HEAVY LIFT CRANE

Abstract

A crane for use on an offshore vessel is provided with a boom restrainer, wherein the boom restrainer is a hydro-pneumatic boom restrainer, for reducing upward pivoting of the boom, when the boom is in the top zone, wherein the boom restrainer includes: multiple hydraulic cylinders, each having a hydraulic circuit and a cylinder rod with a cylinder head, wherein the cylinders are mounted on the crane structure with the cylinder heads directed towards the boom of the crane, preferably are mounted on a stay of the crane structure, a catcher for each hydraulic cylinder, wherein each catcher is mounted on the boom and is configured for receiving the cylinder head of the corresponding hydraulic cylinder, and to lock the cylinder head, preferably pivotable locks the cylinder head, relative to the boom, when the boom pivots upwards in the top zone; a gas buffer for each hydraulic cylinder, wherein each gas buffer is mounted to the corresponding hydraulic cylinder, and is connected to the hydraulic circuit of the corresponding hydraulic cylinder via a medium separator, wherein the gas buffer forces the hydraulic cylinder in an extended position, and wherein the volume ratio between the hydraulic cylinder and the gas buffer is such that the hydraulic cylinder acts as a progressive spring, e.g. the gas buffers each have a size in the range of 1000-1400 litre, for example 1200 litre and the hydraulic cylinders each have a size in the range of 800-1000 litre, for example 900 litre, and preferably the ratio between the volume of the gas buffer and the volume of the associated hydraulic cylinder is 4:3.

Claims

1.-29. (canceled)

30. A heavy lift crane for use on a vessel, the crane comprising: a base structure, wherein the base structure is adapted to be mounted to, or formed integral with, the vessel; a crane structure, wherein the crane structure is rotationally supported by the base structure for rotation of the crane structure relative to the base structure about a vertical rotation axis; a boom, wherein the boom comprises a longitudinal axis, a pivot end, a mid-section, and a hoisting end opposite the pivot end, wherein the boom is supported by the crane structure, so that the boom can rotate about the vertical rotation axis, and wherein the pivot end of the boom is pivotably connected to the crane structure, so that the boom can pivot up and down about a horizontal boom pivot axis; a boom luffing assembly, wherein the luffing assembly comprises a boom luffing wire and a boom luffing winch, wherein the boom luffing wire extends from the boom luffing winch to the hoisting end of the boom, for pivoting the boom upward and downward about the boom pivot axis, and for supporting the boom in a hoisting position relative to the crane structure, wherein the luffing assembly can pivot the boom into a top zone; a hoisting assembly for hoisting a load, wherein the hoisting assembly comprises a hoisting winch, a hoisting wire, and a load suspension device, wherein the hoisting wire extends from the hoisting winch via a hoisting wire guide, located at the hoisting end of the of the boom, to the load suspension device; and a hydro-pneumatic boom restrainer, for reducing upward pivoting of the boom, when the boom is in the top zone, wherein the boom restrainer comprises: multiple hydraulic cylinders, each having a hydraulic circuit and a cylinder rod with a cylinder head, wherein the hydraulic cylinders are mounted on the crane structure with the cylinder heads directed towards the boom of the crane; a catcher for each hydraulic cylinder, wherein each catcher is mounted on the boom and is configured for receiving the cylinder head of the corresponding hydraulic cylinder, and to lock the cylinder head relative to the boom, when the boom pivots upwards in the top zone; a gas buffer for each hydraulic cylinder, wherein each gas buffer is mounted to the corresponding hydraulic cylinder, and is connected to the hydraulic circuit of the corresponding hydraulic cylinder via a medium separator, wherein the gas buffer forces the hydraulic cylinder in an extended position, and wherein the volume ratio between the hydraulic cylinder and the gas buffer is such that the hydraulic cylinder acts as a progressive spring; and a control system; comprising one or more sensors to monitor loss of a load, wherein the boom restrainer can be switched between a passive modus, in which the boom restrainer allows for movement of the cylinder rods in the respective hydraulic cylinders, and thus allows for movement of the boom relative to the crane structure or the mast of the crane in the top zone, and an active modus, in which the boom retainer slows down and blocks movement of the cylinder rods in the respective hydraulic cylinders, and thus slows down and blocks movement of the boom relative to the crane structure or the mast of the crane in the top zone, and wherein the control system is configured to switch the boom restrainer from the passive modus into the active modus when the one or more sensors register a loss of load and/or roll of the vessel.

31. The heavy lift crane according to claim 30, wherein in the top zone the angle of the boom with the vertical rotation axis of the crane is in the range of 0-30 degrees, and wherein the boom of the crane can be pivoted in a working zone, wherein in the working zone the angle of the boom with the vertical rotation axis of the crane is between 20 degrees and 100 degrees, and wherein the top zone overlaps with the working zone.

32. The heavy lift crane according to claim 30, further comprising a boom stop, wherein the boom stop is configured to block movement of the boom at a safety angle, the safety angle being the maximum height wherein the boom can be pivoted, and wherein the boom stop comprises a crush zone, configured to slow down and stop a boom by controlled deformation.

33. The heavy lift crane according to claim 32, wherein the boom stop comprises a bumper that engages the boom prior to the boom reaching a maximum working angle, to resiliently receive the boom and prevent the boom from coming to a hard stop against the boom stop.

34. The heavy lift crane according to claim 33, wherein the boom stop comprises sensors that are linked to the control system, and wherein the control system is configured to block the luffing system from further lifting the boom, thus preventing the luffing system from pivoting the boom beyond the maximum working angle.

35. The heavy lift crane according to claim 30, wherein the boom restrainer is configured to keep the cylinder at a minimum pressure, at least when the boom is in contact with the boom restrainer, such that the restrainer keeps contact with the boom when the boom suddenly pivots in the downward direction.

36. The heavy lift crane according to claim 30, wherein the boom restrainer comprises a crush zone, configured to slow down and stop a boom by controlled deformation, when the boom moves above a maximum pivot speed

37. The heavy lift crane according to claim 30, wherein the hydraulic circuits of the multiple hydraulic cylinders are coupled, to equalize load differences between the hydraulic cylinders.

38. The heavy lift crane according to claim 30, wherein the hydraulic cylinders are compressed when the boom is pivoted upwards in the top zone, and the hydraulic cylinders tension the luffing wires.

39. The heavy lift crane according to claim 30, wherein the cylinder rods of the boom restrainer are fully extended when they engage the boom and the boom is at an angle of 35 degrees with the vertical rotation axis.

40. The heavy lift crane according to claim 30, wherein the cylinder rods of the boom restrainer are fully retracted when the boom is at an angle of 15 degrees with the vertical rotation axis.

41. The heavy lift crane according to claim 30, wherein the boom is an A-frame boom, and the boom restrainer comprises four hydraulic cylinders that are mounted such that each of the four hydraulic cylinders engages a side of a leg of the A-frame.

42. The heavy lift crane according to claim 30, wherein the boom at the base end comprises a box frame, and the catchers for the hydraulic cylinders are mounted on the box frame.

43. The heavy lift crane according to claim 30, wherein the hydraulic cylinders are pivotable supported, such that the hydraulic cylinders can pivot about a horizontal axis relative to the crane structure

44. The heavy lift crane according to claim 30, wherein the stay is an A-frame, and two hydraulic cylinders are mounted on each leg of the A frame.

