Heavy crane

Abstract

This invention relates to cranes for use on marine vessels. According to the invention, the crane is provided with a boom restraint, wherein the boom restraint is a hydraulic-pneumatic boom restraint (108) for reducing upward pivoting of the boom (105) when the boom is in the top region. The boom restraint (108) comprises: a plurality of hydraulic cylinders (127), each having a hydraulic circuit and a cylinder rod (119), the cylinder rod (119) having a cylinder head (128), wherein the hydraulic cylinders (127) are mounted on a crane structure (104), and the cylinder head (120) points towards the boom (105) of the crane (101), preferably the hydraulic cylinders (127) are mounted on a bracket (105) of the crane structure (104); and a catcher (121) corresponding to each hydraulic cylinder (127), wherein each catcher is mounted on the boom (105) and configured to receive the cylinder head (120) of the corresponding hydraulic cylinder (127), and when the boom is in the top region... When the top region pivots upward, each catcher is configured to lock the cylinder head relative to the boom, preferably pivotally locking the cylinder head; a gas buffer (128) for each hydraulic cylinder (127), wherein each gas buffer (128) is mounted to the corresponding hydraulic cylinder (127) and connected to the hydraulic circuit of the corresponding hydraulic cylinder via a media separator, wherein the gas buffer (128) forces the hydraulic cylinder into an extended position, wherein the volume ratio between the hydraulic cylinder (127) and the gas buffer (128) causes the hydraulic cylinder (127) to act as a progressive spring, for example, the size of each gas buffer is in the range of 1000 liters to 1400 liters, such as 1200 liters, and the size of each hydraulic cylinder (127) is in the range of 800 liters to 1000 liters, such as 900 liters, preferably, the ratio between the volume of the gas buffer and the volume of the associated hydraulic cylinder is 4:3.

Description

Technical Field

[0001] This invention relates to a crane for offshore vessels, specifically, to a heavy-duty crane for the installation of offshore wind turbines, and more specifically, to the installation of piles for supporting wind turbines. The invention further relates to an offshore crane vessel (i.e., a vessel including such a heavy-duty crane) and a method for installing piles using such an offshore crane vessel and / or the heavy-duty crane. For example, it relates to the installation of piles suitable for supporting offshore wind turbines. Background Technology

[0002] In the field of offshore cranes, there is a trend towards the development of large-scale cranes, specifically for installing piles used to support offshore wind turbines. Installing offshore wind turbines in waters deeper than currently encountered will necessitate larger and heavier foundations. Therefore, it is anticipated that in the near future, there will be a need to install piles longer than 100 meters (potentially 120 meters or longer). Consequently, handling such components will require very tall cranes. Furthermore, the mass of such piles may exceed 1000 metric tons, possibly 1300 metric tons or more.

[0003] Larger and heavier piles require larger and heavier cranes, specifically cranes with longer booms. Typically, the cranes used for installing piles are rotary cranes. These cranes can be pedestal-mounted cranes, leg-mounted cranes, or tower cranes. The cranes have booms for supporting and positioning the piles. These booms can be 150 meters or longer.

[0004] In addition, there is a trend to install these pylons from floating vessels and along one side of the vessel. Once overboard, the pylons are lowered into the sea close to the vessel.

[0005] Lifting these heavier loads to one side of the vessel (also known as off-ship) requires vessel stability to prevent the hull from tilting laterally (also known as rolling) during installation. Ballast tanks are typically used to compensate for the loads supported by cranes, thus keeping the floating vessel level. It is believed that when the load moves stern rather than to one side (i.e., port or starboard), the movement of the load can affect the vessel's pitch. However, for slender vessels, this effect on pitch is far less significant than its effect on roll.

[0006] The raising and lowering of the long piles keeps the boom primarily in an elevated, essentially vertical position. In this elevated position, the boom is relatively close to the crane structure.

[0007] A sudden reduction in load (e.g., a sudden decrease in load supported by a crane, such as partial loss of load supported by a crane) may cause the boom to be lifted further upward. This lifting is caused by the release of bending and tensile forces within the crane (specifically, the boom and the cables supporting it).

[0008] Furthermore, in the case of floating vessels, the reduction in load supported by the crane can cause the vessel's movable ballast to tilt, thus tilting the crane to an oblique position. Movable ballast, typically in the form of ballast tanks, is used to balance the load supported by the crane on the floating vessel, especially when moving the load along one side of a slender vessel. The reduction in the load supported by the crane causes the mass of the ballast tank to tilt the vessel, which in turn tilts the crane, causing the crane's boom to move upwards relative to the horizontal.

[0009] Therefore, the loss of load supported by the crane can be attributed to the release of tension and bending forces in the crane and / or the loss of balance between the ship's movable ballast and the load, resulting in collisions between the crane boom and crane structure and / or ship components, thereby causing damage to the crane, especially to the ship and the crane boom.

[0010] Furthermore, when the boom is in the raised position, load loss may cause the boom to pivot to or beyond the vertical position. Once the boom pivots beyond the vertical position, it can no longer be supported by the pitch system. Therefore, the boom will collide with the crane structure and / or the vessel. Further, when the boom is positioned near the vertical position, the weight of the pitch cables may pull the boom into or beyond the vertical position. Additionally, when the boom is in or near the vertical position, gravity no longer effectively pulls the boom downwards. Therefore, the boom may become stuck in that position.

[0011] Furthermore, especially in the event of a sudden loss of load or a sudden movement of the vessel (e.g., caused by abnormal waves), the dynamic movement of the boom can cause the cables of the pitching system and / or lifting system to slacken, or even cause these cables to come off their pulleys.

[0012] As can be observed, in this paper, rolling is defined as the tilting rotation of a ship about its longitudinal axis (fore-aft or bow-stern axis). Furthermore, rolling motion towards a stable state (or heel) due to the ship's own weight distribution is called heel. Heeling refers to unintentional or accidental displacement caused by floods, cargo movement, etc.

[0013] Roll typically occurs when a load is added outside the ship and along one side of the vessel (e.g., on the starboard or port side). The ship's ballast system is used to counteract the roll and keep the ship level. Loss of load can cause the ship to eventually be in a heeled position, i.e., the ship lists to the port or starboard side. Summary of the Invention

[0014] According to a first aspect, the present invention aims to provide an improved heavy-duty crane for offshore vessels, or at least an alternative to existing cranes for such applications. A further object of the invention is to provide a crane more capable of handling load loss, or at least less susceptible to damage due to load loss. A further object of the invention is to provide an offshore crane vessel more capable of handling load loss, or at least less susceptible to damage due to load loss.

[0015] The present invention achieves the stated objective by providing a crane according to claim 1.

[0016] According to claim 1, the heavy-duty crane according to the present invention comprises:

[0017] - Base structure, wherein the base structure is suitable for installation on or integrally formed with a vessel;

[0018] - A crane structure, wherein the crane structure is rotatably supported by a base structure for rotating the crane structure relative to the base about a vertical axis of rotation;

[0019] - A boom, preferably having a length of 80 to 200 meters, wherein the boom includes a longitudinal axis, a pivot end, a middle section and a lifting end opposite to the pivot end, wherein the boom is supported by a crane structure so that the boom can rotate about a vertical axis of rotation, wherein the pivot end of the boom is pivotally connected to the crane structure so that the boom can pivot up and down about a horizontal boom pivot axis;

[0020] - A boom pitch assembly, wherein the pitch assembly includes a boom pitch cable and a boom pitch winch, wherein the boom pitch cable extends from the boom pitch winch to the lifting end of the boom for pivoting the boom up and down about a pivot axis and for supporting the boom in a lifting position relative to the crane structure;

[0021] The pitching assembly is capable of pivoting the boom to the top region, preferably in the top region the angle between the boom and the vertical rotation axis of the crane is in the range of 0 to 30 degrees, more preferably in the range of 0 to 25 degrees, and most preferably in the range of 5 to 25 degrees.

[0022] - A lifting assembly for lifting a load, wherein the lifting assembly includes a lifting winch, a lifting cable and a load suspension device, wherein the lifting cable extends from the lifting winch through a lifting cable guide located at the lifting end of the boom to the load suspension device;

[0023] - A hydraulic-pneumatic boom restraint for reducing upward pivoting of the boom when it is in the top region, wherein the boom restraint comprises:

[0024] Multiple hydraulic cylinders, each having a hydraulic circuit and a cylinder rod, the cylinder rod having a cylinder head, wherein the hydraulic cylinders are mounted on a crane structure, the cylinder heads pointing towards the crane's boom, preferably the hydraulic cylinders are mounted on a bracket of the crane structure.

[0025] Catchers, corresponding to each hydraulic cylinder, wherein each catcher is mounted on the boom and configured to receive the cylinder head of the corresponding hydraulic cylinder, and each catcher is configured to lock the cylinder head relative to the boom as the boom pivots upward in the top region, preferably pivotally locking the cylinder head;

[0026] A gas damper is provided for each cylinder, wherein each gas damper is mounted to a corresponding hydraulic cylinder and connected to the hydraulic circuit of the corresponding hydraulic cylinder via a media separator, wherein the gas damper forces the hydraulic cylinder into an extended position, and wherein the volume ratio between the hydraulic cylinder and the damper causes the hydraulic cylinder to act as a progressive spring, for example, the size of the damper is in the range of 1000 liters to 1400 liters, such as 1200 liters, and the size of the hydraulic cylinder is in the range of 800 liters to 1000 liters, such as 900 liters; preferably, the volume ratio between the gas damper and the hydraulic cylinder is 4:3; and

[0027] The control system includes one or more sensors for monitoring load loss, such as sensors for monitoring the movement of the cylinder rod of a hydraulic cylinder, for monitoring the tension in a hoisting cable, for monitoring the tension in a pitch cable, and for monitoring the roll of a ship.

[0028] The boom restraint can switch between a passive mode and an active mode. In the passive mode, the boom restraint allows movement of the boom in the corresponding hydraulic cylinder, thereby allowing movement of the boom in the top region relative to the crane structure or the crane tower. In the active mode, the boom restraint slows down and preferably prevents movement of the boom in the corresponding hydraulic cylinder, thereby slowing down and preferably preventing movement of the boom in the top region relative to the crane structure or the crane tower.

[0029] The control system is configured to switch the boom restraints from passive to active mode when one or more sensors record load loss and / or ship roll.

[0030] This invention provides a heavy-duty crane including a boom restraint. When the boom moves to the top region, the boom restraint elastically engages the boom. A hydraulic cylinder of the boom restraint is forced into an extended position. Therefore, when the boom pivots upward and engages the hydraulic cylinder, the hydraulic cylinder provides an elastic force that pushes the boom downward.

[0031] According to a first aspect of the invention, when the boom pivots to the top region, the boom constraint engages the boom. Thus, when the boom is in the top region, it is engaged by the boom constraint, and when the boom is lowered outside the top region, the boom constraint disengages from the boom. According to the invention, the top region overlaps with the working area of ​​the crane. In an embodiment, the boom constraint engages the boom when it is at an angle of 40 degrees or less, preferably 30 degrees or less, for example, 25 degrees or less. In a further embodiment, in the top region, the angle between the boom and the vertical axis of rotation of the crane is in the range of 0 to 30 degrees, preferably in the range of 0 to 25 degrees, and most preferably in the range of 5 to 25 degrees.

[0032] The boom restraints are equipped with a control system, which includes one or more sensors for monitoring load loss (e.g., sensors for monitoring movement of the cylinder rod of the hydraulic cylinder, tension in the lifting cable and / or pitch cable) and / or one or more sensors for monitoring the ship's roll.

[0033] The control system is configured to switch the boom restraints from passive to active mode when one or more sensors record load loss and / or ship roll.

[0034] In passive mode, the boom constraint allows the boom to move in the corresponding hydraulic cylinder, thereby allowing the boom to move relative to the crane structure or the crane tower in the top region.

[0035] In active mode, the boom restraints slow down and preferably prevent the movement of the boom in the corresponding hydraulic cylinder, thereby slowing down and preferably preventing the movement of the boom in the top region relative to the crane structure or the crane tower.

[0036] In passive mode, the hydraulic cylinder is subjected to the force of a gas damper. When the control system switches the boom restraint to the active position, it throttles the hydraulic fluid in the system, thereby increasing the force required to push the hydraulic cylinder to the retracted position. Therefore, the upward movement of the boom is reduced and preferably stopped.

[0037] As the boom pivots further upward into the top region, the pitch system must overcome the elastic force of the boom restraints. Therefore, the pitch cable is taut by the boom restraints. The progressive elastic force of the hydraulic cylinders means that a greater force is required to pivot the boom upward when it is in a higher position. Therefore, when the boom is in a higher position (i.e., at a smaller angle to the crane's vertical axis of rotation), the upward force due to load loss will be damped more significantly by the boom restraints.

[0038] Furthermore, in the case of load loss, the effect of tension release of the pitch cable, which could potentially cause the boom to move upward, is reduced because the pitch cable is taut by the boom restraints.

[0039] Therefore, according to a first aspect of the invention, in the event of load loss supported by the crane, when the boom is in the top region, the boom constraint is configured to reduce (preferably prevent) the upward pivoting of the boom relative to the crane.

[0040] When the boom is in the top region, the boom restraints engage the boom. In the top region, load losses, which may combine with the distribution of movable ballast on the vessel, can cause the boom to pivot, potentially causing it to end up in an upright or near-upright position and collide with the crane structure or the vessel.

[0041] The extent of the top area is specific to the design of the crane and the vessel on which the crane will be installed. Depending on the crane design, specifically the boom and the load the crane can lift, and the weight of the vessel, specifically the vessel's width and the possible load distribution of movable ballast, the top area can vary depending on the type and design of the crane.

[0042] Furthermore, the design of the boom restraints can affect the extent of the top area. When the boom restraints have a higher spring stiffness, the top area may be narrower. However, according to the invention, the boom restraints are designed to be active over a relatively large area, and are designed to engage the boom while it is still in the working area. This contrasts with conventional boom stops, which are designed to operate in a narrow area and typically engage the boom when it is near an upright position, for example, when the angle between the boom and the vertical is 6 degrees. Moreover, these conventional boom stops are positioned adjacent to the working area (i.e., during normal use for lifting loads, when the boom is not in the top area) or overlap only with a very small area of ​​the working area, for example, only with a certain degree of angular overlap, such as 3 or 4 degrees.

