WO2013012318A1 - Répartiteur de charges, système sous-marin de levage et d'abaissement de charges et procédé de levage et d'abaissement de charges à partir d'un navire - Google Patents

Répartiteur de charges, système sous-marin de levage et d'abaissement de charges et procédé de levage et d'abaissement de charges à partir d'un navire Download PDF

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Publication number
WO2013012318A1
WO2013012318A1 PCT/NL2012/000053 NL2012000053W WO2013012318A1 WO 2013012318 A1 WO2013012318 A1 WO 2013012318A1 NL 2012000053 W NL2012000053 W NL 2012000053W WO 2013012318 A1 WO2013012318 A1 WO 2013012318A1
Authority
WO
WIPO (PCT)
Prior art keywords
load
spreader
piston
cable
cable connectors
Prior art date
Application number
PCT/NL2012/000053
Other languages
English (en)
Inventor
Joop Roodenburg
Terence Willem August Vehmeijer
Original Assignee
Itrec B.V.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Itrec B.V. filed Critical Itrec B.V.
Publication of WO2013012318A1 publication Critical patent/WO2013012318A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C13/00—Other constructional features or details
    • B66C13/04—Auxiliary devices for controlling movements of suspended loads, or preventing cable slack
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/18—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes specially adapted for use in particular purposes
    • B66C23/36—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes specially adapted for use in particular purposes mounted on road or rail vehicles; Manually-movable jib-cranes for use in workshops; Floating cranes
    • B66C23/52—Floating cranes