45. The heavy lift crane according to claim 30, wherein the catchers comprise a guide surface and a blocking surface, and wherein the guide surface engages the cylinder head when the boom pivots towards the top zone, and guides the cylinder head towards the blocking surface while the boom pivots further towards the top zone, and wherein the blocking surface is provided at an end of the guide surface to lock the cylinder head relative to the boom, such that further moment of the boom pushes the rod into the cylinder.

46. The heavy lift crane according to claim 30, wherein the control system comprises sensors for monitoring the angle of the boom, and/or that can detect if the boom is within the top zone or not.

47. An offshore crane vessel comprising the heavy lift crane according to claim 30.

48. A hydro-pneumatic boom restrainer configured to be mounted on a heavy lift crane to provide the heavy lift crane according to claim 30.

49. A method for stopping the upwards pivot movement of a boom, the boom moving in the top zone, using the heavy lift crane according to claim 30, wherein the method comprises the steps: raising the boom into the top zone and engaging the boom with the boom restrainer; lifting a load with the crane; detecting a loss of load; switching the boom restrainer from the passive modus into the active modus; slowing down movement of the cylinder rods in the respective hydraulic cylinders, and thus slowing down movement of the boom relative to the crane structure or the mast of the crane; and stopping movement of the cylinder rods in the respective hydraulic cylinders, and thus stopping movement of the boom, relative to the crane structure or the mast of the crane.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0195] In the Drawings

[0196] FIG. 1 shows a first exemplary embodiment of a heavy lift crane according to a second aspect of the invention in side view, wherein the crane is depicted with a boom in a lowered position and in a raised position;

[0197] FIG. 2 shows the heavy lift crane of FIG. 1 in side view, wherein the crane is depicted with the boom in the lowered position, in the raised position, and two intermediate positions;

[0198] FIG. 3 shows the heavy lift crane of FIG. 1 in partial close up in side view, wherein the crane is depicted with the boom in the lowered position, and in an intermediate position;

[0199] FIG. 4 shows the heavy lift crane of FIG. 1 in a partial close up in top view, wherein the crane is depicted with the boom in the lowered position, and in an intermediate position;

[0200] FIG. 5 shows a hydraulic schedule;

[0201] FIG. 6 shows a second exemplary embodiment of a heavy lift crane according to the invention in side view, wherein the crane is depicted with a boom in a lowered position and in a raised position;

[0202] FIG. 7 shows a third exemplary embodiment of a heavy lift crane according to the invention in side view, wherein the crane is depicted with a boom in a lowered position and in a raised position;

[0203] FIG. 8 shows a partial view in cross section of a vessel according to a third aspect of the invention, wherein the vessel is provided with a floating body on a side opposite a side where a crane is provided on the vessel;

[0204] FIG. 9 shows a partial view in cross section of the vessel of FIG. 8 in a level and in a tilted position, wherein the vessel is provided with a raised floating body on a side opposite a side where a crane is provided on the vessel;

[0205] FIG. 10 shows a partial view in cross section of the vessel of FIG. 8 in a level and in a tilted position, wherein the vessel is provided with an alternative raised floating body on a side opposite a side where a crane (not shown) is provided on the vessel;

[0206] FIG. 11 shows a partial view in cross section of the vessel of FIG. 8 in a level and in a tilted position, wherein the vessel is provided with a partially raised floating body on a side opposite a side where a crane (not shown) is provided on the vessel;

[0207] FIG. 12. shows a partial view in cross section of the vessel of FIG. 8 in a level and in a tilted position, wherein the vessel is provided with a partially raised floating body on a side opposite a side where a crane (not shown) is provided on the vessel;

[0208] FIG. 13 shows an exemplary embodiment of a heavy lift crane according to a fourth aspect of the invention in side view, wherein the crane comprises a boom provided with a strut on a hoisting side of the boom;

[0209] FIG. 14 shows an exemplary embodiment of a vessel in a partial view in cross section according to a fifth aspect of the invention, wherein the vessel is provided with a mobile ballast system;

[0210] FIG. 15 shows another exemplary embodiment of a vessel in a partial view in cross section according to a fifth aspect of the invention, wherein the vessel is provided with a mobile ballast system;

[0211] FIG. 16 shows another exemplary embodiment of a vessel in a partial view in cross section according to a sixth aspect of the invention, wherein the vessel is provided with retractable stabilising fins for use during hoisting activities;

[0212] FIG. 17 show a top vie, a side view and a view in cross section of the vessel of FIG. 12, wherein the view in cross section shows the hull of the vessel also in a tilted position in dotted lines;

[0213] FIG. 18 shows an exemplary embodiment of a heavy lift crane according to a first aspect of the invention in side view, wherein the crane is depicted with a boom positioned at a lower end of a working zone;

[0214] FIG. 19 shows the heavy lift crane of FIG. 18 with the boom positioned at an upper end of the working zone;

[0215] FIG. 20 shows in close up a hydro-pneumatic boom restrainer of the heavy lift crane of FIG. 18, with the hydro pneumatic boom restrainer not yet engaging the boom of the heavy lift crane;

[0216] FIG. 21 shows in close up the hydro-pneumatic boom restrainer of the heavy lift crane of FIG. 18, with the boom at the lower end of the top zone and the hydro pneumatic boom restrainer engaging the boom of the heavy lift crane; and

[0217] FIG. 22 shows in close up the hydro-pneumatic boom restrainer of the heavy lift crane of FIG. 18, with the boom at the upper end of the top zone and the hydro pneumatic boom restrainer engaging the boom of the heavy lift crane.

[0218] FIG. 1 shows a first exemplary embodiment of a heavy lift crane 1 according to a second aspect of the invention in side view, wherein the crane 1 is depicted with a boom 4 in a lowered position and in a raised position.

[0219] According to the invention, the heavy lift crane comprises a base structure 3, a crane structure 4, a boom 5, a boom luffing assembly 6, a hoisting assembly 7, a boom restrainer 8 and a control system 9. In the embodiment shown, the crane is furthermore provided with a boom stop 23.

[0220] In the embodiment shown, the heavy lift crane 1 is a mast crane, and the base structure 3 is embodied as a mast 2 the mast is adapted to be mounted to a vessel.

[0221] The crane structure 4 comprises a crane housing. The crane structure 4 is rotationally supported by the base structure, in this embodiment the mast 2 of the crane, for rotation of the crane structure relative to the base about a vertical rotation axis 15. Thus, the vertical rotation axis of the crane coincides with the vertical axis of the mast of the crane.

[0222] In the embodiment shown, the boom 5 has a length of about 120 meters. The boom 5 comprises a longitudinal axis 11, a pivot end 12, a mid-section 13, and a hoisting end 14 opposite the pivot end 12 of the boom.

[0223] The boom 5 is supported by the crane structure 4, so that the boom can rotate about the vertical rotation axis 15. The pivot end 12 of the boom is pivotable connected to the crane structure 4, so that the boom 5 can pivot up and down about a horizontal boom pivot axis 16. As depicted, the boom of the exemplary embodiment shown in FIG. 1 can pivot about the horizontal boom pivot axis parallel to the plane of the Figure.

[0224] The boom luffing assembly 6 comprises a boom luffing wire 17 and a boom luffing winch, associated with the luffing wire 17. The boom luffing wire 17 extends from the boom luffing winch to the hoisting end 14 of the boom, for pivoting the boom 5 upward and downward about the boom pivot axis 16, and for supporting the boom 5 in a hoisting position relative to the crane structure 4.