[0043] Furthermore, the boom restraints can be designed to prevent upward movement of the crane boom before it reaches a fully upright position; for example, preventing upward movement of the boom when the angle between the boom and the crane's vertical axis of rotation is 5 degrees. Therefore, even if the ship's roll is 5 degrees, the boom will not pass through the upright position.

[0044] According to an embodiment of the first aspect of the invention, when the boom is in the top region, the angle between the boom and the vertical axis of rotation of the crane is in the range of 0 to 30 degrees, preferably in the range of 0 to 25 degrees, and most preferably in the range of 5 to 25 degrees. For example, if the boom constraint engages the boom first when the boom pivots upward at an angle of 25 degrees to the vertical direction, the top region begins from this position of the boom. Therefore, when the angle between the boom and the vertical axis of rotation is 25 degrees or less, the boom is located in the top region.

[0045] According to the invention, the top region has a large range, that is, preferably covers an angle of more than 16 degrees, for example, an angle of 18 degrees, and preferably covers an angle of at least 20 degrees.

[0046] Furthermore, using a heavy-duty crane according to a first aspect of the invention, the crane's boom can pivot in a working area overlapping with the top area. The working area includes a range that allows the crane to control the position of the boom for lifting loads.

[0047] In the implementation scheme, the crane boom is able to pivot in the working area, for example, in the working area, the angle between the boom and the crane's vertical axis of rotation is between 20 and 100 degrees, wherein the top area overlaps with the working area.

[0048] In one embodiment, the angle between the boom and the crane's vertical axis of rotation is between 5 and 100 degrees in the working area, wherein the top region overlaps with the working area. In such an embodiment, the top region, extending at an angle of 5 to 25 degrees with respect to the vertical axis of rotation, completely overlaps with the working area. In an alternative embodiment, the top region extends at an angle of 5 to 25 degrees with respect to the vertical axis of rotation, and the working area extends at an angle of 7 to 100 degrees with respect to the vertical axis of rotation. In such an embodiment, the top region partially overlaps with the working area. It is believed that, according to the first aspect of the invention, the top region always at least partially overlaps with the working area, and more specifically, at least a major portion of the top region overlaps with the crane's working area.

[0049] By providing a crane with a boom retainer according to the first aspect of the invention, significant upward pivoting of the boom caused by the release of bending and tension forces in the crane and / or the rolling of the ship can be reduced and preferably prevented in the event of load loss.

[0050] Furthermore, when the ship pivots to an incline, such as rolling to a heeled position, the crane, and therefore the crane boom, pivots with the ship to the incline. As the ship's rolling slows and eventually stops, the boom retainer slows the boom, thus preventing the boom's kinetic energy from holding the boom in a direction toward the crane structure.

[0051] Furthermore, if the vessel begins to roll in the opposite direction (i.e., return towards its initial position) after rolling to its maximum tilt position, the boom retainer preferably also causes the boom to move with the vessel's return roll. Therefore, the boom retainer prevents the boom from being lifted upwards due to the vessel pivoting towards the boom, i.e., towards the crane structure.

[0052] Therefore, the crane with boom retainer according to the invention reduces the chance of rapid movement of the pitch cable and / or hoisting cable from its pulleys, as well as the chance of the boom colliding with components of the crane structure and / or the vessel. Thus, the boom retainer reduces the chance of significant damage to the boom, crane, and vessel due to load loss.

[0053] According to the first aspect of the invention, when the boom is in the top region, the boom restraint is connected to both the crane structure and the boom. This allows the boom restraint to quickly reduce (preferably prevent) boom movement in the event of load loss. Furthermore, since the boom restraint reduces the upward pivoting movement of the boom, this reduces slack in the pitch cable due to upward movement in the event of load loss and prevents subsequent boom descent, thereby achieving peak load on the pitch system (specifically the pitch cable). Therefore, by providing a crane with a boom retainer according to the first aspect of the invention, the chance of rapid movement of the pitch cable and / or hoisting cable from its pulleys, and the chance of the boom colliding with components of the crane structure and / or the vessel, is reduced. Thus, the boom retainer reduces the chance of significant damage to the boom, crane, and vessel due to load loss.

[0054] According to a first aspect of the invention, when the boom is in the top region, the boom constraint is connected to both the crane structure and the boom. This allows the boom constraint to quickly reduce (preferably prevent) the movement of the boom in the event of load loss.

[0055] Compared to conventional boom stops, the boom restraint according to the invention operates within the crane's working range. Conventional boom stops are configured to engage the boom when it moves out of the working area. In embodiments of the crane according to the invention, conventional boom stops can be combined with boom restraints. Thus, in such embodiments, one or more boom stop cylinders can be configured to engage the boom when the angle between the boom and the crane's vertical axis of rotation is 8 degrees, and to fully retract when the angle between the boom and the crane's vertical axis of rotation is 5 degrees.

[0056] When the crane is used to lift a load in the top area in such an implementation, the crane operates within the boom's working area. The boom is engaged by boom restraints in the top area, but away from conventional boom stops. In the event of load loss, the boom restraints reduce the extent to which the boom can pivot upwards relative to the crane, preferably preventing any substantial upward pivoting of the boom in the event of load loss, and the boom is preferably held in substantially the same position as when supporting a load. If the boom reaches the top of the top area, it is also engaged by boom stops. The boom stops further reduce boom movement and ultimately prevent further movement of the boom.

[0057] In an embodiment, the crane according to the first aspect of the invention is further provided with a boom stop, wherein the boom stop is configured to prevent movement of the boom at a safe angle, the safe angle being the maximum height to which the boom can pivot, for example, at the upper end of the working area.

[0058] It is worth noting that the top region may end at the top of the crane's boom's working range, or it may extend upwards beyond the crane's working range. If the crane is equipped with a conventional boom stop, the working area and the top region may end at the boom stop. In embodiments, the boom stop may be configured to exceed the crane's actual working range, thereby providing an additional range of boom movement and / or an additional range of boom that can be pivoted by the pitch system without supporting a load before the boom is physically stopped by the boom stop.

[0059] In a further embodiment, the boom stop includes a compression region configured to slow down and preferably stop the boom through controlled deformation, for example, when the boom moves beyond the maximum working angle, such as beyond the upper end of the working area.

[0060] In one embodiment, the boom restraint is provided with a compression area, i.e., a structure is installed or includes a configuration to slow down and preferably stop the boom by controlled deformation when the boom moves beyond the upper end of the top area. In a further embodiment, the crane is also provided with a boom stop, and both the boom stop and the boom retainer are provided with compression areas to stop the movement of the boom.

[0061] In a further embodiment, the boom stop includes a shock absorber, such as a hydraulic cylinder, which engages the boom before it reaches its maximum working angle to resiliently support the boom and prevent the boom from coming to a hard stop with the boom stop.

[0062] In a further embodiment, the boom stop includes a sensor, for example, in a shock absorber, such as a hydraulic cylinder, and the sensor is connected to a control system configured to prevent the pitch system from further raising the boom, thereby preventing the pitch system from rotating the boom beyond its maximum working angle.

[0063] According to a first aspect of the invention, the boom constraint is configured for use with heavy-duty cranes, i.e., cranes configured to lift heavier loads, such as loads greater than 1000 metric tons, for example, 1300 metric tons. These cranes typically have large booms, i.e., booms 80 meters or longer. According to the first aspect of the invention, the boom constraint is disposed in the crane structure to engage the pivot end of the boom, i.e., the lower end of the boom. In an embodiment, the boom constraint engages the boom at the lower 20% of the boom, preferably within the lower 15% of the boom. Thus, in a 100-meter-long boom, the boom constraint engages the boom within the lower 15 meters.

[0064] In an embodiment of the heavy-duty crane according to the invention, the crane structure is provided with one or more shock absorbers configured to engage the boom when the boom pivots beyond its maximum working angle, preferably engaging the impact area on the boom. The shock absorbers may be elastic, for example comprising a hydraulic cylinder, and / or may be configured to deform upon contact, or at least deform upon contact if the boom moves beyond a certain speed, thus acting similarly to a compression zone.

[0065] In one implementation, or alternatively, the boom is provided with one or more shock absorbers, which are configured to engage the crane structure and / or the crane tower when the boom pivots beyond its maximum working angle, preferably engaging the impact area of ​​the crane structure or the crane tower. The shock absorbers may be resilient, for example including hydraulic cylinders, and / or may be configured to deform upon contact, or at least deform upon contact if the boom moves beyond a certain speed, thus acting similarly to a compression zone.

[0066] According to a first aspect of the invention, the boom restraint includes a hydraulic cylinder, and the boom restraint is configured to hold the hydraulic cylinder at a minimum pressure, thereby forcing the hydraulic cylinder into an extended position. By forcing the hydraulic cylinder into the extended position, the restraint remains in contact with the boom when the boom pivots in a downward direction, for example, suddenly away from the restraint.

[0067] In this implementation, the boom constraint moves together with the boom in the top region. The biasing within the boom constraint ensures a strong contact between the boom constraint and the boom.

[0068] In an embodiment of the heavy-duty crane according to the invention, the boom constraint is provided with a control system configured to adjust the spring constant of the hydraulic cylinder, thereby switching between slowing down the boom and preventing boom movement.

[0069] In an embodiment of the heavy-duty crane according to the invention, the boom constraint includes a compression region configured to slow down and stop the boom by controlled deformation when the boom moves beyond its maximum pivoting speed.

[0070] In a further embodiment, the boom constraint includes a compression region configured to slow down and stop the boom by controlled deformation when the boom moves beyond a maximum pivot speed, the maximum pivot speed being a speed that is too high for the boom constraint to slow down the boom before it reaches its maximum working angle, taking into account the angle at which the boom constraint switches to active mode.

[0071] In the implementation scheme, the hydraulic control system of each hydraulic cylinder has one or more valves between the medium separator and the hydraulic circuit. When the boom restraint is in passive mode, one or more valves allow free flow of hydraulic fluid, thereby biasing the hydraulic cylinder by the gas damper. When the boom retainer is in active mode, one or more valves throttle the flow of hydraulic fluid, thereby hindering the movement of the piston toward the contracted position, thereby slowing down the movement of the boom, especially slowing down the sudden increase in boom movement.

[0072] In passive mode, the hydraulic cylinder is subjected to the force of a gas damper. When the control system switches the boom restraint to the active position, the hydraulic fluid in the system is throttled, thereby increasing the force required to push the hydraulic cylinder to the retracted position. Therefore, the upward movement of the boom is reduced and preferably stopped.

[0073] In a further embodiment, the hydraulic circuit is configured such that the throttling function applies only to the inward-pushing cylinder rod and not to the cylinder rod moving towards the extended position. Therefore, when the boom moves downward, the gas damper pushes the hydraulic cylinder towards the extended position, thereby maintaining the boom constraint's push on the downward-moving boom. Thus, the boom constraint helps to quickly push the boom towards a lower position and reacts quickly to slow it down again if the boom begins to move upward again. Furthermore, the boom constraint thus reduces the chance of the lift and pitch cables moving rapidly on the guide pulleys.

[0074] In the implementation plan, the hydraulic circuits of multiple hydraulic cylinders are connected to balance the load difference between the hydraulic cylinders.

[0075] In an embodiment of the invention, when the boom pivots upward in the top region, the hydraulic cylinder of the boom holder is compressed, and the hydraulic cylinder is preferably configured to act as a linear spring, thereby tauting the pitch cable.

[0076] In the implementation, the cylinder rod of the boom constraint is fully extended when engaged with the boom and the boom is at an angle of 35 degrees to the vertical axis of rotation.

[0077] In the implementation scheme, the cylinder rod of the boom constraint is fully retracted when the angle between the boom and the vertical axis of rotation is 15 degrees.

[0078] In this implementation, the boom is an A-frame boom, and the boom restraints include four hydraulic cylinders mounted such that each cylinder engages one side of an A-frame leg. This distribution of the hydraulic cylinders is optimal for preventing torsion in the boom. Furthermore, the hydraulic circuits connecting the cylinders are preferably configured to balance the forces applied to the boom by the hydraulic cylinders.

[0079] In this implementation, the boom includes a box-shaped frame at the base end, and a catcher corresponding to the hydraulic cylinder is mounted on the box-shaped frame. This configuration allows for optimal force distribution from the hydraulic cylinder to the boom.

[0080] In the implementation, when the cylinder rod moves from the extended position to the retracted position, the spring stiffness of the hydraulic cylinder increases by at least 15%, preferably at least 20%, for example 25%.

[0081] In the implementation, the hydraulic cylinder is pivotally supported, allowing it to pivot about a horizontal axis relative to the crane structure. Therefore, as the boom moves in the top region, the engagement angle of the hydraulic cylinder (specifically, the cylinder rod) relative to the boom can be adjusted.

[0082] In the implementation scheme, the support is an A-frame, and two hydraulic cylinders are installed on each leg of the A-frame. Preferably, when the boom is in the lowered position, the pitch cable passes between the two sets of hydraulic cylinders.

[0083] In one embodiment, the catcher includes a guide surface and a stop surface, wherein the guide surface engages the cylinder head when the boom pivots toward the top region and guides the cylinder head toward the stop surface as the boom pivots further toward the top region, for example, when the boom is raised beyond an angle in the range of 1 to 3 degrees, such as when the boom is raised beyond an angle of 2 degrees, wherein the stop surface is positioned at the end of the guide surface to lock the cylinder head relative to the boom, such that further torque of the boom pushes the cylinder rod into the hydraulic cylinder.

[0084] In one implementation, the boom constraint includes an interface that allows an operator to switch the boom constraint between passive and active modes.

[0085] In the implementation scheme, the control system includes sensors for monitoring the angle of the boom and / or for detecting whether the boom is in the top area.

[0086] In one implementation, the crane is a pedestal-mounted crane, and the crane structure includes a support frame for supporting the pitch cable, wherein the boom constraint is preferably mounted on the support frame. In an alternative implementation, the crane is a tower crane, and the boom constraint is mounted on the crane structure of the tower crane.

[0087] A first aspect of the invention also provides a marine crane vessel equipped with a heavy-duty crane according to the invention.

[0088] A first aspect of the invention also provides a hydraulic-pneumatic boom restraint configured for mounting on a heavy-duty crane to provide a heavy-duty crane according to the invention.