Definitions

  • the invention relates to a load spreader, to a marine load raising and lowering system for use on a vessel including such a load spreader, and to a method for raising and lowering a load from a vessel.
  • a marine load raising and lowering system is well-known, for example on vessels used for laying pipelines.
  • the system is then used in particular to abandon and recover a pipeline, which system and method are respectively referred to as an A&R system and an A&R method.
  • A&R method is carried out by connecting an A&R head to the end of the laid pipeline;
  • a marine load raising and lowering system may also be used to place other components on the bottom of the sea, e.g. a canister, manifold or any other kind of object.
  • US 7,182,550 discloses an A&R system and method using a single winch, suspension cable and associated driving means for lowering and raising the laid pipeline. The use of this system in deep water, e.g. several hundred metres or even more than one kilometre causes several problems.
  • the suspension cable associated with the winch must have a very high tensile strength to support a heavy load. This requirement leads to a heavy suspension cable with the result that the weight of the suspension cable itself becomes a further factor. Thus an even higher load capacity of the winch will be required.
  • a disadvantage of the system according to WO 2009/002142 is that especially for deep water purposes the load connector may rotate/twist about a vertical oriented axis, thereby entangling the two suspension cable portions.
  • each cable connector is configured to connect a respective suspension cable to the spreader
  • a load connector configured to connect a load to the spreader
  • a passive actuator system configured to move the two cable connectors between a first and second position
  • the passive actuator system is operable by water pressure, such that the spreader automatically moves the two cable connectors towards the second position when the spreader is lowered into a water body and moves the two cable connectors towards the first position when the spreader is raised.
  • An advantage of using this spreader is that by increasing the distance between the two cable connectors when the spreader is lowered into the water body, the chance of entanglement of the suspension cables connected to the two cable connectors is reduced and possibly prevented at all depending on the distance between the two cable connectors in the second position and the depth to which the load spreader is lowered.
  • Another advantage is that by using a passive actuator system that is operable by water pressure, no active components and complex control have to be used in order to obtain the same result. Using active components would require the use of umbilical lines to the load spreader which is a disadvantage especially for deepwater purposes.
  • the load spreader comprises a foldable mechanism to which the two cable connectors are mounted, said foldable mechanism having a collapsed state associated with the first position of the two cable connectors and an unfolded state associated with the second position of the two cable connectors, and wherein the passive actuator system is configured to move the two cable connectors between the first and second position by folding or unfolding of the foldable mechanism.
  • An advantage of the foldable mechanism may be that the space occupied by the load spreader in the collapsed state is much smaller than in the unfolded state so that above water, the spreader is easy to handle, may pass openings that can not be passed in the unfolded state and can be stored using minimal space.
  • the foldable mechanism is a bar linkage with at least four bars that are pivotable relative to each other by respective hinges.
  • the passive actuator system comprises a drive cylinder having:
  • a piston/piston rod assembly which can move axially back and forth, with a piston rod which protrudes outwards through an associated bore in the cylinder head and with a piston which is securely attached to one end of the piston rod and which is displaceable over an axial stroke between the cylinder bottom and the cylinder head;
  • the head-side chamber or the bottom-side chamber is filled with a compressible first medium that exerts a pressure on the piston that urges the piston/piston rod assembly towards a position associated with the first position of the two cable connectors, and wherein the pressure in the other one of the head-side chamber or the bottom-side chamber that urges the piston/piston rod assembly towards a position associated with the second position of the two cable connectors is determined by water pressure.
  • the water pressure may be directly applied to the piston, such that the other one of the head-side chamber or the bottom-side chamber is filled with water when the spreader submerges to exert a pressure on the piston that urges the piston/piston rod assembly towards a position associated with the second position of the two cable connectors.
  • the water pressure may be indirectly applied, for instance using an
  • the other one of the head-side chamber or the bottom-side chamber is in fluid communication with a bellow filled with a second medium, and wherein the bellow is collapsible so that the surrounding water pressure can be transmitted via the bellow and the second medium to the piston to urge the piston/piston rod assembly towards a position associated with the second position of the two cable connectors.
  • the passive actuator system comprises a buoyant member to provide a buoyancy force to the spreader when the spreader is lowered into the water body to move the cable connectors towards the second position.
  • the passive actuator comprises both a buoyant member and a drive cylinder as described above.
  • the buoyant member then provides a buoyancy force that is able to move the cable connectors partially towards the second position and the drive cylinder provides a further force depending on the depth to which the spreader is lowered to move the cable connectors further towards the second position.
  • the passive actuator system is configured as a bi-stable actuator system in which both the first and second position of the cable connectors correspond to a stable position of the actuator position, but wherein the actuator system jumps from the first position to the second position when a certain predetermined first depth is reached during lowering and jumps from the second position to the first position when a predetermined second depth is reached during raising of the spreader.
  • the first and second depth may be the same, but this is not necessary and the actuator system may have a hysteresis-like behavior.