[0225] The hoisting assembly, for hoisting a load, is not shown. Typically, the hoisting assembly comprises a hoisting winch, a hoisting wire, and a load suspension device, wherein the hoisting wire extends from the hoisting winch via a hoisting wire guide, located at the hoisting end of the of the boom 5, to the load suspension device.

[0226] According to the invention, the crane comprises the boom restrainer 8, for reducing, preferably blocking, upward pivoting of the boom 5, when the boom 5 is in a top zone.

[0227] In the top zone, the angle of the boom 5 with the vertical rotation axis 15 of the crane is 40 degrees or less, preferably is 50 degrees or less, most preferably is 60 degrees or less. Thus, in an embodiment, the top zone extends from a position wherein the boom makes an angle with the vertical rotation axis of the crane of 60 degrees, up to a position wherein the boom is fully raised. In the embodiment shown, the top zone starts at the position of the boom 5 with the vertical axis of rotation 15 of the crane 1 is 40 degrees. This is the position wherein the boom restrainer 8 engages the boom 5 of the crane 1.

[0228] The boom restrainer 8 comprises a first member 18 and a second member 19.

[0229] According to the invention, the first member 18 of the boom restrainer is configured for engaging, preferably being connected with, the crane structure or a mast of the crane, when the boom is in the top zone. Furthermore, the second member 19, is configured for engaging, preferably being connected with, the boom, when the boom is in the top zone.

[0230] In the embodiment shown, the boom restrainer is embodied as a telescopic arm 8. The first member is embodied as the piston body 18 and the second member is embodied as the piston rod 19. The second member 19 therefore is telescopically received in the first member 18.

[0231] In the embodiment shown, the first member 18 is mounted on the mast 4 of the crane 1, with the second member 19 directed towards the boom 5 of the crane 1. Furthermore, in the embodiment shown, the boom restrainer 8 comprises a telescopic arm on both sides of the boom 5, which can be seen in the top view depicted in FIG. 4

[0232] The second member 19, of both telescopic arms, comprises a couple element 20, provided on the second member of the respective telescopic arm, for engaging the boom 5, when the boom is pivoted into the top zone. In the embodiment shown, the boom is provided with a catcher 21 embodied as a cylindrical body. The catch is configured to be coupled when the boom is raised into the top zone, and the telescopic arm is in an extended positon. This is depicted in intermediate position shown in FIG. 3.

[0233] When the boom is pivoted upwards in the top zone, the second member 19 is configured to telescopically slide into the first member 18. Furthermore, the couple element 20 remains engaged with the catcher 21. FIG. 1 depicts the boom 5 in a fully raised position, in which the second member 19 of the telescopic arm is fully retracted in the first member 18. In this embodiment, the boom, when in the fully raised positon, is positioned at the top end of the top zone.

[0234] It is furthermore noted that the telescopic arm 8, when not coupled with the boom 5, is supported in a position in which the couple element 20 will engage the catcher 21, when the boom 5 is pivoted into the top zone. This position of the telescopic arm 8 is for example depicted in FIG. 1, in combination with the boom being supported by the luffing assembly in a substantially horizontal position.

[0235] The control system 9 comprises one or more sensors to monitor loss of a load, e.g. sensors monitoring tension in the hoisting wire and/or in the luffing wire, and/or one or more sensors to monitor roll of the vessel. According to the invention, boom restrainer 8 can be switched between a passive modus and an active modus.

[0236] In the passive modus, the boom restrainer allows for movement of the second member 19 relative of the first member 18, and thus allows for movement of the boom 5 relative to the mast 2 of the crane 1. In this modus, the hydraulic cylinders of the telescopic arms allow for the boom to be pivoted upwards. In an embodiment, the hydraulic cylinders are pressurised, such that they are biased, but still allow for the boom to be pivoted upwards.

[0237] In the active modus, the boom restrainer slows down and preferably blocks movement of the second member 19 relative to the first member 18, and thus slows down and preferably blocks movement of the boom 5 relative to the mast 2 of the crane 1. In this modus, the hydraulic cylinders of the telescopic arms are hydraulically actuated, to dampen any upward movement of the boom, and preferably stop any upward movement of the boom.

[0238] In the embodiment shown, the boom restrainer comprises two telescopic arm, and each telescopic arm 8 comprises one hydraulic cylinder. The boom restrainer furthermore comprises a hydraulic system coupled with the two hydraulic cylinders. The hydraulic cylinders are configured to move the second member, i.e. the piston of the hydraulic cylinder, in a linear direction relative to the first member, i.e. the piston body.

[0239] The control system 9 is configured to switch the boom restrainer 8 from the passive modus into the active modus when the one or more sensors register a loss of load and/or roll of the vessel. More in particular, the control system is configured to use the hydraulic system to slow down movement of the boom and/or stop movement of the boom. Thus, the boom restrainer is configured for reducing, preferably blocking, upward pivoting of the boom relative to the crane, when the boom is in a top zone in case of a loss of load supported by the crane.

[0240] It is noted that, when the boom 5 pivots out of the top zone, the first member, more in particular the couple element 20, disengages from the catcher 21.

[0241] FIG. 5 shows a hydraulic schedule of the hydraulic cylinders of the boom restrainer 8. The boom restrainer 8 comprises a gas buffer for each hydraulic cylinder. In the figures, the gas buffer is not depicted. Each gas buffer is mounted to the corresponding cylinder and is connected to the hydraulic circuit of the corresponding cylinder via a medium separator. The gas buffer forces the hydraulic cylinder in an extend position. The volume ratio between the hydraulic cylinder and the gas buffer preferably is such that the hydraulic cylinder acts as a progressive spring.

[0242] FIG. 6 shows an alternative exemplary embodiment of a heavy lift crane 101 according to the invention in side view, wherein the crane 101 is depicted with a boom 105 in a lowered position and in a raised position.

[0243] The second member 119 of the boom restrainer 108 comprises a track 119. The track 119 is mounted on the boom 105 and extends along the longitudinal axis of the boom. The first member 118 is an arm that extends between a base end 118A and a boom end 118B. The base end 118A of the arm 118 is pivotable mounted on the crane structure 104, and the boom end 118B is configured to be slideable coupled with the track 119.

[0244] When the boom 104 is pivoted upward into the top range, the arm 118 slides with its boom end 118B upwards along the boom 105, more in particular, slides with its boom end 118B upwards along the boom 105.

[0245] When the boom 104 is in the top zone, and the boom restrainer 108 is in the passive modus, the boom restrainer allows for the boom end 118B of the arm 118 to slide along the track 119, and thus allows for movement of the boom 104 relative to the crane structure or the mast of the crane.

[0246] When the boom 104 is in the top zone, and the boom restrainer 108 is in the active modus, the boom restrainer is configured to slow down and preferably block movement of the boom end 118B along the track 119, to thus slow down and preferably block movement of the boom 104 in the upward direction relative to the crane structure or the mast of the crane.

[0247] In the embodiment shown, the track is provided with a coupling hook, for engaging the cart, and a brake winch. The hook couples with the cart when the cart engages the track. The hook is linked with the winch via a brake cable. Preferably, the winch is, similar to winches provided on towboats, provided with a slip device, allowing the cable drum of the winch to slip relative to the drive, to thus enable overload of the wire.

[0248] The winch is configured to keep the tension in the brake cable constant, and thus to allow the cart to move along the track, when the boom restrainer is in the passive modus.