[0089] A first aspect of the invention also provides a method for stopping the upward pivotal movement of a boom, the boom moving in a top region, the method utilizing a heavy-duty crane according to the invention or a vessel according to the invention, wherein the method comprises the following steps:

[0090] Raise the boom to the top area and engage the boom with the boom restraints;

[0091] Use a crane to lift the load;

[0092] Detect load loss;

[0093] Switch the boom constraint from passive mode to active mode;

[0094] This slows down the movement of the cylinder rod in the corresponding power cylinder, thereby slowing down the movement of the boom relative to the crane structure or the crane tower.

[0095] Preferably, the movement of the cylinder rod in the corresponding power cylinder is stopped, thereby stopping the movement of the boom relative to the crane structure or the crane tower.

[0096] A first aspect of the invention also provides a crane for a ship, the crane comprising:

[0097] - Base structure, wherein the base structure is suitable for installation on or integrally formed with a vessel;

[0098] - A crane structure, wherein the crane structure is rotatably supported by a base structure for rotating the crane structure relative to the base about a vertical axis of rotation;

[0099] - A boom, wherein the boom includes a longitudinal axis, a pivot end, a middle section and a lifting end opposite to the pivot end, wherein the boom is supported by a crane structure so that the boom can rotate about a vertical axis of rotation, wherein the pivot end of the boom is pivotally connected to the crane structure so that the boom can pivot up and down about a horizontal boom pivot axis;

[0100] - A boom pitch assembly, comprising a boom pitch cable and a boom pitch winch, wherein the boom pitch cable extends from the boom pitch winch to the lifting end of the boom, for pivoting the boom upward and downward about a pivot axis within the working area, and for supporting the boom in a lifted position relative to the crane structure, wherein the pitch assembly is capable of pivoting the boom to a top region overlapping the upper end of the working area.

[0101] - A lifting assembly for lifting a load, wherein the lifting assembly includes a lifting winch, a lifting cable and a load suspension device, wherein the lifting cable extends from the lifting winch through a lifting cable guide located at the lifting end of the boom to the load suspension device;

[0102] - A hydraulic-pneumatic boom restraint for reducing upward pivoting of the boom when it is in the top region, wherein the boom restraint comprises:

[0103] Multiple hydraulic cylinders, each having a hydraulic circuit and a cylinder rod, the cylinder rod having a cylinder head, wherein the hydraulic cylinders are mounted on a crane structure, and the cylinder heads point towards the crane's boom.

[0104] Each capture device corresponds to a hydraulic cylinder, wherein each capture device is mounted on the boom and configured to receive the cylinder head of the corresponding cylinder, and each capture device is configured to pivotally lock the cylinder head relative to the boom as the boom pivots upward in the top region;

[0105] A gas damper is used for each hydraulic cylinder, wherein each gas damper is mounted to the corresponding hydraulic cylinder and connected to the hydraulic circuit of the corresponding cylinder via a media separator, wherein the gas damper forces the hydraulic cylinder to an extended position, wherein the volume ratio between the hydraulic cylinder and the damper causes the hydraulic cylinder to act as a progressive spring.

[0106] A control system that includes one or more sensors for monitoring load loss;

[0107] The boom restraint can switch between a passive mode and an active mode. In the passive mode, the boom restraint allows movement of the boom rod within the corresponding hydraulic cylinder, thereby allowing movement of the boom rod relative to the crane structure or the crane tower in the top region. In the active mode, the boom restraint slows down and preferably prevents movement of the boom rod within the corresponding hydraulic cylinder, thereby slowing down and preferably preventing movement of the boom rod relative to the crane structure or the crane tower in the top region.

[0108] The control system is configured to switch the boom restraints from passive to active mode when one or more sensors record load loss and / or ship roll.

[0109] According to a second aspect, the present invention aims to provide an improved heavy-duty crane for offshore vessels, or at least an alternative to existing cranes for such applications. A further object of the invention is to provide a crane more capable of handling load loss, or at least less susceptible to damage due to load loss. A further object of the invention is to provide an offshore crane vessel more capable of handling load loss, or at least less susceptible to damage due to load loss.

[0110] The present invention achieves the stated objective by providing a crane according to the second aspect of the invention.

[0111] According to a second aspect, the heavy-duty crane according to the invention comprises:

[0112] - Base structure, wherein the base structure is suitable for installation on or integrally formed with a vessel;

[0113] - A crane structure, wherein the crane structure is rotatably supported by a base structure for rotating the crane structure relative to the base about a vertical axis of rotation;

[0114] - A boom, having a length of 80 to 200 meters, comprising a longitudinal axis, a pivot end, a middle section, and a lifting end opposite the pivot end, wherein the boom is supported by a crane structure so that the boom can rotate about a vertical axis of rotation, wherein the pivot end of the boom is pivotally connected to the crane structure so that the boom can pivot up and down about a horizontal boom pivot axis;

[0115] - A boom pitch assembly, wherein the pitch assembly includes a boom pitch cable and a boom pitch winch, wherein the boom pitch cable extends from the boom pitch winch to the lifting end of the boom for pivoting the boom up and down about a pivot axis and for supporting the boom in a lifting position relative to the crane structure;

[0116] - A lifting assembly for lifting a load, wherein the lifting assembly includes a lifting winch, a lifting cable and a load suspension device, wherein the lifting cable extends from the lifting winch through a lifting cable guide located at the lifting end of the boom to the load suspension device;

[0117] - A boom restraint for reducing (preferably preventing) upward pivoting of the boom when it is in the top region, wherein the angle between the boom and the vertical axis of rotation of the crane is 40 degrees or less, preferably 50 degrees or less, and most preferably 60 degrees or less, wherein the boom restraint comprises:

[0118] The first component is used to engage the crane structure or the crane tower when the boom is in the top region, preferably connected to the crane structure or the crane tower.

[0119] The second component is used to engage the boom engagement when the boom is in the top region, and preferably is connected to the boom.

[0120] The control system includes one or more sensors for monitoring load loss (e.g., sensors for monitoring tension in hoisting cables and / or pitch cables) and / or one or more sensors for monitoring the ship's roll.

[0121] The boom constraint can switch between a passive mode and an active mode. In the passive mode, the boom constraint allows movement of the second member relative to the first member, thereby allowing movement of the boom relative to the crane structure or the crane tower. In the active mode, the boom constraint slows down and preferably prevents movement of the second member relative to the first member, thereby slowing down and preferably preventing movement of the boom relative to the crane structure or the crane tower.

[0122] The control system is configured to switch the boom restraints from passive to active mode when one or more sensors record load loss and / or ship roll.

[0123] Therefore, the present invention provides a heavy-duty crane including a boom and a boom constraint. In the event of load loss supported by the crane, when the boom is in the top region, the boom constraint is configured to reduce (preferably prevent) upward pivoting of the boom relative to the crane.

[0124] The constraint according to the second aspect of the invention can be used at least when the boom is in the top region, i.e., when the angle between the boom and the vertical axis of rotation of the crane is 40 degrees or less, preferably 50 degrees or less, and most preferably 60 degrees or less. In the top region, relatively small pivoting movements of the boom may cause the boom to collide with the crane structure or the vessel.

[0125] Compared to conventional boom stops, the constraint according to the second aspect of the invention operates within the crane's working range. Conventional boom stops are configured to engage the boom when it moves out of the working area. In embodiments of the crane according to the invention, conventional boom stops can be combined with boom constraint members.

[0126] When a crane is used to lift a load, it operates using a boom in the working area. Therefore, the boom is positioned away from conventional boom stops. In the event of load loss, boom retainers reduce the extent to which the boom can pivot upwards relative to the crane, preferably preventing any upward pivoting of the boom under load loss conditions. The boom is preferably held in substantially the same position as when supporting a load.

[0127] Therefore, by providing a crane with a boom retainer according to the second aspect of the invention, in the event of load loss, it is possible to reduce and preferably prevent upward pivoting of the boom caused by the release of bending and tension forces in the crane and / or the rolling of the ship.

[0128] Furthermore, when the ship pivots to an incline, such as rolling to a heeled position, the crane, and therefore the crane boom, pivots with the ship to the incline. As the ship's rolling slows and eventually stops, the boom retainer slows the boom, thereby preventing the boom's kinetic energy from causing it to pivot in the upward direction, and more specifically, in the direction toward the crane structure.

[0129] Furthermore, if the vessel begins to roll in the opposite direction after rolling to its maximum tilt position, the boom retainer according to the second aspect of the invention preferably also causes the boom to move with the return rolling of the vessel. Therefore, the boom retainer prevents the boom from being lifted upwards due to the vessel pivoting toward the boom, i.e., toward the crane structure.

[0130] Therefore, by providing a crane with a boom retainer according to the second aspect of the invention, the chance of rapid movement of the pitch cable and / or hoisting cable from its pulleys, and the chance of the boom colliding with components of the crane structure and / or the vessel, are reduced. Thus, the boom retainer reduces the chance of significant damage to the boom, crane, and vessel due to load loss.

[0131] Furthermore, the boom restraints prevent the boom from pivoting upwards beyond the position supported by the pitch cable. This also prevents the boom from subsequently falling back down, thus enabling peak load control in the pitch system (specifically, the pitch cable).

[0132] It is believed that, according to the invention, the boom restraint is preferably connected to the crane structure (or the crane tower) and the boom at least when the boom is in the top region. This allows the boom restraint to quickly reduce (preferably prevent) the movement of the boom when activated.

[0133] It is worth noting that when an assembly of a boom constraint is referred to as being connected to or supported by the crane tower, it is considered to be connected to or supported by the tower, rather than being connected to or supported by the crane structure. More specifically, it is considered to be rotatably connected to or rotatably supported by the tower, such that the assembly can rotate synchronously with the crane structure and the crane boom.

[0134] For example, in tower cranes, the pitch cable (and in particular the pulleys supporting the pitch cable) is typically rotatably supported at the top of the tower. Furthermore, a boom stop can be located at the top of the tower, allowing it to rotate together with the pitch system pulleys and the crane structure (i.e., the crane boom) about the crane's vertical axis of rotation.

[0135] In an embodiment of the heavy-duty crane according to the invention, the crane boom is pivotable in the working area, for example, in the working area, the angle between the boom and the crane's vertical axis of rotation is between 20 and 100 degrees, wherein the top area overlaps with the working area.

[0136] The work area is the range of boom positions that allow for lifting loads using a crane.

[0137] In the implementation plan, the crane is also equipped with a boom stop, wherein the boom stop is configured to prevent the movement of the boom at a safe angle, which is the maximum height to which the boom can pivot, for example, at the upper end of the working area.

[0138] It is worth noting that the top region may end at the top of the crane's boom's working range, or it may extend upwards beyond the crane's working range. If the crane is equipped with a conventional boom stop, the working area and the top region may end at the boom stop. In embodiments, the boom stop may be configured to exceed the crane's actual working range, thereby providing an additional range of boom movement and / or an additional range of boom that can be pivoted by the pitch system without supporting a load before the boom is physically stopped by the boom stop.

[0139] In a further embodiment, the boom stop includes a compression region configured to slow down and preferably stop the boom through controlled deformation, for example, when the boom moves beyond the maximum working angle, such as beyond the upper end of the working area.

[0140] In a further embodiment, the boom stop includes a shock absorber, such as a hydraulic cylinder, which engages the boom before it reaches its maximum working angle to resiliently support the boom and prevent the boom from coming to a hard stop with the boom stop.

[0141] In a further embodiment, the boom stop includes a sensor, for example, in a shock absorber, such as a hydraulic cylinder, and the sensor is connected to a control system configured to prevent the pitch system from further raising the boom, thereby preventing the pitch system from pivoting the boom beyond its maximum working angle.

[0142] In an embodiment of the heavy-duty crane according to the invention, the crane structure is provided with one or more shock absorbers configured to engage the boom when the boom pivots beyond its maximum working angle, preferably engaging the impact area on the boom. The shock absorbers may be resilient, for example including hydraulic cylinders, and / or may be configured to deform upon contact, or at least deform upon contact if the boom moves beyond a certain speed, thus acting similarly to a compression zone.

[0143] In one implementation, or alternatively, the boom is provided with one or more shock absorbers, which are configured to engage the crane structure and / or the crane tower when the boom pivots beyond its maximum working angle, preferably engaging the impact area of ​​the crane structure or the crane tower. The shock absorbers may be resilient, for example including hydraulic cylinders, and / or may be configured to deform upon contact, or at least deform upon contact if the boom moves beyond a certain speed, thus acting similarly to a compression zone.

[0144] In an embodiment of the heavy-duty crane according to the invention, the boom constraint includes a hydraulic cylinder configured to maintain the hydraulic cylinder at a minimum pressure at least when the boom is in contact with the boom constraint, such that when the boom suddenly pivots in a downward direction, i.e., suddenly pivots away from the constraint, the constraint remains in contact with the boom.

[0145] In this implementation, the boom restraint still allows the pitch system to pivot the boom in the top region under normal operating conditions, and the boom restraint moves with the boom in the top region. The biasing in the boom restraint ensures a firm contact between the boom restraint and the boom. Furthermore, the biasing may have already suppressed or partially suppressed any upward movement of the boom not caused by the pitch system before the boom restraint is activated. Therefore, this pretension in the hydraulic cylinder may reduce the movement that the boom restraint reduces or prevents when activated, or prevent the boom restraint from being activated in the case of relatively small upward movements.

[0146] In an embodiment of the heavy-duty crane according to the invention, the control system is configured to switch between slowing down the boom and stopping the boom movement, for example, by partially and fully activating the brake calipers or hydraulic cylinders in the telescopic boom, respectively.

[0147] In an embodiment of the heavy-duty crane according to the invention, the boom constraint includes a compression region configured to slow down and stop the boom by controlled deformation when the boom moves beyond its maximum pivoting speed.

[0148] In a further implementation, the maximum pivot speed is the speed at which the boom constraint switches to active mode, which is too high for the boom constraint to slow down the boom before it reaches its maximum working angle.

[0149] In an embodiment of the heavy-duty crane according to the invention, when the boom is lowered below the top region, the boom restraint can be disconnected from the crane and / or the boom, or the first member can be moved away from the second member.

[0150] In an embodiment of the heavy-duty crane according to the invention, the control system is configured to slow down the movement of the boom in both the upward and downward directions once switched to active mode.

[0151] In an embodiment of the heavy-duty crane according to the present invention, the boom constraint includes a telescopic boom, the telescopic boom including a first component and a second component, wherein the second component is telescopically accommodated in the first component, wherein the first component is mounted on the crane structure or the crane tower, and the second component points toward the crane boom;

[0152] The second component includes a connecting element disposed on the second component of the telescopic boom for engaging the boom when the boom pivots to the top region, preferably engaging a catcher disposed on the boom. The second component is configured to retractably slide into the first component when the boom rotates to the top region.

