooling water return from heat exchangers which contain fuel are not to be led into the main machinery spaces.

6.9.4 Thermal oxidation systems

6.9.4.1 Thermal oxidation can be done by either consumption of the vapours according to the regulations for consumers described in this Code or in a dedicated gas combustion unit (GCU). It shall be demonstrated that the capacity of the oxidation system is sufficient to consume the required quantity of vapours. In this regard, periods of slow steaming and/or no consumption from propulsion or other services of the ship shall be considered.

6.9.5 Compatibility

6.9.5.1 Refrigerants or auxiliary agents used for refrigeration or cooling of fuel shall be compatible with the fuel they may come in contact with (not causing any hazardous reaction or excessively corrosive products). In addition, when several refrigerants or agents are used, these shall be compatible with each other.

6.9.6 Availability of systems

6.9.6.1 The availability of the system and its supporting auxiliary services shall be such that in case of a single failure (of mechanical non-static component or a component of the control systems) the fuel tank pressure and temperature can be maintained by another service/system.

6.9.6.2 Heat exchangers that are solely necessary for maintaining the pressure and temperature of the fuel tanks within their design ranges shall have a standby heat exchanger unless they have a capacity in excess of 25% of the largest required capacity for pressure control and they can be repaired on board without external sources.

LR 6.9-03 The largest required capacity for pressure control is to include additional capacity to account for any system inefficiencies expected in service and any additional capacity required to deal with variations in bunkering process conditions (e.g. temperature, pressure, flow rate, etc.).

6.10 Regulations on atmospheric control within the fuel containment system

6.10.1 A piping system shall be arranged to enable each fuel tank to be safely gas-freed, and to be safely filled with fuel from a gas-free condition. The system shall be arranged to minimize the possibility of pockets of gas or air remaining after changing the atmosphere.

6.10.2 The system shall be designed to eliminate the possibility of a flammable mixture existing in the fuel tank during any part of the atmosphere change operation by utilizing an inerting medium as an intermediate step.

6.10.3 Gas sampling points shall be provided for each fuel tank to monitor the progress of atmosphere change.

6.10.4 Inert gas utilized for gas freeing of fuel tanks may be provided externally to the ship.

6.11 Regulations on atmosphere control within fuel storage hold spaces (Fuel containment systems other than type C independent tanks)

6.11.1 Interbarrier and fuel storage hold spaces associated with liquefied gas fuel containment systems requiring full or partial secondary barriers shall be inerted with a suitable dry inert gas and kept inerted with make-up gas provided by a shipboard inert gas generation system, or by shipboard storage, which shall be sufficient for normal consumption for at least 30 days. Shorter periods may be considered by the Administration depending on the ship's service.

6.11.2 Alternatively, the spaces referred to in 6.11.1 requiring only a partial secondary barrier may be filled with dry air provided that the ship maintains a stored charge of inert gas or is fitted with an inert gas generation system sufficient to inert the largest of these spaces, and provided that the configuration of the spaces and the relevant vapour detection systems, together with the capability of the inerting arrangements, ensures that any leakage from the liquefied gas fuel tanks will be rapidly detected and inerting effected before a dangerous condition can develop. Equipment for the provision of sufficient dry air of suitable quality to satisfy the expected demand shall be provided.

6.12 Regulations on environmental control of spaces surrounding type C independent tanks

6.12.1 Spaces surrounding liquefied gas fuel tanks shall be filled with suitable dry air and be maintained in this condition with dry air provided by suitable air drying equipment. This is only applicable for liquefied gas fuel tanks where condensation and icing due to cold surfaces is an issue.

6.13 Regulations on inerting

6.13.1 Arrangements to prevent back-flow of fuel vapour into the inert gas system shall be provided as specified below.

6.13.2 To prevent the return of flammable gas to any non-hazardous spaces, the inert gas supply line shall be fitted with two shutoff valves in series with a venting valve in between (double block and bleed valves). In addition, a closable non-return valve shall be installed between the double block and bleed arrangement and the fuel system. These valves shall be located outside non-hazardous spaces.

6.13.3 Where the connections to the fuel piping systems are non-permanent, two non-return valves may be substituted for the valves required in 6.13.2.

6.13.4 The arrangements shall be such that each space being inerted can be isolated and the necessary controls and relief valves, etc. shall be provided for controlling pressure in these spaces.

6.13.5 Where insulation spaces are continually supplied with an inert gas as part of a leak detection system, means shall be provided to monitor the quantity of gas being supplied to individual spaces.

6.14 Regulations on inert gas production and storage on board

LR 6.14-01 The nitrogen generator, where fitted, is to be capable of delivering high purity nitrogen in accordance with Ch 15, 2.2.1.2.5 of the FSS Code, as amended by MSC. 367(93). In addition to Ch 15, 2.2.2.4 of the FSS Code, as amended by MSC. 367(93), the system is to be fitted with automatic means to discharge ‘off-spec’ gas to the atmosphere during start-up and abnormal operation.

LR 6.14-02 Inert gas systems are to be so designed as to minimise the risk of ignition from the generation of static electricity by the system itself.

6.14.1 The equipment shall be capable of producing inert gas with oxygen content at no time greater than 5% by volume. A continuous-reading oxygen content meter shall be fitted to the inert gas supply from the equipment and shall be fitted with an alarm set at a maximum of 5% oxygen content by volume.

6.14.2 An inert gas system shall have pressure controls and monitoring arrangements appropriate to the fuel containment system.

6.14.3 Where a nitrogen generator or nitrogen storage facilities are installed in a separate compartment outside of the engine-room, the separate compartment shall be fitted with an independent mechanical extraction ventilation system, providing a minimum of 6 air changes per hour. A low oxygen alarm shall be fitted.

6.14.4 Nitrogen pipes shall only be led through well ventilated spaces. Nitrogen pipes in enclosed spaces shall:

- be fully welded;
- have only a minimum of flange connections as needed for fitting of valves; and
- be as short as possible.