[0249] When the boom restrainer is switched into the active modus, the winch exerts a pulling force on the hook, thus slowing down the cart, preferably stopping the cart, and thus slowing down upward movement of the boom.

[0250] In an alternative embodiment, the winch is provided on the crane structure, and the brake wire is connected to the arm of the boom restrainer. In this embodiment, the wire can be permanently coupled with the arm. When the boom retainer is switched into the active modus, the winch.

[0251] Also, in addition or as an alternative, other configurations may be used to slow down and/or stop the cart and pivoting of the arm. For example, the track can be provided with a brake cylinder, extending parallel to the track, that couples with the cart when the cart engages the track, and that, by extending and retracting allows for the cart to move along the track, and that is also used for slowing down and stopping movement of the cart along the track.

[0252] In the embodiment shown, the boom end 118 of the arm 118 is provided with a cart that engages the track 119 provided on the boom.

[0253] According to the invention, the arm 118 may also be a telescopic arm, comprising a hydraulic cylinder configured to at least partially dampen movements of the boom.

[0254] It is noted that, when the boom 105 pivots out of the top zone, the first member, more in particular the cart mounted at the end of the arm 188, disengages the track.

[0255] FIG. 7 shows an alternative exemplary embodiment of a heavy lift crane 201 according to the invention in side view, wherein the crane 201 is depicted with a boom 205 in a lowered position and in a raised position.

[0256] In the embodiment shown in FIG. 7, the first member 218 of the boom restrainer 208 has an receiving end 218A and the second member 219 has a penetrating end 219A. The penetrating end 219A of the second member 219 is configured to be at least partially inserted into the receiving end 218A of the first member.

[0257] The first member 218 is mounted to the crane structure 204 with the receiving end 218A facing the boom 205, and the second member 219 is mounted on the boom 205 with the penetrating end 219A facing the crane structure 204. When the boom 205 is pivoted into the top zone, the penetrating end 219A of the second member 219 is inserted into the receiving end 218A of the first member 218, and the second member 219 slides into the first member 218 when the boom 205 is pivoted upwards in the top zone,

[0258] The first member 218 is configured to, when the boom 205 is in the top zone and the boom restrainer 208 is in the passive modus, allow for movement of the second member 219 relative of the first member 2018, and to thus allow for movement of the boom 205 relative to the crane structure 204 or the mast 210 of the crane 201.

[0259] The first member 218 is furthermore configured to, when the boom 205 is in the top zone and the boom restrainer 208 is in the active modus, slow down and preferably block movement of the second member 219 relative to the first member 218, to thus slow down and preferably block tilting movement of the boom 205 in the upward direction relative to the crane structure 204 or the mast 210 of the crane 201.

[0260] In the preferred embodiment shown, the first member 218 is provided with fixating devices for engaging the second member 219. The fixating devices 218 can be activated by the control system 209 to reduce movement of the first member 218 relative to the second member 219, and preferably stop movement of the first member 218 relative to the second member 219, and huts of the boom 204 relative to the crane structure 204 or the mast 210 of the crane.

[0261] More in particular, in the embodiment shown, the first member 218 comprises fixating devices embodied as brake callipers, and the second member 219 comprises a brake plate 222 configured to slide between the brake callipers of the first member, when the boom is in the top zone. By activating the brake callipers, they engage the braking plate, which slows down movement of the second member relative to the first member, and may stop movement of the second member relative to the first member.

[0262] According to a third aspect, the invention provides for an offshore crane vessel, preferably comprising a heavy lift crane as shown in one or more of the FIGS. 1-7, wherein the vessel is configured for preventing excessive roll due to loss of load.

[0263] In an embodiment, the vessel is provided with additional floating bodies, set up opposite the lifting side of the vessel, to provide the hull with a more stable set up. The lifting side is the side where the crane is set up, and at which side the load will be lifted into of out of the water. For example, the crane may be mounted on the starboard side of the vessel, for lifting a pile, overboarding the pile, and lowering the pile towards the seafloor. In such an embodiment, the floating bodies are provided opposite the starboard side, at the port side of the vessel.

[0264] By providing the floating bodies, the hull of a vessel can temporarily be widened. Thus, in such an embodiment, the hull is effectively extended in a direction away from the side at which the crane is to lift a load. Thus, the hull is better able to resist a roll of the vessel, caused by the ballast tanks, in case of a sudden loss of the load lifted by the crane. For example, one or more pontoons can be connected to the hull of the vessel. Preferably, the pontoons are set up spaced form the hull, and are connected to the vessel via spacer arms, for example a truss construction extending between the vessel and the pontoons.

[0265] In an embodiment, the pontoons are also configured to provide a counterweight, in addition to the ballast tanks, to compensate for the load lifted by the crane.

[0266] FIG. 8 shows a partial view in cross section of a vessel 300 according to a third aspect of the invention, wherein the vessel 300 is provided with a floating body 302, e.g. a pontoon, on a side opposite a side where a crane 301 is provided on the vessel. It is noted that the crane 301 is only partially depicted.

[0267] In this embodiment, the floating body 302 is connected to the hull of the vessel via an arm. By providing an arm between the vessel and the floating body, in contrast with mounting the floating body directly to the hull of the vessel, the floating body is spaced from the vessel. This configuration increase the effect of the floating body, by increasing the moment force enacted by the floating body onto the vessel, in case of a loss of load. Due to the loss of load, the ballast tanks present in the vessel are no longer balanced by the load that was supported by the crane, and will make the vessel pivot about its longitudinal axis. This pivot movement is than counteracted by the upward force enacted by the floating bodies.

[0268] FIG. 9 shows a partial view in cross section of the vessel of FIG. 8 in a level and in a tilted position, wherein the vessel 310 is provided with a raised pontoon 312 on a side opposite a side where a crane (not shown) is provided on the vessel. In this embodiment, the floating body is pivotable attached to the hull, such that it can be pivoted in into an upright storage position, depicted with dotted lines, and a horizontal working position, in which it enacts an upward floating forces upon the hull of the vessel in case the vessel is pivoted due to the crane losing a load. In the figure, the vessel with the floating body is depicted in a level floating position, indicated with continuous lines, and is depicted in a tilted position in dotted lines. Furthermore, the floating body is also depicted in the upright storage positon in dotted lines.

[0269] In the particular embodiment shown, the floating body is attached to the hull such that it, in the horizontal working position, is located above the water. Thus, the floating body only enters the water when the ship is pivoted. Under normal conditions, the floating body is located outside the water and thus does not influence the dynamic characteristics of the hull of the vessel, for example does not cause drag when the vessel is moved from one location to the other.

[0270] The upright position of the floating body, which floating body is wider than it is high, reduces the overall width of the vessel, which is for example beneficial when maneuvering inside a port, or close to other vessels.

[0271] FIG. 10 shows a partial view in cross section of the vessel of FIG. 8 in a level and in a tilted position, wherein the vessel 320 is provided with an alternative raised floating body 322 on a side opposite a side where a crane (not shown) is provided on the vessel. The floating body shown in FIG. 10 is similar to the one shown in FIG. 9, except for the dimensions of the body. The floating body in FIG. 9 is a thinner, has a bit more height and is longer. Thus, the floating body can provides substantially the same upwards floating force as the floating body depicted in FIG. 9, albeit with different dimensions.