[0153] The telescopic boom is also configured as follows:

[0154] When the boom is in the top region and the boom restraints are in passive mode, movement of the second member relative to the first member is permitted, thereby allowing movement of the boom relative to the crane structure or the crane tower.

[0155] When the boom is in the top region and the boom restraint is in active mode, the movement of the second member relative to the first member is slowed down and preferably prevented, for example by using brake pads or hydraulic fluid, thereby slowing down and preferably preventing the boom from tilting upward relative to the crane structure or the crane tower.

[0156] In a further embodiment, the telescopic boom includes at least one hydraulic cylinder and a hydraulic system coupled to the at least one hydraulic cylinder, wherein the at least one hydraulic cylinder is configured to move a second member relative to a first member in a linear direction, and wherein the control system is configured to utilize the hydraulic system to slow down and / or stop the movement of the boom.

[0157] It is believed that if the boom restraints are engaged quickly enough, boom movement can be prevented. Once the boom has moved, the system can choose to stop it directly or slow it down before stopping its movement. It is worth noting that in some implementations, under certain conditions, the boom restraints may only successfully slow the boom's movement, not successfully stop it. This is still sufficient to prevent the boom from contacting the crane or causing significant damage to the top of the boom mounted on the crane structure. Because the boom restraints are engaged with the boom when operating in the top area, they can respond quickly to load losses or sudden, unexpected increases in the boom's pivoting speed. Therefore, the boom restraints prevent damage to the boom that would be impossible without them.

[0158] In an embodiment of the heavy-duty crane according to the invention, a first component has a receiving end and a second component has an inserting end, wherein the inserting end of the second component (brake plate) is configured to be at least partially inserted into the receiving end of the first component (brake caliper).

[0159] The first component is mounted on the crane structure with its receiving end facing the boom, and the second component is mounted on the boom with its insertion end facing the crane structure. When the boom pivots to the top region, the insertion end of the second component inserts into the receiving end of the first component. When the boom pivots upwards in the top region, the second component slides into the first component.

[0160] The first component is configured as follows:

[0161] When the boom is in the top region and the boom restraints are in passive mode, movement of the second member relative to the first member is permitted, thereby allowing movement of the boom relative to the crane structure or the crane tower.

[0162] When the boom is in the top region and the boom restraint is in active mode, the movement of the second member relative to the first member is slowed down and preferably prevented, for example by using brake pads, thereby slowing down and preferably preventing the boom from tilting upward relative to the crane structure or the crane tower.

[0163] In a further embodiment, the first component and / or the second component are respectively provided with a fixing device for engaging the second component or the first component, wherein the fixing device can be activated by the control system to reduce the movement of the first component relative to the second component, and preferably to stop the movement of the first component relative to the second component.

[0164] In an embodiment of the heavy-duty crane according to the invention, the first component and / or the second component includes a fixing device implemented as a brake caliper, wherein the second component and / or the first component each include a brake plate configured to slide between the brake calipers of the first component and / or the second component when the boom is in the top region.

[0165] In an embodiment of the heavy-duty crane according to the invention, the second component includes a rail, wherein the rail is mounted on the boom and extends along the longitudinal axis of the boom, wherein the first component is an arm extending between a base end and a boom end, wherein the base end of the arm is pivotally mounted to the crane structure or the crane tower, and the boom end is configured to be slidably connected to the rail, wherein when the boom pivots upward in its top range, the arm and the boom end of the arm slide upward along the boom.

[0166] The first component is configured as follows:

[0167] When the boom is in the top region and the boom restraints are in passive mode, the boom end is allowed to slide along the track, thus allowing movement of the boom relative to the crane structure or the crane tower.

[0168] When the boom is in the top region and the boom restraints are in active mode, the movement of the boom end along the track is slowed down and preferably prevented, for example by using brake pads or a power cylinder, thereby slowing down and preferably preventing the boom from tilting relative to the crane structure or the crane tower in the upward direction.

[0169] In a further embodiment, the boom end is configured to engage a track or a slider mounted on the track when the boom pivots to the top region, and disengage from the track or slider when the boom pivots downward out of the top region.

[0170] In a further embodiment, or as an alternative embodiment, the first component is configured as a slider on the track, such as a trolley, or is slidably engaged with the track.

[0171] In an embodiment of the heavy-duty crane according to the invention, one end of the boom constraint is connected to the crane structure or the crane tower, and can be disconnected from the crane and / or boom to achieve a larger angle between the boom and the crane structure.

[0172] In a further embodiment, the boom constraint is configured to engage the boom and the crane structure when the angle between the boom and the vertical axis of rotation of the crane is 40 degrees or less, preferably 50 degrees or less, and most preferably 60 degrees or less.

[0173] In an embodiment of the heavy-duty crane according to the invention, the boom constraint includes an interface that allows the operator to switch the boom constraint between a passive mode and an active mode.

[0174] In an embodiment of the heavy-duty crane according to the invention, the control system includes sensors for monitoring the angle of the boom and / or for detecting whether the boom is in the top region.

[0175] In an embodiment of the heavy-duty crane according to the present invention, the crane is a tower crane.

[0176] In an alternative embodiment of the heavy-duty crane according to the invention, the crane is a base-mounted crane, the crane structure including a support for supporting the pitch cable, wherein the boom constraint is preferably mounted on the support.

[0177] The present invention also provides a marine crane vessel equipped with one or more heavy-duty cranes according to the preceding claims.

[0178] The present invention also provides a method for stopping the upward pivoting movement of a boom, the boom moving in the top region, the method utilizing a heavy-duty crane according to the invention or a vessel according to the invention, wherein the method comprises the following steps:

[0179] Increase the load and raise the boom to the top area;

[0180] Detect load loss;

[0181] Switch the boom constraint from passive mode to active mode;

[0182] Join the second component to the first component;

[0183] This slows down the movement of the second component relative to the first component, thereby slowing down the movement of the boom relative to the crane structure or the crane tower.

[0184] To stop the movement of the second component relative to the first component, thereby stopping the movement of the boom relative to the crane structure or the crane tower;

[0185] In one embodiment, the crane includes a mobile mass. The mobile mass is slidably supported by the crane's boom, allowing the mass to move along the boom from a proximal end of the boom located at its pivot axis to a distal end. Preferably, the boom is provided with a track extending along it, and the boom mass is provided with a track for mounting a carriage, enabling the mobile mass to move along the track.

[0186] In addition, the boom is equipped with a mass drive, such as a lifting system or a magnetic drive, which is configured to move the mass away from the proximal end of the boom in a damping direction and toward the distal end of the boom.

[0187] In a further embodiment, the boom is provided with a movable block retaining system to ensure that the movable block is located at a position away from the proximal end of the boom, and more specifically, to prevent the movable block from moving toward the proximal end of the boom.

[0188] In the event of upward pivoting of the boom, such as by a sudden loss of load supported by the boom and / or by pivoting movement of the vessel, the movable block is pushed toward the distal end of the boom.

[0189] When the boom pivots upward, for example, due to a sudden loss of load supported by the boom and / or the pivoting movement of the vessel, the movable block is pushed toward the distal end of the boom. Moving the movable block away from the boom's pivot axis, and optionally away from the vessel's pivot axis, the block shifts away from the vessel's center of gravity, and the boom's pivoting movement is slowed.

[0190] In addition, or as an alternative implementation, the crane's pitch system may be equipped with a pitch release device, so that the pitch is released to the extent that the boom does not pivot rather than to a tilted position, or only in a limited manner.

[0191] In the implementation scheme, the pitch cable segments can form a loop via an emergency release pulley, which can move to extend the amount of pitch cable between the crane superstructure and the boom, thereby preventing the crane structure from pivoting due to the ship's rolling motion, thus pulling the boom upward and preventing passive and active lifting of the boom.

[0192] In addition, or as an alternative implementation, the boom equipped with pulley blocks for guiding pitch cables can be movably supported so that it can move along or even away from the boom in an emergency, thereby preventing the crane structure from pivoting due to the ship's rolling to pull the boom upward, thus preventing passive and active lifting of the boom.

[0193] In one embodiment, the crane boom has a support structure on the lifting side of the crane, and one or more retaining cables connected to the support structure to apply tension to the boom. The retaining cables are connected to a pulling device (e.g., including one or more hydraulic cylinders and / or one or more winches) to apply tension to the retaining cables. The support structure is configured to position the retaining cables away from the boom structure, thereby enabling the application of a torque on the boom to pull it downwards.

[0194] In a preferred embodiment, one or more support cables extend from the strut structure toward the top of the arm, and the cables are secured to the boom and strut structure to prevent excessive bending of the boom when a tensile torque is applied to the boom using the holding cables.

[0195] This implementation of the boom is particularly advantageous when the height of the crane structure is limited compared to the length of the boom.

[0196] According to a third aspect, the present invention provides an offshore crane vessel, preferably comprising a heavy-duty crane according to a second aspect of the invention, wherein the vessel is configured to prevent excessive rolling due to load loss.

[0197] In this implementation, the vessel is equipped with additional buoys positioned opposite the lifting side to provide a more stable setup for the hull. Therefore, in this implementation, the hull effectively extends away from the side where the crane lifts the load. Consequently, in the event of a sudden loss of the load lifted by the crane, the hull is better able to resist the rolling motion caused by the ballast tanks.

[0198] For example, one or more pontoons may be connected to the hull of a vessel. Preferably, the pontoons are spaced apart from the hull and connected to the vessel via spacer arms, such as a truss structure extending between the vessel and the pontoons.

[0199] In the implementation scheme, or alternatively, the vessel supporting the crane is equipped with a floating anchor to prevent excessive tilting of the vessel should the crane lose at least a portion of the load being lifted. As described above, when the crane is used to form a floating vessel for lifting heavier loads (particularly, along one side of the vessel), ballast tanks are used to compensate for the load lifted by the crane, thereby balancing the vessel. When the load or a portion thereof is lost, the ballast tanks tilt the vessel to a pivot position. The changed position of the vessel (specifically, the move to the changed position) causes the crane boom to be raised, and may result in the boom being raised to or beyond a vertical position.

[0200] To prevent ship movement caused by the weight of the ballast tanks, thus preventing dynamic lifting of the boom, the ship is equipped with a floating anchor. The floating anchor is installed on the side of the ship where the crane supports the load. If the load is partially lost, the weight of the ballast tanks will cause the ship to roll away from the floating anchor. Even if the floating anchor does not prevent the ship from rolling to a pivot position, the rate of roll will be reduced. This, in turn, reduces dynamic lifting caused by the ship's rolling movement.

[0201] In a further embodiment, the floating anchor is supported by a winch, which can be activated to wind the floating anchor support line at a higher speed. This increases the tension of the floating anchor, thereby generating a tension opposite to the ship's roll. Preferably, a control system is provided that monitors the ship's position and / or the load supported by a crane (specifically, by the crane's lifting cable). In the event of a sudden loss of roll and / or load, the control system can activate the winch to pull the floating anchor, thereby counteracting the ship's roll. The control system can also reduce the winch speed as the ship rolls back towards its initial position after rolling away from the side supporting the load. Thus, the control system prevents the winch from rolling the ship in the opposite direction.

[0202] In the implementation scheme, the vessel is equipped with a hull featuring a stabilizing plate configured to reduce the speed at which the hull can roll in the water, i.e., reduce the speed at which the hull can pivot about its longitudinal axis. For example, in the event of partial load loss, ballast tanks can roll the vessel's hull to a pivoting position. The hull with the stabilizing plate is not designed to prevent the vessel from rolling, but rather to reduce the speed at which the vessel rolls to a pivoting position. By reducing the rolling speed, the kinetic energy transmitted to the boom is reduced, thereby reducing or even eliminating the boom's dynamic lifting. Therefore, the boom remains more or less in the position defined by the pitch cable relative to the crane. This reduces the chance of the boom pivoting to a vertical position.

[0203] The stabilizing plate has a surface extending in a plane perpendicular to the ship's roll direction, similar to a bilge keel. To effectively reduce roll speed caused by sudden load loss, the stabilizing plate has a relatively large surface area. Therefore, when the ship is not used for lifting but is traveling between geographical locations, the stabilizing plate must be removed to avoid negatively impacting the ship's dynamic characteristics. In some embodiments, the stabilizing plate can be folded along the ship's hull or raised onto the ship's deck. In other embodiments, the stabilizing plate is telescopic and can be folded or retracted into a recess in the ship's hull.

[0204] In the implementation scheme, or as an alternative implementation scheme, the vessel supporting the crane is provided with one or more devices for reducing and / or slowing down the vessel's rolling motion caused by a sudden loss of load supported by the crane.

[0205] Heavy-duty crane vessels are typically equipped with ballast water systems to compensate for static heeling caused by the weight of the boom and the suspended load during lifting operations, especially when the load is overboard. Such ballast water systems usually consist of ballast tanks and associated pumps within the vessel's hull. Pump capacity typically limits ballast transfer and prevents the ballast tanks from being emptied quickly enough in the event of load loss.

[0206] In the prior art, it is known to additionally stabilize crane vessels through active roll damping mechanisms. These mechanisms actively suppress roll motion, a rotational movement about the ship's longitudinal axis generated by moments generated by waves that periodically oppose the ship's torque. For crane vessels, even small roll moments can result in large roll deviations due to the load suspended by the heavy crane.

[0207] An example of an active roll damping mechanism is described in WO 2009048322.

[0208] For a ship according to a fourth aspect of the invention, the roll suppression mechanism is configured to react quickly in the event of load loss and to counteract the roll motion of the ship caused by the load loss. A solid roll suppression ballast movable in the lateral direction of the hull is provided, a sensor for detecting load loss, and an actuator and control system operable to induce and control movement of the solid roll suppression ballast in response to sensor detection, thereby providing roll stability.

[0209] During operation, the solid blocks of the roll suppression mechanism are used to balance the load supported by the crane, and can be used in conjunction with water-filled ballast tanks. In the event of load loss, the solid blocks are rapidly moved to the other side of the vessel, thereby counteracting the roll caused by the initial imbalance resulting from the load loss.

[0210] If ballast tanks are used, it is preferable to move the solid load as far as possible to the other side of the vessel. If the solid load is the main weight balancing the load supported by the crane, the solid load may initially be moved to the other side of the vessel, but will eventually be moved to the center of the vessel.