  • the invention also relates to a marine load raising and lowering system for use on a vessel, preferably a vessel for laying an offshore pipeline, which system comprises:
  • a first winch comprising first driving means for raising or lowering a first suspension cable from the first winch;
  • a second winch comprising second driving means for raising or
  • system further comprises a tension equalizing mechanism adapted to equalize the tension in the first and second suspension cables.
  • the invention further relates to a method for raising and lowering a load from a vessel using a load connector that is suspended by two suspension cables, said method comprising the following steps:
  • the steps d) and f) are performed automatically as a result of changing water pressure.
  • the horizontal distance between the two suspension cables is increased and decreased at the location where the two suspension cables are directly or indirectly connected to the load connector.
  • Fig. 1 depicts a schematic view of a load spreader according to an embodiment of the invention
  • Fig. 2 depicts the load spreader of Fig. 1 in another position
  • Fig. 3 depicts a drive cylinder suitable for a passive actuator system of a load spreader according to the invention
  • Fig. 4 depicts a load spreader according to another embodiment of the invention in collapsed state
  • Fig. 5 depicts the load spreader of Fig. 4 in an unfolded state
  • Fig. 6A-6G depict in a simplified way the unfolding process of the load spreader of Fig. 4 and 5 from the position as shown in Fig. 4 to the position as shown in Fig. 5;
  • Fig. 7 depicts schematically a marine load raising and lowering system according to an embodiment of the invention.
  • FIG. 8 and 9 depict schematically a load spreader according to a further embodiment of the invention.
  • Figs. 1 and 2 schematically depict a load spreader CS according to an embodiment of the invention.
  • the load spreader CS comprises a load connector LC to connect a load LO to the spreader CS, in this case via a cable CA, and two cable connectors CC to respectively connect a first suspension cable SC1 and a second suspension cable SC2 to the load spreader CS.
  • the load spreader CS is further equipped with a passive actuator system, here indicated by arrow PAS, to move the cable connectors CC between a first position as shown in Fig. 1 to a second position as shown in Fig. 2.
  • a passive actuator system here indicated by arrow PAS
  • PAS passive actuator system
  • the horizontal distance between the two cable connectors CC is larger in the second position (see Fig. 2) than in the first position (see Fig. 1 ).
  • the distance between the first suspension cable SC1 and the second suspension cable SC2 increases when moving from the first position towards the second position, thereby reducing the chance of entanglement, i.e. twisting, of the two suspension cables SC1 , SC2.
  • the passive actuator system PAS is configured to be operable by water pressure, such that when the spreader is submerged under water and lowered, the increased water pressure moves the cable connectors automatically towards the second position so that with increased suspension cable length, the distance between the two suspension cables is increased as well.
  • the spreader is raised again, the opposite occurs, such that the decreased water pressure automatically results in movement of the cable connectors towards the first position until the spreader resurfaces.
  • the cable connectors CC are moveable along a beam BE which is configured to guide said movement, wherein the load connector LC is fixed to that beam BE.
  • the passive actuator system PAS may comprise a drive cylinder directly arranged between the two cable connectors CC.
  • the passive actuator system may comprise a drive cylinder per cable connector, wherein each drive cylinder is arranged between the respective cable connector and the beam BE.
  • An example of a suitable drive cylinder DC that is operable by water pressure is depicted in Fig. 3 in cross-sectional view.
  • the drive cylinder DC of Fig. 3 comprises a cylinder sleeve 100 with a cylinder bottom 101 and a cylinder head 103 arranged axially apart from each other.
  • a piston/piston rod assembly which can move axially back and forth, wherein the piston/piston rod assembly includes a piston rod 105 which protrudes outwards through an associated bore BO in the cylinder head 103 and with a piston 107 which is securely attached to one end of the piston rod 105 and which is displaceable over an axial stroke between the cylinder bottom 101 and the cylinder head 103.
  • a fluid seal 109 is provided on the piston 107 for providing a seal with an inner surface of the cylinder sleeve 100, so that the piston 107 delimits in the drive cylinder DC between the piston 107 and the cylinder head 103 a variable head-side chamber 111 and further delimits between the piston 107 and the cylinder bottom 101 a variable bottom-side chamber 113.
  • the head-side chamber 1 11 is a closed chamber filled with a compressible medium.
  • the head-side chamber 11 may be in fluid
  • the bottom-side chamber 113 is in fluid communication with the surroundings via openings 115 in the cylinder bottom 101.
  • the drive cylinder i.e. the load spreader
  • water is able to fill the bottom-side chamber 113 via the openings 115 (see arrows A1 ), so that the water pressure surrounding the drive cylinder can be applied to the piston 107 which urges the piston to move towards the cylinder head 103. This should correspond to movement of the cable connectors towards the second position.
  • the bottom-side chamber is filled with compressible medium and the head-side chamber is filled with water, so that consequently movement of the piston towards the cylinder head corresponds to movement towards the first position and movement of the piston towards the cylinder bottom corresponds to movement towards the second position.
  • the pressure inside the bottom-side chamber is induced by water pressure, but not directly.
  • the bottom-side chamber may be in fluid communication with a bellow instead of the surrounding, wherein the bellow and the bottom- side chamber are filled with a second medium.
  • the bellow is collapsible so that it is able to transmit the water pressure exerted on the bellow to the piston via the second medium in the bellow and the bottom-side chamber.
  • the drive cylinder is further provided with hinge connections HC to connect the drive cylinder to a cable connector and/or a beam BE as described with reference to Figs. 1 and 2.
  • Fig. 4 and 5 depict a load spreader CS according to another embodiment of the invention.
  • the load spreader CS comprises two cable connectors CC to connect the load spreader respectively to a first suspension cable SC1 and a second suspension cable SC2.
  • the load spreader CS further comprises a load connector LC to which a load can be connected.