[0272] FIG. 11 shows a partial view in cross section of the vessel of FIG. 8 in a level and in a tilted position, wherein the vessel 330 is provided with a partially raised floating body 332 on a side opposite a side where a crane (not shown) is provided on the vessel. Thus, the floating body is not emerged, and only partially penetrates the water. Therefore it only has a minimal effect on the dynamic properties of the vessel.

[0273] FIG. 12. shows a partial view in cross section of the vessel of FIG. 8 in a level and in a tilted position, wherein the vessel 340 is provided with a partially raised floating body 342 on a side opposite a side where a crane (not shown) is provided on the vessel. The floating body is similar to the floating body depicted in FIG. 11. In this embodiment, the floating body has a bevelled shape, to provide the floating body with a more dynamic shape, that compliments the shape of the vessel. Thus the drag of the floating body, when the vessel is moved from one location to another, is reduced.

[0274] FIG. 17 show a top view, a side view and a view in cross section of the vessel of FIG. 12, wherein the view in cross section shows the hull of the vessel also in a tilted position in dotted lines.

[0275] FIG. 13 shows an exemplary embodiment of a heavy lift crane 401 according to a fourth aspect of the invention in side view, wherein the crane 401 comprises a boom 404 provided with a strut on a hoisting side of the boom.

[0276] The boom of the crane 401 is provided with a strut structure 402 at the lifting side of the crane, and with one or more retainer wires 403 connected to the strut structure, for exerting a pulling force on the boom. The retainer wires are connected to a pulling device, e.g. comprising one or more hydraulic cylinders and/or one or more winches, for enacting a pulling force on the retainer wires. The strut structure 402 sets the retainer wires 403 away from the boom, to thus enable a moment force to be enacted on the boom, pulling the boom downward.

[0277] In the preferred embodiment shown, support wires 404 extend from the strut structure 402 towards the top of the boom 404, the wires being fixed to the boom and the strut structure, to prevent excessive flexing of the boom when exerting a pulling moment on the boom using the retainer wires. This embodiment of the boom is in particular beneficial in case the crane structure is of limited height compared to the length of the boom.

[0278] With a vessel according to a further aspect of the invention, a roll damping mechanism is configured to quickly react in case of loss of load, and counteract roll motion of the vessel generated by the loss of load. A solid roll damping ballast is provided that is movable in the transverse direction of the hull, a sensor detecting a loss of load, and preferably a drive and a control system operable to cause and control the movements of the solid roll damping ballast in response to the detections of the sensor to provide roll stabilization.

[0279] During use, the solid mass of the roll damping mechanism is used to counter balance the load supported by the crane, optionally in combination with the use of ballast tanks comprising water and/or for example with the floating bodies discussed above. In case of a loss of load, the solid mass is transported quickly towards the opposite side of the vessel, to thus counteract the roll generated by the initial unbalance created by the loss of load.

[0280] FIG. 14 shows an exemplary embodiment of a vessel in a partial view in cross section according to a fifth aspect of the invention, wherein the vessel is provided with a mobile ballast system. In the embodiment shown, the mobile ballast is moved along a curved track. To balance the load of the crane, the ballast is moved to the left, and upward, along the track. In case of a loss of load by the crane, the ballast is released, and will move to the right under gravity. At the right end of the track, a stop is provided. The stop preferably is configured to somewhat gradually stop the mobile ballast

[0281] FIG. 15 shows another exemplary embodiment of a vessel in a partial view in cross section according to a fifth aspect of the invention, wherein the vessel is provided with a mobile ballast system. In this embodiment, the mobile ballast is moved along the track using wires and winches.

[0282] FIG. 16 shows another exemplary embodiment of a vessel in a partial view in cross section according to a sixth aspect of the invention, wherein the vessel is provided with retractable stabilising fins for use during hoisting activities.

[0283] FIG. 18 and FIG. 19 show an exemplary embodiment of a heavy lift crane 101 according to a first aspect of the invention in side view,

[0284] According to the invention, the heavy lift crane 101 comprises a base structure 103, a crane structure 104, a boom 105, a boom luffing assembly 106, a hoisting assembly 107, a boom restrainer 108 and a control system 109. In the embodiment shown, the crane is furthermore provided with a boom stop 123. The crane is mounted on a pedestal 102.

[0285] In the embodiment shown, the heavy lift crane 101 is a pedestal crane, and the base structure 103 is embodied as a pedestal 102 that is adapted to be mounted to a vessel.

[0286] The crane structure 104 comprises a crane housing. The crane structure 104 is rotationally supported via a slew bearing that is mounted on the pedestal 102 of the crane. Thus, the crane structure 104 can rotate relative to the base 103 about a vertical rotation axis 115.

[0287] In the embodiment shown, the boom 105 has a length of about 120 meters. The boom 105 comprises a longitudinal axis 111, a pivot end 112, a mid-section 113, and a hoisting end 114 opposite the pivot end 112 of the boom.

[0288] The boom 105 is supported by the crane structure 104, so that the boom can rotate about the vertical rotation axis 115. The pivot end 112 of the boom is pivotable connected to the crane structure 104, so that the boom 105 can pivot up and down about a horizontal boom pivot axis 116. As depicted, the boom of the exemplary embodiment shown in FIG. 18 and FIG. 19 can pivot about the horizontal boom pivot axis parallel to the plane of the Figure.

[0289] The hoisting assembly 107 comprises a hoisting winch, a hoisting wire 124, and a load suspension device 125. The hoisting wire extends from the hoisting winch, along the boom 105 via a hoisting wire guide 125, located at the hoisting end of the of the boom 105, to the load suspension device 126.

[0290] The boom luffing assembly 106 comprises a boom luffing wire 117 and a boom luffing winch, associated with the luffing wire 117. The boom luffing wire 117 extends from the boom luffing winch to the hoisting end 114 of the boom, for pivoting the boom 105 upward and downward about the boom pivot axis 116, and for supporting the boom 105 in a hoisting position relative to the crane structure 104.

[0291] With the luffing system, the boom 105 of the crane 101 can be pivoted in a working zone. The working zone comprises the range of boom positions, that allow for controlled lifting loads with the crane.

[0292] According to the invention, the crane 101 comprises the boom restrainer 108 for reducing upward pivoting of the boom 105. According to the first aspect of the invention, the boom restrainer 108 engages the boom 105 when the boom is pivoted into the top zone. Thus, when the boom 105 is in the top zone it is engaged by the boom restrainer 108, and when it is lowered out of the top zone, the boom restrainer disengages the boom.

[0293] The top zone overlaps with the working zone of the crane. In the embodiment shown, when the boom 105 is in the top zone, the angle of the boom 105 with the vertical rotation axis 115 of the crane is in the range of 5-25 degrees.

[0294] In FIG. 18 the crane 101 is depicted with a boom 105 positioned at a lower end of a working zone, and in FIG. 19 with the boom 105 positioned at an upper end of the working zone.

[0295] FIGS. 20-22 show in close up a hydro-pneumatic boom restrainer 108 of the heavy lift crane 101 in different working positions.

[0296] FIG. 20 shows in close up a hydro-pneumatic boom restrainer 108 of the heavy lift crane 101 with the hydro pneumatic boom restrainer 108 not yet engaging the boom 105 of the heavy lift crane 101.

[0297] FIG. 21 shows in close up the hydro-pneumatic boom restrainer 108 of the heavy lift crane 101 with the boom 105 at the lower end of the top zone and the hydro pneumatic boom restrainer 108 engaging the boom 105 of the heavy lift crane 101.