[0211] A solid block can be mounted on a track extending from one side of the vessel to the other, perpendicular to the vessel's longitudinal axis. In one embodiment, an actuator, such as a winch or supercapacitor, is provided to rapidly move the solid block to the other side of the vessel. Alternatively, a pre-tensioned power cylinder can also be used to move the block from its initial position. At the other end of the track, a buffer is provided to slow the block. In one embodiment, the buffer can be a capacitor. As an alternative embodiment, a deformable buffer or a hydraulic cylinder connected to the buffer can be used, wherein the buffer is configured to slow the block without acting as a spring to push the block back after slowing.

[0212] In an alternative embodiment, the block is configured as a fall weight and mounted on a curved track. In this embodiment, in the event of load loss, the fall weight is released and travels downwards to the other side of the vessel under gravity. In a further embodiment, an additional actuator may be provided to accelerate the load. At the other end of the track, a shock absorber / damper is provided to capture and slow down the block.

[0213] Advantageous embodiments of heavy-duty cranes according to a second aspect of the invention, methods according to a second aspect of the invention, and methods according to further aspects of the invention are disclosed in the sub-claims and / or the specification, wherein aspects of the invention are further described and elucidated based on several exemplary embodiments, some of which are shown in the schematic diagrams. In the drawings, the last two digits of the reference numerals for components that correspond in terminology or construction and / or function are the same.

[0214] The embodiments and aspects of the invention disclosed herein can be used alone or in combination to prevent the crane boom from pivoting upwards, more specifically to prevent contact between the boom and the crane structure, more specifically to prevent the boom from folding, and more specifically to prevent the boom from collapsing.

[0215] While reference is made to one or more figures primarily for illustrative purposes, any technical feature described below may be combined with any independent claim of this application, either alone or in any other form that may be technically combined with one or more other technical features.

[0216] Those skilled in the art will understand that the technical features required or optional for one embodiment of the invention discussed herein can also be applied to one or more other embodiments described herein, and that the features perform their specified functions. All such combinations are contemplated herein, unless such combinations would result in a technically impossible solution and / or fail to satisfy the required function. Attached Figure Description

[0217] In the attached diagram:

[0218] Figure 1 A side view of a first exemplary embodiment of a heavy-duty crane according to a second aspect of the invention is shown, wherein the crane is described as having a boom in a lowered position and a raised position;

[0219] Figure 2 It shows Figure 1 A side view of a heavy-duty crane, wherein the crane is depicted with the boom in a lowered position, a raised position, and two intermediate positions;

[0220] Figure 3 It shows Figure 1A close-up side view of a heavy-duty crane, in which the crane is depicted with the boom in both a lowered and intermediate position;

[0221] Figure 4 It shows Figure 1 A close-up top view of a heavy-duty crane, in which the crane is depicted with the boom in a lowered and intermediate position;

[0222] Figure 5 The hydraulic stroke is shown;

[0223] Figure 6 A side view of a second exemplary embodiment of a heavy-duty crane according to the present invention is shown, wherein the crane is described as having a boom in a lowered position and a raised position;

[0224] Figure 7 A side view of a third exemplary embodiment of a heavy-duty crane according to the present invention is shown, wherein the crane is described as having a boom in a lowered position and a raised position;

[0225] Figure 8 A partial schematic diagram of a cross-section of a ship according to a third aspect of the present invention is shown, wherein a floating body is provided on the side of the ship opposite to the side on which a crane is mounted;

[0226] Figure 9 It shows Figure 8 Partial schematic diagrams of cross-sections of a ship in horizontal and inclined positions, wherein the ship has an elevated floating body on the side opposite to the side where the crane is mounted on the ship;

[0227] Figure 10 It shows Figure 8 Partial schematic diagrams of cross-sections of a ship in horizontal and inclined positions, wherein an alternative raised float is provided on the side of the ship opposite to the side on which a crane (not shown) is mounted;

[0228] Figure 11 It shows Figure 8 Partial schematic diagrams of cross-sections of a ship in horizontal and inclined positions, wherein a partially raised floating body is provided on the side of the ship opposite to the side on which a crane (not shown) is installed;

[0229] Figure 12 It shows Figure 8 Partial schematic diagrams of cross-sections of a ship in horizontal and inclined positions, wherein a partially raised floating body is provided on the side of the ship opposite to the side on which a crane (not shown) is installed;

[0230] Figure 13A side view of an exemplary embodiment of a heavy-duty crane according to a fourth aspect of the present invention is shown, wherein the crane includes a boom with a support column disposed on the lifting side of the boom;

[0231] Figure 14 A partial schematic cross-section of an exemplary embodiment of a ship according to a fifth aspect of the present invention is shown, wherein the ship is provided with a movable ballast system;

[0232] Figure 15 A partial schematic cross-section of another exemplary embodiment of a ship according to a fifth aspect of the invention is shown, wherein the ship is provided with a movable ballast system;

[0233] Figure 16 A partial schematic cross-section of another exemplary embodiment of a vessel according to a sixth aspect of the invention is shown, wherein the vessel is provided with retractable stabilizing fins for use during lifting operations;

[0234] Figure 17 It shows Figure 12 The ship's top view, side view, and cross-sectional schematic diagram, where the cross-sectional schematic diagram shows the ship's hull in an inclined position as indicated by the dashed line;

[0235] Figure 18 A side view of an exemplary embodiment of a heavy-duty crane according to a first aspect of the invention is shown, wherein the crane is described as having a boom located at the lower end of the working area;

[0236] Figure 19 It shows Figure 18 A heavy-duty crane, wherein the boom is located at the upper end of the working area;

[0237] Figure 20 Shown in close-up Figure 18 The hydraulic and pneumatic boom restraint of the heavy-duty crane, wherein the hydraulic and pneumatic boom restraint has not yet engaged the boom of the heavy-duty crane;

[0238] Figure 21 Shown in close-up Figure 18 The hydraulic and pneumatic boom restraint of the heavy-duty crane, wherein the boom is located at the lower end of the top area, and the hydraulic and pneumatic boom restraint engages with the boom of the heavy-duty crane;

[0239] Figure 22 Shown in close-up Figure 18 The hydraulic-pneumatic boom restraint of a heavy-duty crane, wherein the boom is located at the upper end of the top region, and the hydraulic-pneumatic boom restraint engages with the boom of the heavy-duty crane. Detailed Implementation

[0240] Figure 1A side view of a first exemplary embodiment of a heavy-duty crane 1 according to a second aspect of the invention is shown, wherein the crane 1 is described as having a boom 4 in a lowered position and an elevated position.

[0241] According to the present invention, a heavy-duty crane includes a base structure 3, a crane structure 4, a boom 5, a boom pitching assembly 6, a lifting assembly 7, a boom restraint member 8, and a control system 9. In the illustrated embodiment, the crane is further provided with a boom stop member 23.

[0242] In the illustrated embodiment, the heavy-duty crane 1 is a tower crane, the base structure 3 is implemented as a tower 2, and the tower is suitable for installation on a ship.

[0243] The crane structure 4 includes a crane housing. The crane structure 4 is rotatably supported by a base structure (in this embodiment, the crane tower 2) for rotation of the crane structure relative to the base about a vertical axis of rotation 15. Therefore, the vertical axis of rotation of the crane coincides with the vertical axis of the crane tower.

[0244] In the illustrated embodiment, the boom 5 has a length of approximately 120 meters. The boom 5 includes a longitudinal axis 11, a pivot end 12, a middle section 13, and a lifting end 14, which is opposite to the pivot end 12 of the boom.

[0245] The boom 5 is supported by the crane structure 4, allowing the boom to rotate about a vertical axis of rotation 15. The pivot end 12 of the boom is pivotally connected to the crane structure 4, allowing the boom 5 to pivot up and down about a horizontal boom pivot axis 16. As described, Figure 1 The boom of the exemplary embodiment shown can pivot about a horizontal boom pivot axis parallel to the plane of the figures.

[0246] The boom pitch assembly 6 includes a boom pitch cable 17 and a boom pitch winch associated with the pitch cable 17. The boom pitch cable 17 extends from the boom pitch winch to the lifting 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 the lifting position relative to the crane structure 4.

[0247] A lifting assembly for lifting the load is not shown. Typically, the lifting assembly includes a lifting winch, a lifting cable, and a load suspension device, wherein the lifting cable extends from the lifting winch through a lifting cable guide located at the lifting end of the boom 5 to the load suspension device.

[0248] According to the invention, the crane includes a boom constraint 8 for reducing (preferably preventing) upward pivoting of the boom 5 when the boom 5 is in the top region.

[0249] In the top region, the angle between the boom 5 and the vertical rotation axis 15 of the crane is 40 degrees or less, preferably 50 degrees or less, and most preferably 60 degrees or less. Therefore, in this embodiment, the top region extends from a position where the angle between the boom and the vertical rotation axis of the crane is 60 degrees to a position where the boom is fully raised. In the illustrated embodiment, the top region begins at a position where the angle between the boom 5 and the vertical rotation axis 15 of the crane 1 is 40 degrees. This is the position where the boom constraint 8 engages with the boom 5 of the crane 1.

[0250] The rod restraint member 8 includes a first component 18 and a second component 19.

[0251] According to the invention, the first member 18 of the boom constraint is configured to engage (preferably connect) with the crane structure or the crane tower when the boom is in the top region. Furthermore, the second member 19 is configured to engage (preferably connect) with the boom when the boom is in the top region.

[0252] In the illustrated embodiment, the boom constraint is implemented as a telescopic arm 8. The first component is implemented as a piston body 18, and the second component is implemented as a piston rod 19. Therefore, the second component 19 is telescopically accommodated within the first component 18.

[0253] In the illustrated embodiment, the first component 18 is mounted on the tower 4 of the crane 1, and the second component 19 points towards the boom 5 of the crane 1. Furthermore, in the illustrated embodiment, the boom restraint 8 includes telescopic booms on both sides of the boom 5, which can... Figure 4 As seen in the top view described in the text.

[0254] The second member 19 of each of the two telescopic booms includes a connecting element 20 disposed on the second member of the respective telescopic boom to engage the boom 5 when the boom pivots into the top region. In the illustrated embodiment, the boom is provided with a catcher 21 implemented as a cylinder. The catcher is configured to engage when the boom is raised to the top region and the telescopic boom is in the extended position. This is in Figure 3 The middle position shown is described.

[0255] As the boom pivots upward in the top region, the second member 19 is configured to retractably slide into the first member 18. Furthermore, the coupling element 20 remains engaged with the catcher 21. Figure 1 The description shows the boom 5 in a fully raised position, where the second member 19 of the telescopic boom is fully retracted into the first member 18. In this embodiment, the boom is located at the top of the top region when in the fully raised position.

[0256] It is further noteworthy that when boom 5 pivots to the top region, telescopic boom 8, when not connected to boom 5, is supported at the position where coupling element 20 will engage catcher 21. Combined with boom supported in a substantially horizontal position by the pitch assembly, the position of telescopic boom 8 is, for example, as shown... Figure 1 As shown.

[0257] The control system 9 includes one or more sensors for monitoring load loss (e.g., sensors for monitoring tension in the hoisting cable and / or pitch cable) and / or one or more sensors for monitoring the ship's roll. According to the invention, the boom restraint 8 can switch between passive and active modes.

[0258] In passive mode, the boom constraint allows movement of the second member 19 relative to the first member 18, thereby allowing movement of the boom 5 relative to the tower 2 of the crane 1. In this mode, the hydraulic cylinder of the telescopic boom allows the boom to pivot upward. In an embodiment, the hydraulic cylinder is pressurized such that it is biased, but still allows the boom to pivot upward.

[0259] In active mode, the boom restraints slow down and preferably prevents movement of the second member 19 relative to the first member 18, thereby slowing down and preferably preventing movement of the boom 5 relative to the tower 2 of the crane 1. In this mode, the hydraulic cylinder of the telescopic boom is hydraulically actuated to suppress any upward movement of the boom, preferably stopping any upward movement of the boom.

[0260] In the illustrated embodiment, the boom constraint includes two telescopic booms, and each telescopic boom 8 includes a hydraulic cylinder. The boom constraint also includes a hydraulic system coupled to 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).

[0261] The control system 9 is configured to switch the boom restraint 8 from a passive mode to an active mode when one or more sensors record load loss and / or ship roll. More specifically, the control system is configured to utilize a hydraulic system to slow down and / or stop the movement of the boom. Thus, in the event of load loss supported by the crane, when the boom is in the top region, the boom restraint is configured to reduce (preferably prevent) the upward pivoting of the boom relative to the crane.

[0262] It is worth noting that when boom 5 pivots out of the top area, the first component (more specifically, connecting element 20) disengages from catcher 21.

[0263] Figure 5The hydraulic stroke of the hydraulic cylinders of the boom constraint 8 is shown. The boom constraint 8 includes a gas damper for each hydraulic cylinder. The gas dampers are not depicted in the figures. Each gas damper is mounted to the corresponding hydraulic cylinder and connected to the hydraulic circuit of the corresponding hydraulic cylinder via a media separator. The gas damper forces the hydraulic cylinder into an extended position. The volume ratio between the hydraulic cylinder and the gas damper is preferably such that the hydraulic cylinder acts as a progressive spring.

[0264] Figure 6 A side view of an alternative exemplary embodiment of a heavy-duty crane 101 according to the present invention is shown, wherein the crane 101 is described as having the boom 105 in a lowered position and an elevated position.

[0265] The second member 119 of the boom constraint 108 includes 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 extending between a base end 118A and a boom end 118B. The base end 118A of the arm 118 is pivotally mounted to the crane structure 104, and the boom end 118B is configured to be slidably connected to the track 119.

[0266] When boom 104 pivots upward to the top range, arm 118 and its boom end 118B slide upward along boom 105, more specifically, arm 118 and its boom end 118B slide upward along boom 105.

[0267] When the boom 104 is in the top region and the boom constraint 108 is in passive mode, the boom constraint allows the boom end 118B of the arm 118 to slide along the track 119, thereby allowing the boom 104 to move relative to the crane structure or the crane tower.

[0268] When the boom 104 is in the top region and the boom constraint 108 is in active mode, the boom constraint is configured to slow down and preferably prevent the movement of the boom end 118B along the track 119, thereby slowing down and preferably preventing the movement of the boom 104 relative to the crane structure or the crane tower in the upward direction.