  • the load connector LC and the cable connectors CC are hingably connected to a bar linkage via respectively hinges H1 , H2, and H3.
  • the bar linkage includes a load bar LB to which the load connector is attached, and four bars B1 -B4 which together with the load bar LB form a five-bar linkage.
  • the bars B1 and B2 are hingably mounted to the load bar LB via respectively hinges H4 and H5.
  • Bar B3 is hingably connected to bar B1 via hinge H6 and hingably connected to bar B4 via hinge H7.
  • Bar B4 in turn is hingeably connected to bar B2 via hinge H8.
  • the five bar linkage forms a foldable mechanism having a collapsed state as shown in Fig. 4 which is associated with a first position of the cable connectors CC. In the first position, the horizontal distance between the cable connectors is small such that the distance between the first and second suspension cables is small.
  • the foldable mechanism also has an unfolded state as shown in Fig. 5 which is associated with a second position of the cable connectors CC. In the second position, the horizontal distance between the cable
  • the distance between the first and second suspension cables in the second position is larger than in the first position, thereby reducing the risk of entanglement of the first and second suspension cables when lowering a load into a water body.
  • the load spreader comprises a passive actuator system including four drive cylinders DC. Two of the drive cylinders DC are arranged between bar B1 and bar B3. The other two drive cylinders DC are arranged between bar B2 and bar B4. As a result, the drive cylinders are able to actuate the five bar linkage to move between the collapsed state of Fig. 4 and the unfolded state of Fig. 5 as will be explained with reference to the Figs. 6A-6G.
  • Fig. 6A depicts the load spreader of Figs. 4 and 5 in a simplified way. For example, the suspension cables, load connector and drive cylinders are omitted to clearly depict the five bar linkage.
  • Fig. 6A depicts the five bar linkage in the collapsed state of Fig. 4. In this state, the drive cylinders are fully retracted and the bars B1-B4 are substantially parallel to each other, such that the width W of the five bar linkage is minimal. This state is also associated with the absence of any load to the load connector
  • the drive cylinders of the load spreader are in this embodiment of the type of Fig. 3.
  • the head-side chamber of each drive cylinder is filled with a compressible first medium under pressure that exerts a pressure on the piston urging the piston rod to retract inside the cylinder sleeve.
  • the drive cylinder will be in the retracted position as shown in Fig. 4 and corresponding to the state of Fig. 6A.
  • This water pressure in the drive cylinders will urge the piston to move towards the cylinder head and thus to further unfold the mechanism, e.g. towards a position as depicted in one of the Figs. 6D-6F.
  • a depth i.e. a water pressure
  • the position of Fig. 6G is reached and no further movement is possible upon further lowering the spreader.
  • An advantage of a spreader according to this embodiment is that when the spreader is in the collapsed state, the width W is small and the spreader is able to pass small openings compared to the size of an opening required if the spreader has to pass in the unfolded state.
  • Fig. 7 schematically depicts a marine load raising and lowering system 1 for use on a vessel, preferably a vessel for laying an offshore pipeline, which system comprises a first winch 2 with first driving means 3 for raising and lowering a first suspension cable SC1 from the first winch 2, and a second winch 5 with second driving means 6 for raising and lowering a second suspension cable SC2 from the second winch 5.
  • the first and second driving means 3, 6 can be synchronized by operating means 8 connected to the first and second driving means so as to perform synchronous raising and lowering of the first and second
  • the operating means are in this embodiment electronic operating means.
  • the first and second suspension cable SC1 , SC2 will in practice be very long, but represented here short for reasons of clarity.
  • the first and second driving means are electronically and/or mechanically connected to the respective first and second winch 2,5.
  • the driving means may include any type of motor.
  • the first suspension cable SC1 is suspended via a sheave 9 from the first winch 2.
  • the second suspension cable SC2 is suspended via a sheave 10'from the second winch 5.
  • the first and second suspension cable SC1 , SC2 are connected to a load spreader CS according to the invention with a respective terminal end 4c, 7c of the first and second suspension cable SC1 , SC2.
  • the load spreader CS comprises a load connector which is or can be coupled to a load 12.
  • the load spreader is able to vary the distance between the terminal ends 4c, 7c of the first and second suspension cable thereby enabling a large distance when the load is lowered into a water body to minimize or prevent entanglement of the first and second suspension cable.
  • the load spreader may be of one of the types as shown with reference to the Figs. 1-6G.
  • a first tension equalizing mechanism 13 is provided through which the first and second suspension cable SC1 , SC2 pass.
  • the first tension equalizing mechanism is not shown in detail in Fig. 1 , but ensures that the load is suspended by both the first and second suspension cable and no overload in one of the suspension cables occurs due to e.g. non-synchronous lowering or raising of the cables.
  • Fig. 8 and 9 depict a load spreader CS according to another embodiment of the invention, wherein said load spreader includes a four bar linkage with four bars B1-B4.
  • the four bar linkage forms a foldable mechanism having a collapsed state as shown in Fig. 8 and an unfolded state as shown in Fig. 9.
  • the four bars are linked together via respective hinges H10-H13.
  • a load connector is provided at hinge H10 and two cable connectors are provided at hinges H11 and H13 respectively to connect a first and second suspension cable SC1 , SC2 to the spreader.
  • the load spreader further comprises a passive actuator system comprising springs SP that urge the mechanism towards its collapsed state and a buoyant member BM that urges the mechanism towards its unfolded state when the spreader including buoyant member are lowered into the water.
  • a passive actuator system comprising springs SP that urge the mechanism towards its collapsed state and a buoyant member BM that urges the mechanism towards its unfolded state when the spreader including buoyant member are lowered into the water.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Load-Engaging Elements For Cranes (AREA)