[0298] FIG. 22 shows in close up the hydro-pneumatic boom restrainer 108 of the heavy lift crane 101 with the boom 105 at the upper end of the top zone and the hydro pneumatic boom restrainer 108 engaging the boom of the heavy lift crane.

[0299] The boom restrainer shown in FIGS. 18-22 is similar to the boom restrainer shown in FIGS. 1-5.

[0300] In both embodiments, the boom restrainer comprises hydraulic cylinders having a first member and a second member. In the embodiments shown, the first member is embodied as a piston body or cylinder body and the second member is embodied as a piston rod or cylinder rod. The second member being telescopically received in the first member. The first member of the boom restrainer is connected with the crane structure of the crane, while the second member is configured for engaging the boom, when the boom is in the top zone.

[0301] In the embodiment shown in FIGS. 18-22 the first members, i.e. piston bodies or cylinder bodies 118, of the hydraulic cylinders 127, are mounted on a stay 110 of the crane 101, with the second members, i.e. piston rods or cylinder rods 119, more in particular the cylinder heads 129, directed towards the boom 105 of the crane 101. Furthermore, in both the embodiments shown, the boom restrainer 108 comprises telescopic arms, i.e. hydraulic cylinders 127, at both sides of the boom 105.

[0302] According to the invention, the boom restrainer 108 comprises a gas buffer 128 for each hydraulic cylinder 127. Each gas buffer 128 is mounted to the corresponding cylinder 127 and is connected to the hydraulic circuit of the corresponding cylinder via a medium separator. The gas buffer 128 forces the hydraulic cylinder 127 in an extend position. The volume ratio between the hydraulic cylinder 127 and the gas buffer 128 is such that the hydraulic cylinder acts as a progressive spring. In the embodiment shown, the gas buffers 128 each have a size of 1200 litre and the cylinders 127 each have a size of 900 litre. Preferably the ratio between the volume of the gas buffer and the volume of the associated hydraulic cylinder is 4:3.

[0303] The piston rods 119 of the hydraulic cylinders 127 comprises a couple element 120, in the embodiment shown embodied as the cylinder head, for engaging the boom 105, when the boom is pivoted into the top zone.

[0304] In the embodiment shown, the boom 105 is provided with a catcher 121 for each cylinder 127. Each catcher 121 is mounted on the boom 105 and is configured for receiving the cylinder head 120 of the corresponding cylinder 127, and to lock the cylinder head, in the embodiment shown pivotable locks the cylinder head, relative to the boom, when the boom pivots upwards in the top zone. This is depicted in intermediate position shown in FIG. 21.

[0305] The catcher 121 is configured to engage the couple element 120 when the boom 105 is raised into the top zone and the hydraulic cylinders 127 are in an extended position.

[0306] In the embodiment shown, the catcher 121 comprises a guide surface 130 and a blocking surface 131. The guide surface 130 engages the cylinder head 120 when the boom 105 pivots towards the top zone, and guides the cylinder head towards the blocking surface while the boom pivots into the top zone. The blocking surface 131 is provided at an end of the guide surface 130 to lock the cylinder head 120 relative to the boom 105. In FIG. 21 the cylinder head is pivotable locked relative to the boom by the catch, such that further moment of the boom 105 pushes the cylinder rod 119 into the cylinder body 118.

[0307] In the embodiment shown, the boom is to be raised over an angle of 2 degrees for the cylinder head 120 to move along the guide surface and get locked by the catcher 121.

[0308] It is furthermore noted that, in the embodiment shown, the hydraulic cylinders 127 are pivotable supported, such that they can pivot about a horizontal axis relative to the crane structure. When the boom restrainer engages the boom, and the boom pivots upwards, the cylinders pivot in an upward direction.

[0309] When the boom is pivoted upwards in the top zone, the cylinder rod 119 telescopically slides into the cylinder body 118 while the cylinder head 120 remains engaged with the catcher 121. FIG. 19 and FIG. 22 depict boom restrainer 108 when the boom 105 is in a fully raised position. The cylinder rod 119 of the hydraulic cylinder 127 is fully retracted in the cylinder body 118. In this embodiment, the boom, when in the fully raised position, is positioned at the top end of the top zone. It is noted that in the embodiment shown the boom, when in the fully raised position, is still at an angle with the vertical rotation axis of the crane.

[0310] Under normal working conditions, the boom restrainer 108 is in a passive modus. In this passive modus, the boom restrainer 108 allows for movement of the cylinder rods 119 relative of the cylinder bodies 118, and thus allows for movement of the boom 105 relative to the crane structure 104. In this modus, the hydraulic cylinders 127 allow for the boom to be pivoted upwards.

[0311] The hydraulic cylinders are pressurised, such that they are biased into the extended position. Furthermore, the gas buffer of the hydraulic cylinders is configured such that the cylinders act as a progressive spring. When the boom restrainer engages the boom in the passive modus, the hydraulic cylinders allow for the boom to be pivoted upwards but do provide a counter force that makes that the luffing wires are extra tensioned.

[0312] The control system 109 of the boom restrained 108 comprises sensors to monitor loss of a load. In the embodiment shown, the sensors are configured to measure the movement of the cylinders rods in the cylinder bodies. When the boom suddenly pivots upwards, due to loss of load and and/or roll of the vessel, the relative speed of the cylinder rods surpasses a predetermined threshold and the control system switches the boom retainer into the active modus

[0313] In the active modus, the boom restrainer activates one or more valves in the hydraulic circuit of the hydraulic cylinders, to throttle the flow of hydraulic fluid towards the medium separator.

[0314] Thus, the movement of the cylinder rods is impeded, which slows down, and preferably eventually blocks, movement of the cylinder rods relative to the cylinder bodies, and thus slows down, and preferably eventually blocks, movement of the boom 105 relative to the crane structure 104. In the active modus, the hydraulic cylinders are thus hydraulically actuated to dampen any upward movement of the boom, and preferably stop any upward movement of the boom.

[0315] As explained, the control system 109 is configured to switch the boom restrainer 108 from the passive modus into the active modus when the one or more sensors register a loss of load and/or roll of the vessel. More in particular, the control system is configured to use the hydraulic circuit to slow down movement of the boom and/or stop movement of the boom. Thus, the boom restrainer 108 is configured for reducing, preferably blocking, upward pivoting of the boom relative to the crane, when the boom is in a top zone in case of a loss of load supported by the crane.

[0316] In the embodiment shown, the boom restrainer 108 comprises four hydraulic cylinders. The boom restrainer furthermore comprises a hydraulic circuit and a gas buffer coupled with each hydraulic cylinder.

[0317] It is noted that, when the boom 105 pivots out of the top zone, the couple element 120, disengages from the catcher 121.

[0318] In the embodiment shown, the crane 101 is furthermore provided with a boom stop 134. The boom stop 134 is configured to stop the boom 105 when it is positioned at the upper end of the working are. In this position, the boom is also at the upper end of the top zone, end is at an angle of 5 degrees with the vertical pivot axis of the crane.