[0269] In the illustrated embodiment, the track is equipped with a connecting hook (for engaging the trolley) and a brake winch. When the trolley engages the track, the hook is connected to the trolley. The hook is connected to the winch via a brake cable. Preferably, the winch (similar to a winch on a tugboat) is equipped with a sliding mechanism, allowing the cable drum of the winch to slide relative to the drive mechanism, thereby enabling cable overload.

[0270] The winch is configured to maintain constant tension in the brake cable, thereby allowing the trolley to move along the track when the boom restraints are in passive mode.

[0271] When the boom constraint is switched to active mode, the winch applies tension to the hook, which slows down the trolley (preferably stops the trolley), thereby slowing down the upward movement of the boom.

[0272] In an alternative implementation, the winch is mounted on the crane structure, and the brake cable is connected to the boom of the boom restraint. In this implementation, the cable can be permanently connected to the boom. The winch operates when the boom restraint switches to active mode.

[0273] In addition, or as an alternative, other configurations can be used to slow down and / or stop the pivoting of the trolley and arm. For example, the track can be provided with brake cylinders extending parallel to the track, which engage with the trolley when it engages with the track and allow the trolley to move along the track by extending and retracting. The brake cylinders are also used to slow down and stop the movement of the trolley along the track.

[0274] In the illustrated embodiment, the boom end 118 of the arm 118 is provided with a trolley, which engages with a track 119 provided on the boom.

[0275] According to the invention, arm 118 may also be a telescopic arm, including a hydraulic cylinder configured to at least partially suppress movement of the boom.

[0276] It is worth noting that when boom 105 pivots out of the top area, the first component (more specifically, the trolley mounted at the end of boom 188) disengages from the track.

[0277] Figure 7 A side view of an alternative exemplary embodiment of a heavy-duty crane 201 according to the present invention is shown, wherein the crane 201 is described as having the boom 205 in a lowered position and an elevated position.

[0278] exist Figure 7 In the illustrated embodiment, the first member 218 of the boom restraint 208 has a receiving end 218A, and the second member 219 has an inserting end 219A. The inserting end 219A of the second member 219 is configured to be at least partially inserted into the receiving end 218A of the first member.

[0279] A first component 218 is mounted to the crane structure 204, with its receiving end 218A facing the boom 205. A second component 219 is mounted to the boom 205, with its insertion end 219A facing the crane structure 204. When the boom 205 pivots to the top region, the insertion end 219A of the second component 219 is inserted into the receiving end 218A of the first component 218. Furthermore, when the boom 205 pivots upwards in the top region, the second component 219 slides into the first component 218.

[0280] The first component 218 is configured to allow the second component 219 to move relative to the first component 2018 when the boom 205 is in the top region and the boom constraint 208 is in passive mode, thereby allowing the boom 205 to move relative to the crane structure 204 or the tower 210 of the crane 201.

[0281] The first component 218 is also configured to slow down and preferably prevent the movement of the second component 219 relative to the first component 218 when the boom 205 is in the top region and the boom constraint 208 is in active mode, thereby slowing down and preferably preventing the boom 205 from tilting in the upward direction relative to the crane structure 204 or the tower 210 of the crane 201.

[0282] In the preferred embodiment shown, the first component 218 is provided with a fixing device to engage the second component 219. The fixing device 218 can be activated by the control system 209 to reduce movement of the first component 218 relative to the second component 219, and preferably to stop movement of the first component 218 relative to the second component 219 and tilting of the boom 204 relative to the crane structure 204 or the crane tower 210.

[0283] More specifically, in the illustrated embodiment, the first member 218 includes a fixing device implemented as a brake caliper, and the second member 219 includes a brake plate 222 configured to slide between the brake calipers of the first member when the boom is in the top region. By engaging the brake calipers, the brake calipers engage the brake plate, which slows the movement of the second member relative to the first member and can bring the movement of the second member relative to the first member to a stop.

[0284] According to a third aspect, the present invention provides a marine crane vessel, preferably comprising, as shown in the figure below. Figures 1 to 7 One or more heavy-duty cranes are shown in the figure, wherein the vessel is configured to prevent excessive rolling due to loss of load.

[0285] In this implementation, the vessel is equipped with additional floating bodies positioned opposite the lifting side to provide greater stability to the hull. The lifting side is the side where a crane is mounted, on which the load will be lowered into or raised from the water. For example, the crane may be mounted on the starboard side of the vessel to lift piles, bring piles overboard, and lower piles toward the seabed. In this implementation, the floating bodies are positioned on the port side of the vessel opposite the starboard side.

[0286] By providing floats, the hull of the vessel is temporarily widened. Therefore, in this embodiment, the hull is effectively extended in a direction away from the side where the crane lifts the load. Consequently, in the event of a sudden loss of the load lifted by the crane, the hull is better able to resist the rolling of the vessel caused by the ballast tanks.

[0287] For example, one or more pontoons may be connected to the hull of a vessel. Preferably, the pontoons are spaced apart from the hull and connected to the vessel via spacer arms, such as a truss structure extending between the vessel and the pontoons.

[0288] In the implementation plan, the pontoons are also configured to provide a counterweight in addition to the ballast tanks to compensate for the load lifted by the crane.

[0289] Figure 8 A partial schematic diagram of a cross-section of a vessel 300 according to a third aspect of the invention is shown, wherein a float 302, for example a pontoon, is provided on the side of the vessel 300 opposite to the side on which a crane 301 is mounted. It is worth noting that the crane 301 is depicted only partially.

[0290] In this embodiment, the float 302 is connected to the ship's hull via an arm. By placing the arm between the ship and the float, the float is spaced apart from the ship, unlike when it is directly mounted to the hull. In the event of load loss, this configuration enhances the effect of the float by increasing the moment exerted by the float on the ship. Due to the load loss, the ballast tanks present on the ship are no longer balanced with the load supported by the crane, causing the ship to pivot about its longitudinal axis. This pivoting movement is counteracted by the upward force exerted by the float.

[0291] Figure 9 It shows Figure 8 A partial schematic diagram of the cross-section of a vessel in a horizontal and inclined position is provided, wherein the vessel 310 has an elevated buoy 312 on the side opposite to the side where a crane (not shown) is mounted on the vessel. In this embodiment, the buoy is pivotally attached to the hull, allowing it to pivot to an upright storage position (described by dashed lines) and a horizontal working position, in which the buoy exerts an upward buoyancy on the hull to prevent the vessel from pivoting due to load loss from the crane. In the figures, the vessel with the buoy is depicted in a horizontal floating position (indicated by solid lines) and in an inclined position (described by dashed lines). Furthermore, the buoy is also depicted in an upright storage position (described by dashed lines).

[0292] In the specific embodiment shown, the float is attached to the hull such that it (in a horizontal operating position) is above the water surface. Therefore, the float only enters the water when the ship is pivoting. Under normal circumstances, the float is above the water surface and therefore does not affect the dynamic characteristics of the ship's hull; for example, it does not cause drag when the ship moves from one position to another.

[0293] The upright position of the buoy (the buoy is wider than its height) reduces the overall width of the vessel, which is beneficial, for example, when maneuvering in port or approaching other vessels.

[0294] Figure 10 It shows Figure 8 Partial schematic diagrams of the ship's cross-sections in horizontal and inclined positions, wherein the ship 320 has an alternative raised float 322 on the side opposite to the side where a crane (not shown) is mounted on the ship. Apart from the dimensions of the main body, Figure 10 The floating body shown is Figure 9 Similar to what is shown. Figure 9 The floats in this type are thinner, higher, and longer. Therefore, despite the difference in size, the floats can provide the same level of support as... Figure 9 The upward buoyancy is basically the same as that described in the text.

[0295] Figure 11 It shows Figure 8 Partial schematic diagrams of the ship's cross-sections in horizontal and inclined positions are shown, wherein the ship 330 has a partially raised float 332 on the side opposite to the side where a crane (not shown) is mounted on the ship. Therefore, the float does not rise above the water surface and is only partially submerged. Consequently, its impact on the ship's dynamic characteristics is minimal.

[0296] Figure 12 It shows Figure 8 Partial schematic diagrams of cross-sections of the vessel in horizontal and inclined positions, wherein the vessel 340 has a partially raised float 342 on the side opposite to the side where a crane (not shown) is mounted on the vessel. The float is similar to... Figure 11 The described float has a beveled shape to provide a more dynamic form that complements the shape of the vessel. Therefore, the drag of the float is reduced as the vessel moves from one position to another.

[0297] Figure 17 It shows Figure 12 The diagram shows the ship's top view, side view, and cross-sectional view, with the cross-sectional view showing the ship's hull in an inclined position as indicated by the dashed line.

[0298] Figure 13 A side view of an exemplary embodiment of a heavy-duty crane 401 according to a fourth aspect of the invention is shown, wherein the crane 401 includes a boom 404, the boom having a support column on the lifting side of the boom.

[0299] The boom of crane 401 has a support structure 402 on the lifting side of the crane, and one or more retaining cables 403 connected to the support structure to apply tension to the boom. The retaining cables are connected to a pulling device (e.g., including one or more hydraulic cylinders and / or one or more winches) to apply tension to the retaining cables. The support structure 402 is configured to keep the retaining cables 403 away from the boom, thereby enabling a torque to be applied to the boom, thereby pulling the boom downward.

[0300] In the preferred embodiment shown, the support cable 404 extends from the support structure 402 toward the top of the boom 404, and the cable is secured to the boom and the support structure to prevent excessive bending of the boom when a tensile torque is applied to the boom using the holding cable. This embodiment of the boom is particularly advantageous when the height of the crane structure is limited relative to the length of the boom.

[0301] For a ship according to another aspect of the invention, the roll suppression mechanism is configured to react quickly in the event of load loss and to counteract the roll motion of the ship caused by the load loss. A solid roll suppression ballast movable in the lateral direction of the hull is provided, a sensor for detecting load loss, and preferably operable actuators and a control system to induce and control the movement of the solid roll suppression ballast in response to sensor detection, thereby providing roll stability.

[0302] During operation, the solid block of the roll suppression mechanism is used to balance the load supported by the crane, optionally in conjunction with water-filled ballast tanks and / or, for example, the aforementioned floats. In the event of load loss, the solid block is rapidly moved to the other side of the vessel, thereby counteracting the roll caused by the initial imbalance resulting from the load loss.

[0303] Figure 14 A partial schematic cross-section of an exemplary embodiment of a ship according to a fifth aspect of the invention is shown, wherein the ship is provided with a movable ballast system. In the illustrated embodiment, the movable ballast moves along a curved track. To balance the load of the crane, the ballast moves left and up along the track. In the event of a loss of load on the crane, the ballast is released and will move to the right under gravity. A stop is provided at the right end of the track. The stop is preferably configured to gradually bring the movable ballast to a stop to a certain extent.

[0304] Figure 15 A partial schematic cross-section of another exemplary embodiment of a vessel according to a fifth aspect of the invention is shown, wherein the vessel is provided with a movable ballast system. In this embodiment, the movable ballast is moved along tracks using cables and winches.

[0305] Figure 16A partial schematic cross-section of another exemplary embodiment of a vessel according to a sixth aspect of the invention is shown, wherein the vessel is provided with retractable stabilizing fins for use during lifting operations.

[0306] Figure 18 and Figure 19 A side view of an exemplary embodiment of a heavy-duty crane 101 according to a first aspect of the present invention is shown.

[0307] According to the present invention, a heavy-duty crane 101 includes a base structure 103, a crane structure 104, a boom 105, a boom pitching assembly 106, a lifting assembly 107, a boom restraint member 108, and a control system 109. In the illustrated embodiment, the crane is further provided with a boom stop member 123. The crane is mounted on a base 102.

[0308] In the illustrated embodiment, the heavy-duty crane 101 is a pedestal crane, and the base structure 103 is implemented as a base 102 suitable for installation onto a ship.

[0309] The crane structure 104 includes a crane housing. The crane structure 104 is rotatably supported by a slewing bearing mounted on the crane base 102. Therefore, the crane structure 104 can rotate relative to the base 103 about a vertical axis of rotation 115.

[0310] In the illustrated embodiment, the boom 105 has a length of approximately 120 meters. The boom 105 includes a longitudinal axis 111, a pivot end 112, a middle section 113, and a lifting end 114, which is opposite to the pivot end 112 of the boom.

[0311] The boom 105 is supported by the crane structure 104, allowing the boom to rotate about a vertical axis of rotation 115. The pivot end 112 of the boom is pivotally connected to the crane structure 104, allowing the boom 105 to pivot vertically about a horizontal boom pivot axis 116. As described, Figure 18 and Figure 19 The boom of the exemplary embodiment shown can pivot about a horizontal boom pivot axis parallel to the plane of the figures.

[0312] The hoisting assembly 107 includes a hoisting winch, a hoisting cable 124, and a load suspension device 125. The hoisting cable extends from the hoisting winch through a hoisting cable guide 125 located at the hoisting end of the boom 105 along the boom 105 to the load suspension device 126.

[0313] The boom pitch assembly 106 includes a boom pitch cable 117 and a boom pitch winch associated with the pitch cable 117. The boom pitch cable 117 extends from the boom pitch winch to the lifting 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 the lifting position relative to the crane structure 104.

[0314] Using the pitch system, the boom 105 of the crane 101 can pivot within the working area. The working area includes the range that allows the crane to control the position of the boom to lift the load.

[0315] According to the invention, the crane 101 includes a boom constraint 108 to reduce upward pivoting of the boom 105. According to a first aspect of the invention, the boom constraint 108 engages the boom 105 when the boom is pivoted to the top region. Therefore, when the boom 105 is in the top region, the boom 105 is engaged by the boom constraint 108, and when the boom 105 is lowered outside the top region, the boom constraint disengages from the boom.

[0316] The top region overlaps with the working area of ​​the crane. In the illustrated embodiment, when the boom 105 is in the top region, the angle between the boom 105 and the vertical axis of rotation 115 of the crane is in the range of 5 degrees to 25 degrees.

[0317] exist Figure 18 In the text, the crane 101 is described as having its boom 105 located at the lower end of the working area. Figure 19 In the text, boom 105 is described as being located at the upper end of the work area.

[0318] Figures 20 to 22 The hydraulic and pneumatic boom restraints 108 of the heavy-duty crane 101 in different working positions are shown in close-up.

[0319] Figure 20 The hydraulic pneumatic boom restraint 108 of the heavy-duty crane 101 is shown in close-up view, wherein the hydraulic pneumatic boom restraint 108 is not yet engaged with the boom 105 of the heavy-duty crane 101.