Abstract

L'invention concerne un répartiteur de charges comprenant : - deux connecteurs de câble conçus chacun pour connecter un câble de suspension respectif à un répartiteur de charges ; - un connecteur de charge conçu pour connecter une charge au répartiteur de charges ; et - un système d'actionnement passif conçu pour déplacer les deux connecteurs de câble entre une première et une seconde position, dans lesquelles en cours d'utilisation la distance horizontale entre les deux connecteurs de câble est plus importante dans la seconde position que dans la première position. Le système d'actionnement passif est activé par la pression de l'eau de telle sorte que le répartiteur de charges déplace automatiquement les deux connecteurs de câble vers la seconde position lorsqu'il est abaissé dans la masse d'eau, et les déplace vers la première position lorsqu'il est levé. L'invention concerne également un système sous-marin de levage et d'abaissement de charges comprenant le répartiteur de charges, et un procédé de levage et d'abaissement de charges dans une masse d'eau.
PCT/NL2012/000053 2011-07-18 2012-07-17 Répartiteur de charges, système sous-marin de levage et d'abaissement de charges et procédé de levage et d'abaissement de charges à partir d'un navire WO2013012318A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NL2007131 2011-07-18
NL2007131A NL2007131C2 (en) 2011-07-18 2011-07-18 A load spreader, marine load raising and lowering system and a method for raising and lowering a load from a vessel

Publications (1)

Publication Number Publication Date
WO2013012318A1 true WO2013012318A1 (fr) 2013-01-24

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PCT/NL2012/000053 WO2013012318A1 (fr) 2011-07-18 2012-07-17 Répartiteur de charges, système sous-marin de levage et d'abaissement de charges et procédé de levage et d'abaissement de charges à partir d'un navire

Country Status (2)

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NL (1) NL2007131C2 (fr)
WO (1) WO2013012318A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5951227A (en) * 1998-07-28 1999-09-14 J. Ray Mcdermott, S.A. Deep water lowering apparatus
JP2003246582A (ja) * 2002-02-20 2003-09-02 Ishikawajima Harima Heavy Ind Co Ltd 吊具振れ止め装置
US20050265788A1 (en) * 2004-05-26 2005-12-01 Heerema Marine Contractors Nederland B.V. Abandonment and recovery head apparatus
WO2006013053A1 (fr) * 2004-08-02 2006-02-09 Terex-Demag Gmbh & Co. Kg Mecanisme de commande de cable de levage comprenant un bloc a tenon inferieur unique et deux treuils
EP2008959A1 (fr) * 2007-06-27 2008-12-31 Kalmar Industries B.V. Cadre de levage et grue à conteneur comprenant un tel cadre de levage.
WO2009002142A1 (fr) 2007-06-22 2008-12-31 Itrec B.V. Système de levage et d'abaissement de charges marines
JP2009085966A (ja) * 2008-12-01 2009-04-23 Mitsubishi Heavy Ind Ltd 放射性廃棄物収納容器の把持装置

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5951227A (en) * 1998-07-28 1999-09-14 J. Ray Mcdermott, S.A. Deep water lowering apparatus
JP2003246582A (ja) * 2002-02-20 2003-09-02 Ishikawajima Harima Heavy Ind Co Ltd 吊具振れ止め装置
US20050265788A1 (en) * 2004-05-26 2005-12-01 Heerema Marine Contractors Nederland B.V. Abandonment and recovery head apparatus
US7182550B2 (en) 2004-05-26 2007-02-27 Heerema Marine Contractors Nederland B.V. Abandonment and recovery head apparatus
WO2006013053A1 (fr) * 2004-08-02 2006-02-09 Terex-Demag Gmbh & Co. Kg Mecanisme de commande de cable de levage comprenant un bloc a tenon inferieur unique et deux treuils
WO2009002142A1 (fr) 2007-06-22 2008-12-31 Itrec B.V. Système de levage et d'abaissement de charges marines
EP2008959A1 (fr) * 2007-06-27 2008-12-31 Kalmar Industries B.V. Cadre de levage et grue à conteneur comprenant un tel cadre de levage.
JP2009085966A (ja) * 2008-12-01 2009-04-23 Mitsubishi Heavy Ind Ltd 放射性廃棄物収納容器の把持装置

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