[0319] The invention can be summarized according to one or more of the following clauses:

[0320] 1. Heavy lift crane for use on a vessel, the crane comprising: [0321] a base structure, wherein the base structure is adapted to be mounted to, or formed integral with, the vessel; [0322] a crane structure, wherein the crane structure is rotationally supported by the base structure for rotation of the crane structure relative to the base about a vertical rotation axis; [0323] a boom, preferably having a length of 80-200 meters, wherein the boom comprises a longitudinal axis, an pivot end, a mid-section, and a hoisting end opposite the pivot end, wherein the boom is supported by the crane structure, so that the boom can rotate about the vertical rotation axis, and wherein the pivot end of the boom is pivotably connected to the crane structure, so that the boom can pivot up and down about a horizontal boom pivot axis; [0324] a boom luffing assembly, wherein the luffing assembly comprises a boom luffing wire and a boom luffing winch, wherein the boom luffing wire extends from the boom luffing winch to the hoisting end of the boom, for pivoting the boom upward and downward about the pivot axis, and for supporting the boom in a hoisting position relative to the crane structure; [0325] a hoisting assembly for hoisting a load, wherein the hoisting assembly comprises a hoisting winch, a hoisting wire, and a load suspension device, wherein the hoisting wire extends from the hoisting winch via a hoisting wire guide, located at the hoisting end of the of the boom, to the load suspension device; [0326] a boom restrainer, for reducing, preferably blocking, upward pivoting of the boom, when the boom is in a top zone, in which top zone the angle of the boom with the vertical rotation axis of the crane is 40 degrees or less, preferably is 50 degrees or less, most preferably is 60 degrees or less, wherein the boom restrainer comprises: a first member for engaging, preferably being connected with, the crane structure or a mast of the crane, when the boom is in the top zone;
a second member, for engaging, preferably being connected with, the boom, when the boom is in the top zone;
a control system; comprising one or more sensors to monitor loss of a load, e.g. sensors monitoring tension in the hoisting wire and/or in the luffing wire, and/or one or more sensors to monitor roll of the vessel;
wherein the boom restrainer can be switched between a passive modus, in which it allows for movement of the second member relative of the first member, and thus allows for movement of the boom relative to the crane structure or the mast of the crane, and an active modus, in which it slows down and preferably blocks movement of the second member relative to the first member, and thus slows down and preferably blocks movement of the boom relative to the crane structure or the mast of the crane, and
wherein the control system is configured to switch the boom restrainer from the passive modus into the active modus when the one or more sensors register a loss of load and/or roll of the vessel.

[0327] 2. Heavy lift crane according to clause 1, wherein the boom of the crane can be pivoted in a working zone, in which working zone for example the angle of the boom with the vertical rotation axis of the crane is between 20 degrees and 100 degrees with the vertical rotation axis of the crane, and wherein the top zone overlaps with the working zone.

[0328] 3. Heavy lift crane according to clause 1 or clause 2, wherein the crane furthermore is provided with a boom stop, wherein the boom stop is configured to block movement of the boom at a safety angle, the safety angle being the maximum height wherein the boom can be pivoted, for example is at the upper end of the working zone.

[0329] 4. Heavy lift crane according to clause 3, wherein the boom stop comprises a crush zone, configured to slow down and preferably stop a boom by controlled deformation, for example when the boom moves beyond a maximum working angle, for example moves beyond the upper end of the working zone.

[0330] 5. Heavy lift crane according to clause 3 or clause 4, wherein the boom stop comprises a bumper, e.g. hydraulic cylinders, that engage the boom prior to the boom reaching a maximum working angle, to resiliently receive the boom and prevent the boom from coming to a hard stop against the boom stop.

[0331] 6. Heavy lift crane according to clause 5, wherein the boom stop comprises sensors, for example in the bumper, e.g. in the form of hydraulic cylinders, that are linked to the control system, and wherein the control system is configured to block the luffing system from further lifting the boom, thus preventing the luffing system from pivoting the boom beyond the maximum working angle.

[0332] 7. Heavy lift crane according to one or more of the preceding clauses, wherein the crane structure is provided with one or more bumpers that are configured to engage the boom, preferably an impact zone on the boom, when the boom pivots beyond a maximum working angle.

[0333] 8. Heavy lift crane according to one or more of the preceding clauses, wherein the boom is provided with one or more bumpers that are configured to engage the crane structure and/or the mast of the crane, preferably an impact zone on the crane structure or the mast of the crane, when the boom pivots beyond a maximum working angle

[0334] 9. Heavy lift crane according to one or more of the preceding clauses, wherein the boom restrainer comprises a hydraulic cylinder, and wherein the boom restrainer is configured to keep the cylinder at a minimum pressure, at least when the boom is in contact with the boom restrainer, such that the restrainer keeps contact with the boom when the boom suddenly pivots in the downward direction, i.e. suddenly pivots away from the restrainer.

[0335] 10. Heavy lift crane according to one or more of the preceding clauses, wherein the control system is configured to switch between slowing down of the boom and blocking the boom movement of the boom, for example by respectively partially and fully activating brake callipers or a hydraulic cylinder in a telescopic arm.

[0336] 11. Heavy lift crane according to one or more of the preceding clauses, wherein the boom restrainer is comprises a crush zone, configured to slow down and stop a boom by controlled deformation, when the boom moves above a maximum pivot speed.

[0337] 12. Heavy lift crane according to clause 11, wherein the maximum pivot speed is too high for the boom restrainer to slow down the boom prior to the boom receiving a maximum working angle, given the angle at which the boom restrainer is switched into the active modus.

[0338] 13. Heavy lift crane according to one or more of the preceding clauses, wherein the boom restrainer can be disconnected from the crane and/or from the boom, or wherein the first member can be moved away from the second member, when the boom is lowered below the top zone.

[0339] 14. Heavy lift crane according to one or more of the preceding clauses, wherein the control system is configured to, once switched into the active modus, slow down movement of the boom in the upward direction as well as in the downward direction.

[0340] 15. Heavy lift crane according to one or more of the preceding clauses, wherein the boom restrainer comprises a telescopic arm, the telescopic arm comprising the first member and the second member, wherein the second member is telescopically received in the first member, and wherein the first member is mounted on the crane structure, or the mast of the crane, with the second member directed towards the boom of the crane; and

wherein the second member comprises a couple element, provided on the second member of the telescopic arm, for engaging the boom, preferably for engaging a catch provided on the boom, when the boom is pivoted into the top zone, and wherein the second member is configured to telescopically slide into the first member when the boom is pivoted into the top zone,
wherein the telescopic arm furthermore is configured to,
when the boom is in the top zone and the boom restrainer is in the passive modus, allow for movement of the second member relative of the first member, and to thus allow for movement of the boom relative to the crane structure or the mast of the crane, and
when the boom is in the top zone and the boom restrainer is in the active modus, slow down and preferably block movement of the second member relative to the first member, e.g using brake pads or hydraulic fluid, to thus slow down and preferably block tilting movement of the boom in the upward direction relative to the crane structure or the mast of the crane.

[0341] 16. Heavy lift crane according to clause 15, wherein the arm comprises at least one hydraulic cylinder and an hydraulic system coupled with the at least one hydraulic cylinder, wherein the at least one hydraulic cylinder is configured to move the second member in a linear direction relative to the first member, and wherein the control system is configured to use the hydraulic system to slow down movement of the boom and/or stop movement of the boom.