[0320] Figure 21 The hydraulic pneumatic boom restraint 108 of the heavy-duty crane 101 is shown in close detail, wherein the boom 105 is located at the lower end of the top region, and the hydraulic pneumatic boom restraint 108 engages the boom 105 of the heavy-duty crane 101.

[0321] Figure 22 The hydraulic-pneumatic boom restraint 108 of the heavy-duty crane 101 is shown in close detail, wherein the boom 105 is located at the upper end of the top region, and the hydraulic-pneumatic boom restraint 108 engages the boom of the heavy-duty crane.

[0322] Figures 18 to 22 The shown boom constraint and Figures 1 to 5 The rod constraint shown is similar.

[0323] In both embodiments, the boom restraint includes a hydraulic cylinder having a first member and a second member. In the illustrated embodiment, the first member is implemented as a piston body or cylinder body, and the second member is implemented as a piston rod or cylinder rod. The second member is telescopically received within the first member. The first member of the boom restraint is connected to the crane structure of the crane, while the second member is configured to engage the boom when it is in the top region.

[0324] exist Figures 18 to 22 In the illustrated embodiment, the first component of the hydraulic cylinder 127 (i.e., the piston body or cylinder body 118) is mounted on the bracket 110 of the crane 101, and the second component (i.e., the piston rod or cylinder rod 119, more specifically, the cylinder head 129) points towards the boom 105 of the crane 101. Furthermore, in both illustrated embodiments, the boom restraint 108 includes telescopic arms (i.e., hydraulic cylinders 127) located on both sides of the boom 105.

[0325] According to the invention, the boom restraint 108 includes a gas buffer 128 for each hydraulic cylinder 127. Each gas buffer 128 is mounted to the corresponding hydraulic cylinder 127 and connected to the hydraulic circuit of the corresponding hydraulic cylinder via a media separator. The gas buffer 128 forces the hydraulic cylinder 127 into an extended position. The volume ratio between the hydraulic cylinder 127 and the gas buffer 128 causes the hydraulic cylinder to act as a progressive spring. In the illustrated embodiment, each gas buffer 128 has a volume of 1200 liters, and each hydraulic cylinder 127 has a volume of 900 liters. Preferably, the volume ratio of the gas buffer to the associated hydraulic cylinder is 4:3.

[0326] The piston rod 119 of the hydraulic cylinder 127 includes a coupling element 120, implemented as a cylinder head in the illustrated embodiment, to engage the boom 105 when the boom 105 pivots to the top region.

[0327] In the illustrated embodiment, the boom 105 is provided with a catcher 121 for each hydraulic cylinder 127. Each catcher 121 is mounted on the boom 105 and configured to receive the cylinder head 120 of the corresponding hydraulic cylinder 127 to lock the cylinder head. In the illustrated embodiment, each catcher 121 pivotally locks the cylinder head relative to the boom as the boom pivots upward in the top region. This... Figure 21 The middle position shown is described.

[0328] The catcher 121 is configured to engage the coupling element 120 when the boom 105 is raised to the top region and the hydraulic cylinder 127 is in the extended position.

[0329] In the illustrated embodiment, the catcher 121 includes a guide surface 130 and a stop surface 131. When the boom 105 pivots toward the top region, the guide surface 130 engages with the cylinder head 120, and when the boom pivots to the top region, it guides the cylinder head toward the stop surface. The stop surface 131 is disposed at the end of the guide surface 130 to lock the cylinder head 120 relative to the boom 105. Figure 21 In the middle, the cylinder head is pivotally locked relative to the boom, such that a further torque of the boom 105 pushes the cylinder rod 119 into the cylinder body 118.

[0330] In the illustrated embodiment, the boom will be raised by 2 degrees to allow the cylinder head 120 to move along the guide surface and be locked by the catcher 121.

[0331] It is further noteworthy that, in the illustrated embodiment, the hydraulic cylinder 127 is pivotally supported, allowing it to pivot about a horizontal axis relative to the crane structure. The hydraulic cylinder pivots in the upward direction as the boom constraint engages the boom and the boom pivots upward.

[0332] As the boom pivots upward in the top region, the cylinder rod 119 retractably slides into the cylinder body 118 while the cylinder head 120 remains engaged with the catcher 121. Figure 19 and Figure 22 The boom constraint 108 is described when the boom 105 is in the 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 is located at the top of the top region when in the fully raised position. It is worth noting that in the illustrated embodiment, the boom is still at an angle to the vertical axis of rotation of the crane when in the fully raised position.

[0333] Under normal operating conditions, the boom constraint 108 is in passive mode. In this passive mode, the boom constraint 108 allows movement of the rod 119 relative to the cylinder body 118, thereby allowing movement of the boom 105 relative to the crane structure 104. In this mode, the hydraulic cylinder 127 allows the boom to pivot upwards.

[0334] The hydraulic cylinder is pressurized, causing it to be biased to the extended position. Furthermore, the gas damper of the hydraulic cylinder is configured to allow it to act as a progressive spring. When the boom restraints engage the boom in passive mode, the hydraulic cylinder allows the boom to pivot upwards, but does provide a reaction force, causing additional tension on the pitch cable.

[0335] The control system 109 of the boom restraint 108 includes sensors for monitoring load loss. In the illustrated embodiment, the sensors are configured to measure the movement of the boom rod within the cylinder. When the boom suddenly pivots upward due to load loss and / or ship roll, and the relative velocity of the boom rod exceeds a predetermined threshold, the control system switches the boom retainer to an active mode.

[0336] In active mode, the boom restraint activates one or more valves in the hydraulic circuit of the hydraulic cylinder to throttle the hydraulic fluid flowing towards the media separator. Therefore, movement of the boom is impeded, slowed, and preferably ultimately stopped, relative to the cylinder body, thereby slowing and preferably ultimately stopping movement of the boom 105 relative to the crane structure 104. Thus, in active mode, the hydraulic cylinder is hydraulically actuated to suppress any upward movement of the boom, preferably stopping any upward movement of the boom.

[0337] As described, the control system 109 is configured to switch the boom restraint 108 from a passive mode to an active mode when one or more sensors record load loss and / or ship roll. More specifically, the control system is configured to use a hydraulic circuit to slow down and / or stop the movement of the boom. Thus, in the event of load loss supported by the crane, when the boom is in the top region, the boom restraint 108 is configured to reduce (preferably prevent) the upward pivoting of the boom relative to the crane.

[0338] In the illustrated embodiment, the boom restraint 108 includes four hydraulic cylinders. The boom restraint also includes a hydraulic circuit and a gas damper coupled to each hydraulic cylinder.

[0339] It is worth noting that when the boom 105 pivots out of the top area, the connecting element 120 disengages from the catcher 121.

[0340] In the illustrated embodiment, the crane 101 is further provided with a boom stop 134. The boom stop 134 is configured to stop the boom when the boom 105 is at the upper end of the working area. In this position, the boom is also at the upper end of the top area, with its end at an angle of 5 degrees to the vertical pivot axis of the crane.

[0341] This invention can be summarized according to one or more of the following claims:

[0342] 1. A heavy-duty crane for use on a ship, said crane comprising:

[0343] - Base structure, wherein the base structure is suitable for installation on or integrally formed with a vessel;

[0344] - A crane structure, wherein the crane structure is rotatably supported by a base structure for rotation of the crane structure relative to the base about a vertical axis of rotation;

[0345] - A boom, preferably having a length of 80 to 200 meters, wherein the boom includes a longitudinal axis, a pivot end, a middle section and a lifting end opposite the pivot end, wherein the boom is supported by a crane structure so that the boom can rotate about a vertical axis of rotation, wherein the pivot end of the boom is pivotally connected to the crane structure so that the boom can pivot up and down about a horizontal boom pivot axis;

[0346] - A boom pitch assembly, wherein the pitch assembly includes a boom pitch cable and a boom pitch winch, wherein the boom pitch cable extends from the boom pitch winch to the lifting end of the boom for pivoting the boom up and down about a pivot axis and for supporting the boom in a lifting position relative to the crane structure;

[0347] - A lifting assembly for lifting a load, wherein the lifting assembly includes a lifting winch, a lifting cable and a load suspension device, wherein the lifting cable extends from the lifting winch through a lifting cable guide located at the lifting end of the boom to the load suspension device;

[0348] - A boom restraint for reducing (preferably preventing) upward pivoting of the boom when it is in the top region, wherein the angle between the boom and the vertical axis of rotation of the crane is 40 degrees or less, preferably 50 degrees or less, and most preferably 60 degrees or less, wherein the boom restraint comprises:

[0349] The first component is used to engage the crane structure or the tower of the crane when the boom is in the top region, preferably connected to the crane structure or the tower of the crane.

[0350] The second component is used to engage the boom when the boom is in the top region, and preferably is connected to the boom;

[0351] The control system includes one or more sensors for monitoring load loss (e.g., sensors for monitoring tension in hoisting cables and / or pitch cables) and / or one or more sensors for monitoring the ship's roll.

[0352] The boom constraint can switch between a passive mode and an active mode. In the passive mode, the boom constraint allows movement of the second member relative to the first member, thereby allowing movement of the boom relative to the crane structure or the crane tower. In the active mode, the boom constraint slows down and preferably prevents movement of the second member relative to the first member, thereby slowing down and preferably preventing movement of the boom relative to the crane structure or the crane tower.

[0353] The control system is configured to switch the boom restraints from passive to active mode when one or more sensors record load loss and / or ship roll.

[0354] 2. The heavy-duty crane according to claim 1, wherein the crane boom is pivotable in the working area, for example, in the working area the angle between the boom and the vertical axis of rotation of the crane is between 20 degrees and 100 degrees, wherein the top area overlaps with the working area.

[0355] 3. The heavy-duty crane according to claim 1 or claim 2, wherein the crane is further provided with a boom stop, wherein the boom stop is configured to prevent movement of the boom at a safe angle, the safe angle being the maximum height to which the boom can pivot, for example at the upper end of the working area.

[0356] 4. The heavy-duty crane according to claim 3, wherein the boom stop includes a compression region configured to slow down and preferably stop the boom by controlled deformation, for example when the boom moves beyond the maximum working angle, for example, beyond the upper end of the working area.

[0357] 5. The heavy-duty crane according to claim 3 or claim 4, wherein the boom stop includes a shock absorber, such as a hydraulic cylinder, which engages the boom before it reaches its maximum working angle to resiliently support the boom and prevent the boom from coming to a hard stop with the boom stop.

[0358] 6. The heavy-duty crane according to claim 5, wherein the boom stop includes a sensor, for example, in a shock absorber, for example, in the form of a hydraulic cylinder, the sensor being connected to a control system, wherein the control system is configured to prevent the pitch system from further raising the boom, thereby preventing the pitch system from pivoting the boom beyond the maximum working angle.

[0359] 7. The heavy-duty crane according to one or more of the preceding claims, wherein the crane structure is provided with one or more shock absorbers, the one or more shock absorbers being configured to engage the boom when the boom pivots beyond the maximum working angle, preferably engaging the impact area on the boom.

[0360] 8. The heavy-duty crane according to one or more of the preceding claims, wherein the boom is provided with one or more shock absorbers, the one or more shock absorbers being configured to engage the crane structure and / or the crane tower when the boom pivots beyond the maximum working angle, preferably engaging the impact area of ​​the crane structure or the crane tower.

[0361] 9. The heavy-duty crane according to one or more of the preceding claims, wherein the boom constraint includes a hydraulic cylinder, wherein the boom constraint is configured to maintain the hydraulic cylinder at a minimum pressure at least when the boom is in contact with the boom constraint, such that when the boom suddenly pivots in a downward direction, i.e., suddenly pivots away from the constraint, the constraint remains in contact with the boom.

[0362] 10. The heavy-duty crane according to one or more of the preceding claims, wherein the control system is configured to switch between slowing down the boom and stopping the boom movement, for example by partially and fully activating the brake calipers or hydraulic cylinders in the telescopic boom, respectively.

[0363] 11. The heavy-duty crane according to one or more of the preceding claims, wherein the boom constraint includes a compression region configured to slow and stop the boom by controlled deformation when the boom moves beyond a maximum pivoting speed.

[0364] 12. The heavy-duty crane according to claim 11, wherein the maximum pivoting speed is a speed that takes into account the angle at which the boom constraint switches to active mode, and is too high for the boom constraint to slow down the boom before it reaches its maximum working angle.

[0365] 13. The heavy-duty crane according to one or more of the preceding claims, wherein when the boom is lowered below the top region, the boom restraint can be disconnected from the crane and / or the boom, or wherein the first member can be moved away from the second member.

[0366] 14. The heavy-duty crane according to one or more of the preceding claims, wherein the control system is configured to slow down the movement of the boom in the upward and downward directions once switched to active mode.

[0367] 15. A heavy-duty crane according to one or more of the preceding claims, wherein the boom constraint includes a telescopic boom, the telescopic boom includes a first member and a second member, wherein the second member is telescopically received in the first member, wherein the first member is mounted on the crane structure or the crane tower, and the second member points toward the crane boom;

[0368] The second component includes a connecting element disposed on the second component of the telescopic boom for engaging the boom when the boom pivots to the top region, preferably engaging a catcher disposed on the boom. The second component is configured to retractably slide into the first component when the boom rotates to the top region.

[0369] The telescopic boom is also configured as follows:

[0370] When the boom is in the top region and the boom restraints are in passive mode, movement of the second member relative to the first member is permitted, thereby allowing movement of the boom relative to the crane structure or the crane tower.

[0371] When the boom is in the top region and the boom restraint is in active mode, the movement of the second member relative to the first member is slowed down and preferably prevented, for example by using brake pads or hydraulic fluid, thereby slowing down and preferably preventing the boom from tilting upward relative to the crane structure or the crane tower.

[0372] 16. The heavy-duty crane according to claim 15, wherein the telescopic boom includes at least one hydraulic cylinder and a hydraulic system coupled to the at least one hydraulic cylinder, wherein the at least one hydraulic cylinder is configured to move a second member relative to a first member in a linear direction, wherein the control system is configured to use the hydraulic system to slow down and / or stop the movement of the boom.

[0373] 17. A heavy-duty crane according to one or more of claims 1 to 14, wherein a first component has a receiving end and a second component has an inserting end, wherein the inserting end of the second component is configured to be at least partially inserted into the receiving end of the first component.