[0342] 17. Heavy lift crane according to one or more of the clauses 1-14, wherein the first member has an receiving end and the second member has a penetrating end, and wherein the penetrating end of the second member is configured to be at least partially inserted into the receiving end of the first member,

wherein the first member is mounted to the crane structure with the receiving end facing the boom, and the second member is mounted on the boom with the penetrating end facing the crane structure, and wherein, when the boom is pivoted into the top zone, the penetrating end of the second member is inserted into the receiving end of the first member, and the second member slides into the first member when the boom is pivoted upwards in the top zone,
wherein the first member is configured to,
when the boom is in the top zone and the boom restrainer is in the passive modus, allow for movement of the second member relative of the first member, and to thus allow for movement of the boom relative to the crane structure or the mast of the crane, and when the boom is in the top zone and the boom restrainer is in the active modus, slow down and preferably block movement of the second member relative to the first member, e.g using brake pads, to thus slow down and preferably block tilting movement of the boom in the upward direction relative to the crane structure or the mast of the crane.

[0343] 18. Heavy lift crane according to clause 17, wherein the first member and/or the second member are/is provided with fixating devices for engaging the second member or the first member respectively, wherein the fixating devices can be activated by the control system to reduce movement of the first member relative to the second member, and preferably stop movement of the first member relative to the second member.

[0344] 19. Heavy lift crane according to clause 17 or clause 18, wherein the first member and/or the second member comprises fixating devices embodied as brake callipers, and wherein respectively the second member and/or the first member comprise a brake plate configured to slide between the brake callipers of the first member and/or the second member, when the boom is in the top zone.

[0345] 20. Heavy lift crane according one or more of the clauses 1-14, wherein the second member comprises a track, wherein the track is mounted on the boom and extends along the longitudinal axis of the boom, and wherein the first member is an arm that extends between a base end and a boom end, wherein the base end of the arm is pivotably mounted on the crane structure, or to the mast of the crane, and the boom end is configured to be slideable coupled with the track, and wherein, when the boom is pivoted upward in the top range, the arm slides with its boom end upwards along the boom,

wherein the first member is configured to,
when the boom is in the top zone and the boom restrainer is in the passive modus, allow for the boom end of the arm to slide along the track, and to thus allow for movement of the boom relative to the crane structure or the mast of the crane, and
when the boom is in the top zone and the boom restrainer is in the active modus, slow down and preferably block movement of the boom end of along the track, e.g. using brake pads or a cylinder, to thus slow down and preferably block tilting movement of the boom in the upward direction relative to the crane structure or the mast of the crane.

[0346] 21. Heavy lift crane according to clause 20, wherein the boom end is configured to engage the track, or a slide mounted on the track, when the boom pivots into the top zone, and to disengage the track, or slide, when the boom is pivoted in a downward direction out of the top zone.

[0347] 22. Heavy lift crane according to clause 20 or clause 21, wherein the first member is configured to engage a slide, e.g. a cart, on the track or to slidable engage the track,

[0348] 23. Heavy lift crane according to one or more of the preceding clauses, wherein the boom restrainer is at one end connected to the crane structure or the mast of the crane can be disconnected from the crane and/or from the boom, to enable a large angle between the boom and the crane structure

[0349] 24. Heavy lift crane according to clause 23, wherein the boom restrainer is configured to engage the boom and the crane structure when the angle of the boom with the vertical rotation axis of the crane is 40 degrees or less, preferably is 50 degrees or less, most preferably is 60 degrees or less.

[0350] 25. Heavy lift crane according to one or more of the preceding clauses, wherein the boom restrainer comprises an interface that enables an operator switch the boom restrainer between the passive modus and the active modus.

[0351] 26. Heavy lift crane according to one or more of the preceding clauses, wherein the control system comprises sensors for monitoring the angle of the boom, and/or that can detect of the boom is within the top zone or not.

[0352] 27. Heavy lift crane according to one or more of the preceding clauses, wherein the crane is a mast crane.

[0353] 28. Heavy lift crane according to one or more of the clauses 1-26, wherein the crane is a pedestal crane, the crane structure comprising a stay for supporting the luffing wires, and wherein the boom restrainer is preferably mounted to the stay.

[0354] 29. Offshore crane vessel provided with a heavy lift crane according to one or more of the preceding clauses.

[0355] 30. Method for stopping the upwards pivot movement of a boom, the boom moving in the top zone, using a heavy lift crane according to one or more of the clauses 1-26, or a vessel according to clause 29, wherein the method comprises the steps: [0356] Lifting a load and raising the boom into the top zone; [0357] Detecting a loss of load; [0358] Switching the boom restrainer from the passive modus into the active modus; [0359] Engaging the second member with the first member; [0360] Slowing down movement of the second member, and thus the boom, relative to the first member, and thus relative to the crane structure or the mast of the crane; [0361] Stopping movement of the second member, and thus the boom, relative to the first member, and thus relative to the crane structure or the mast of the crane.

REFERENCE SIGNS

[0362] 01 heavy lift crane [0363] 02 mast [0364] 03 base structure [0365] 04 crane structure [0366] 05 boom [0367] 06 boom luffing assembly [0368] 07 hoisting assembly [0369] 08 boom restrainer [0370] 09 control system [0371] 10 mast of the mast crane [0372] 11 longitudinal axis boom [0373] 12 pivot end boom [0374] 13 mid-section boom [0375] 14 hoisting end boom [0376] 15 vertical rotation axis of the crane [0377] 16 boom pivot axis [0378] 17 boom luffing wire [0379] 18 first member boom restrainer [0380] 118A base end arm [0381] 118B boom end arm [0382] 19 second member boom restrainer [0383] 20 couple element [0384] 21 catcher [0385] 22 brake plate [0386] 23 boom stop [0387] 101 heavy lift crane [0388] 102 pedestal [0389] 103 base structure [0390] 104 crane structure [0391] 105 boom [0392] 106 boom luffing assembly [0393] 107 hoisting assembly [0394] 108 boom restrainer [0395] 109 control system [0396] 110 stay [0397] 111 longitudinal axis of the boom [0398] 112 pivot end boom [0399] 113 mid-section of the boom [0400] 114 hoisting end boom [0401] 115 vertical rotation axis of the crane [0402] 116 boom pivot axis [0403] 117 boom luffing wire [0404] 118 piston body hydraulic cylinder [0405] 119 piston rod hydraulic cylinder [0406] 120 couple element/cylinder head [0407] 121 catcher [0408] 122 track [0409] 123 [0410] 124 hoisting wire [0411] 125 wire guide hoisting device [0412] 126 load suspension device [0413] 127 hydraulic cylinders [0414] 128 gas buffer [0415] 129 cylinder head [0416] 130 guide surface catcher 131 blocking surface catcher [0417] 132 control system [0418] 133 sensor control system [0419] 300 vessel [0420] 301 crane [0421] 302 floating body

HEAVY LIFT CRANE

Assignee

Inventors

Cpc classification

Classification Explorer

B66C23/58

PERFORMING OPERATIONS; TRANSPORTING

Classification Explorer

B66C23/52

PERFORMING OPERATIONS; TRANSPORTING

Classification Explorer

B66C23/92

PERFORMING OPERATIONS; TRANSPORTING

Classification Explorer

B66C2700/084

PERFORMING OPERATIONS; TRANSPORTING

Classification Explorer

B66C23/905

PERFORMING OPERATIONS; TRANSPORTING

International classification

Classification Explorer

B66C23/52

PERFORMING OPERATIONS; TRANSPORTING

Classification Explorer

B66C23/90

PERFORMING OPERATIONS; TRANSPORTING

Classification Explorer

B66C23/92

PERFORMING OPERATIONS; TRANSPORTING

Classification Explorer

B66C23/58

PERFORMING OPERATIONS; TRANSPORTING

Abstract

Claims

Description