[0374] The first component is mounted on the crane structure with its receiving end facing the boom, and the second component is mounted on the boom with its insertion end facing the crane structure. When the boom pivots to the top region, the insertion end of the second component inserts into the receiving end of the first component. When the boom pivots upwards in the top region, the second component slides into the first component.

[0375] The first component is configured as follows:

[0376] When the boom is in the top region and the boom restraints are in passive mode, movement of the second member relative to the first member is permitted, thereby allowing movement of the boom relative to the crane structure or the crane tower.

[0377] When the boom is in the top region and the boom restraint is in active mode, the movement of the second member relative to the first member is slowed down and preferably prevented, for example by using brake pads, thereby slowing down and preferably preventing the boom from tilting upward relative to the crane structure or the crane tower.

[0378] 18. The heavy-duty crane according to claim 17, wherein the first component and / or the second component are respectively provided with fixing devices for engaging the second component or the first component, wherein the fixing devices can be activated by the control system to reduce movement of the first component relative to the second component, and preferably to stop movement of the first component relative to the second component.

[0379] 19. The heavy-duty crane according to claim 17 or claim 18, wherein the first component and / or the second component includes a fixing device implemented as a brake caliper, wherein the second component and / or the first component each include a brake plate configured to slide between the brake calipers of the first component and / or the second component when the boom is in the top region.

[0380] 20. A heavy-duty crane according to one or more of claims 1 to 14, wherein the second component includes a rail, wherein the rail is mounted on the boom and extends along the longitudinal axis of the boom, wherein the first component is an arm extending between a base end and a boom end, wherein the base end of the arm is pivotally mounted to the crane structure or the crane tower, and the boom end is configured to be slidably connected to the rail, wherein when the boom pivots upward in its top range, the arm and the boom end of the arm slide upward along the boom.

[0381] The first component is configured as follows:

[0382] When the boom is in the top region and the boom restraints are in passive mode, the boom end is allowed to slide along the track, thus allowing movement of the boom relative to the crane structure or the crane tower.

[0383] When the boom is in the top region and the boom restraints are in active mode, the movement of the boom end along the track is slowed down and preferably prevented, for example by using brake pads or a power cylinder, thereby slowing down and preferably preventing the boom from tilting relative to the crane structure or the crane tower in the upward direction.

[0384] 21. The heavy-duty crane according to claim 20, wherein the boom end is configured to engage a rail or a sliding element mounted on the rail when the boom is pivoted to the top region, and to disengage from the rail or the sliding element when the boom is pivoted downward out of the top region.

[0385] 22. The heavy-duty crane according to claim 20 or claim 21, wherein the first component is configured to engage a slider on a rail, such as a trolley, or to engage the rail slidably.

[0386] 23. The heavy-duty crane according to one or more of the preceding claims, wherein one end of the boom constraint is connected to the crane structure or the crane tower and is detachable from the crane and / or boom to achieve a larger angle between the boom and the crane structure.

[0387] 24. The heavy-duty crane according to claim 23, wherein the boom constraint is configured to engage the boom and the crane structure when the angle between the boom and the vertical axis of rotation of the crane is 40 degrees or less, preferably 50 degrees or less, and most preferably 60 degrees or less.

[0388] 25. The heavy-duty crane according to one or more of the preceding claims, wherein the boom restraint includes an interface that enables an operator to switch the boom restraint between a passive mode and an active mode.

[0389] 26. The heavy-duty crane according to one or more of the preceding claims, wherein the control system includes sensors for monitoring the angle of the boom and / or for detecting whether the boom is in the top region.

[0390] 27. The heavy-duty crane described in one or more of the preceding clauses, wherein the crane is a tower crane.

[0391] 28. The heavy-duty crane according to one or more of claims 1 to 26, wherein the crane is a pedestal crane, the crane structure includes a support for supporting the pitch cable, wherein the boom restraint is preferably mounted on the support.

[0392] 29. A marine crane vessel equipped with one or more heavy-duty cranes as described in the preceding paragraph.

[0393] 30. A method for stopping the upward pivoting movement of a boom, the boom moving in a top region, the method utilizing one or more heavy-duty cranes according to claims 1 to 26 or a vessel according to claim 29, wherein the method comprises the following steps:

[0394] Increase the load and raise the boom to the top area;

[0395] Detect load loss;

[0396] Switch the boom constraint from passive mode to active mode;

[0397] Join the second component to the first component;

[0398] This slows down the movement of the second component relative to the first component, thereby slowing down the movement of the boom relative to the crane structure or the crane tower.

[0399] This stops the movement of the second component relative to the first component, thereby stopping the movement of the boom relative to the crane structure or the crane tower.

[0400] Figure Labels

[0401] 01: Heavy-duty crane

[0402] 02: Tower

[0403] 03: Base Structure

[0404] 04: Crane Structure

[0405] 05: Hanger rod

[0406] 06: Boom pitch assembly

[0407] 07: Lifting Components

[0408] 08: Hanger rod restraints

[0409] 09: Control System

[0410] 10: Tower crane tower

[0411] 11: Longitudinal axis of the boom

[0412] 12: Pivot end of the boom

[0413] 13: Middle section of the boom

[0414] 14: Lifting end of the boom

[0415] 15: Vertical axis of rotation of the crane

[0416] 16: Borehole pivot axis

[0417] 17: Cable for boom tilting

[0418] 18: First component of the boom constraint; 118A: Base end arm; 118B: Boom end arm; 19: Second component of the boom constraint.

[0419] 20: Connecting elements

[0420] 21: Capturer

[0421] 22: Brake plate

[0422] 23: Borehole stop

[0423] 101: Heavy-duty crane

[0424] 102: Base

[0425] 103: Base Structure

[0426] 104: Crane Structure

[0427] 105: Hanger rod

[0428] 106: Boom pitch assembly

[0429] 107: Lifting Components

[0430] 108: Hanger rod restraints

[0431] 109: Control System

[0432] 110: Bracket

[0433] 111: Longitudinal axis of the boom

[0434] 112: Pivot end of the boom

[0435] 113: Middle section of the boom

[0436] 114: Lifting end of the boom

[0437] 115: Vertical axis of rotation of the crane

[0438] 116: Borehole pivot axis

[0439] 117: Pole elevation cable

[0440] 118: Piston body of a hydraulic cylinder

[0441] 119: Piston rod of hydraulic cylinder

[0442] 120: Connecting element / cylinder head

[0443] 121: The Capturer

[0444] 122: Track 123:

[0446] 124: Lifting cable

[0447] 125: Cable guide for hoisting device

[0448] 126: Load suspension device

[0449] 127: Hydraulic cylinder

[0450] 128: Gas Buffer

[0451] 129: Cylinder head

[0452] 130: Guide surface of the catcher

[0453] 131: The blocking surface of the catcher

[0454] 132: Control System

[0455] 133: Sensor Control System

[0456] 300: Ships

[0457] 301: Crane

[0458] 302: Floating body

Claims

1. A heavy-duty crane for use on a ship, said crane comprising: - Base structure, wherein the base structure is suitable for installation on or integrally formed with a vessel; - A crane structure, wherein the crane structure is rotatably supported by a base structure for rotation of the crane structure relative to the base structure about a vertical axis of rotation; - A boom, wherein the boom includes a longitudinal axis, a pivot end, a middle section and a lifting end opposite to the pivot end, wherein the boom is supported by a crane structure so that the boom can rotate about a vertical axis of rotation, wherein the pivot end of the boom is pivotally connected to the crane structure so that the boom can pivot up and down about a horizontal boom pivot axis; - A boom pitch assembly, wherein the pitch assembly includes a boom pitch cable and a boom pitch winch, wherein the boom pitch cable extends from the boom pitch winch to the lifting end of the boom for pivoting the boom upward and downward about the boom pivot axis and for supporting the boom in the lifting position relative to the crane structure; The pitching assembly is capable of pivoting the boom to a top region that covers an angle of at least 16 degrees relative to the crane’s vertical axis of rotation. - A lifting assembly for lifting a load, wherein the lifting assembly includes a lifting winch, a lifting cable and a load suspension device, wherein the lifting cable extends from the lifting winch through a lifting cable guide located at the lifting end of the boom to the load suspension device; - A hydraulic-pneumatic boom restraint, wherein when the boom pivots to the top region, the boom restraint engages the boom to reduce upward pivoting of the boom when it is in the top region, wherein the boom restraint comprises: Multiple hydraulic cylinders, each having a hydraulic circuit and a cylinder rod, include one or more valves that allow free flow of hydraulic fluid when the boom constraint is in a passive mode, and throttle the flow of hydraulic fluid when the boom constraint is in an active mode. The cylinder rod has a cylinder head, wherein the hydraulic cylinders are mounted on the crane structure, and the cylinder heads point towards the crane's boom. Each capture device corresponds to a hydraulic cylinder, wherein each capture device is mounted on the boom and configured to receive the cylinder head of the corresponding hydraulic cylinder, and each capture device is configured to lock the cylinder head relative to the boom when the boom pivots upward in the top region; A gas damper is used for each hydraulic cylinder, wherein each gas damper is mounted to the corresponding hydraulic cylinder and connected to the hydraulic circuit of the corresponding hydraulic cylinder via a media separator, wherein the gas damper forces the hydraulic cylinder into an extended position, and wherein the volume ratio between the hydraulic cylinder and the gas damper causes the hydraulic cylinder to act as a progressive spring; and The control system includes one or more sensors for monitoring load loss and / or one or more sensors for monitoring the ship's roll; The boom constraint can switch between a passive mode and an active mode. In the passive mode, the boom constraint allows movement of the boom in the corresponding hydraulic cylinder, thereby allowing movement of the boom relative to the crane structure or the crane tower in the top region. In the active mode, the boom constraint (108) slows down and prevents movement of the boom in the corresponding hydraulic cylinder, thereby slowing down and preventing movement of the boom relative to the crane structure or the crane tower in the top region. The control system is configured to, when one or more sensors record load loss and / or ship roll, throttle the flow of hydraulic fluid by activating one or more valves in the hydraulic circuit of the corresponding hydraulic cylinder to slow down and ultimately prevent the movement of the cylinder rod relative to the cylinder body, thereby slowing down and ultimately hindering the movement of the boom relative to the crane structure, and switching the boom constraint from passive mode to active mode.

2. The heavy-duty crane according to claim 1, wherein, In the top area, the angle between the boom and the crane's vertical axis of rotation is within the range of 0 to 30 degrees. The crane's boom is capable of pivoting within the working area, where the angle between the boom and the crane's vertical axis of rotation is between 20 and 100 degrees, and the top area overlaps with the working area.

3. The heavy-duty crane according to claim 1, wherein, The crane is also equipped with a boom stop, which is configured to prevent the boom from moving at a safe angle. The safe angle is the maximum height to which the boom can pivot. The boom stop includes a compression area configured to slow down and stop the boom through controlled deformation.

4. The heavy-duty crane according to claim 3, wherein, The boom stop includes a shock absorber that engages the boom before it reaches its maximum working angle to resiliently support the boom and prevent a hard stop between the boom and the boom stop.

5. The heavy-duty crane according to claim 4, wherein, The boom stop includes a sensor connected to a control system configured to prevent the pitch system from further raising the boom, thereby preventing the pitch system from pivoting the boom beyond its maximum working angle.

6. The heavy-duty crane according to claim 1, in, The boom constraint is configured to maintain the hydraulic cylinder at minimum pressure at least when the boom is in contact with the boom constraint, such that when the boom suddenly pivots in the downward direction, i.e., when it suddenly pivots away from the constraint, the constraint remains in contact with the boom.

7. The heavy-duty crane according to claim 1, wherein, The boom constraint includes a compression region configured to slow down and stop the boom through controlled deformation when the boom moves beyond its maximum pivoting speed.

8. The heavy-duty crane according to claim 1, wherein, The hydraulic circuits of multiple hydraulic cylinders are connected to balance the load difference between the hydraulic cylinders.

9. The heavy-duty crane according to claim 1, wherein, As the boom pivots upward in the top area, the hydraulic cylinder is compressed, and the hydraulic cylinder tauts the pitch cable.

10. The heavy-duty crane according to claim 1, wherein, The cylinder rod of the boom constraint is fully extended when it is engaged with the boom and the angle between the boom and the vertical axis of rotation is 35 degrees.

11. The heavy-duty crane according to claim 1, wherein, The cylinder rod of the boom constraint is fully retracted when the angle between the boom and the vertical axis of rotation is 15 degrees.

12. The heavy-duty crane according to claim 1, wherein, The boom is an A-frame boom, and the boom constraint includes four hydraulic cylinders, which are mounted such that each hydraulic cylinder engages one side of the A-frame leg.

13. The heavy-duty crane according to claim 1, wherein, The boom includes a box-shaped frame at the base end, and a catcher corresponding to the hydraulic cylinder is mounted on the box-shaped frame.

14. The heavy-duty crane according to claim 1, wherein, The hydraulic cylinder is pivotally supported, allowing it to pivot about a horizontal axis relative to the crane structure.

15. The heavy-duty crane according to claim 1, wherein, The support frame is an A-frame, and two hydraulic cylinders are installed on each leg of the A-frame.

16. The heavy-duty crane according to claim 1, wherein, The catcher includes a guide surface and a stop surface, wherein the guide surface engages the cylinder head as the boom pivots toward the top region and guides the cylinder head toward the stop surface as the boom pivots further toward the top region, wherein the stop surface is positioned at the end of the guide surface to lock the cylinder head relative to the boom, such that further torque of the boom pushes the cylinder rod into the hydraulic cylinder.

17. The heavy-duty crane according to claim 1, wherein, The control system includes sensors for monitoring the angle of the boom and / or for detecting whether the boom is in the top area.

18. A marine crane vessel equipped with a heavy-duty crane according to any one of the preceding claims.

19. A hydraulic-pneumatic boom restraint configured for mounting on a heavy-duty crane to provide the heavy-duty crane according to claim 1.

20. A method for stopping the upward pivoting movement of a boom, the boom moving in a top region, said method utilizing a heavy-duty crane according to claim 1 or a vessel according to claim 18, wherein, The method includes the following steps: Raise the boom to the top area and engage the boom with the boom restraints; Use a crane to lift the load; Detect load loss; Switch the boom constraint from passive mode to active mode; This slows down the movement of the cylinder rod in the corresponding hydraulic cylinder, thereby slowing down the movement of the boom relative to the crane structure or the crane tower. This stops the movement of the cylinder rod in the corresponding hydraulic cylinder, thereby stopping the movement of the boom relative to the crane structure or the crane tower.

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