(HEAVE) BALANCING DEVICE, HOISTING SYSTEM, METHOD FOR HOISTING AND KIT OF PARTS FOR SPRING BALANCING A HOISTING SYSTEM

Abstract

Heave balance device (1) can balance a lifted or supported load (8). The load can be lifted by a hoisting device (10) or it can be supported. The heave balance device comprises a first frame (2) and a connection unit (22) that can be suspended, e.g. to a hoisting device. Further a moveable carrying unit (32) allows for carrying (suspending or supporting) a load. The device comprises a transmission that couples the connection unit and carrying unit, wherein said transmission is arranged to guide the connection unit and the carrying unit to move along a guideline with respect to each other, the transmission having a spring force balancing arrangement (4) with one or more leverage units, such as one or more pivoting arms (50, 51), and with one or more configurable (gas- or) hydropneumatic springs. A method comprises suspending the load via a (heave) balance device. Further a kit of parts for hoisting devices is provided to allow load decoupling.

Claims

1. A (heave) balancing device for balancing a load, comprising: a first frame; a connection unit that can be supported; a moveable carrying unit for carrying a load; and a transmission that couples the connection unit and carrying unit, wherein said transmission is arranged to guide the connection unit and the carrying unit to move along a guideline with respect to each other, the transmission having a spring force balancing arrangement with one or more leverage units, such as one or more pivoting arms, and with one or more configurable gas- or hydro-pneumatic springs.

2. A device according to claim 1, wherein the gas- or hydro-pneumatic spring is arranged to apply the force at a first point of application on the first frame or on the leverage unit, and a second point of application on the first frame or on the leverage unit, and said gas- or hydro-pneumatic spring pivots with respect to the guideline around at least one of said points of application during: extension or contraction of the gas- or hydro-pneumatic spring, and/or movement of the leverage unit relative to the gas- or hydro-pneumatic spring, connection unit and/or carrying unit, and/or movement of the connection unit relative to the carrying unit.

3. A device according to claim 1, wherein the gas- or hydro-pneumatic spring is arranged to apply the force at a first point of application on the first frame or on the leverage unit, and a second point of application on the first frame or on the leverage unit, wherein a point of the leverage unit, the first point of application and the second point of application define a triangle having an area correlated with the torque applied on the carrying unit.

4. A device according to claim 1, wherein a second frame connects the carrying unit to the transmission, the leverage unit is formed by an arm and the transmission comprises at least two pivoting arms that have pivoting points.

5. A device according to claim 1, wherein the transmission comprises a linear guide for guiding the first frame with respect to the second frame; and/or the transmission comprises one or more moveable pivot point, one or more extendable arms; and/or the transmission comprises at least two configurable gas- or hydro-pneumatic springs.

6. A device according to claim 1, wherein the configurable gas- or hydro-pneumatic spring is positioned not-in-line with the guideline; and/or the configurable gas- or hydro-pneumatic spring pivotably connects the first and second frames, and/or the configurable gas- or hydro-pneumatic spring is positioned between one of the frames and the pivoting arm; and/or the configurable gas- or hydro-pneumatic spring is positioned on different arms of the transmission.

7. A device according to claim 1, wherein the leverage unit is arranged to, at different extension of the gas- or hydro-pneumatic spring, convert the spring force onto the load with different multipliers, and wherein the leverage unit comprises a rotating element having a thread with a variable pitch; and/or the gas- or hydro-pneumatic spring pivotably arranged between first and second frame.

8. A device according to claim 1, wherein the transmission further has an actuator.

9. A device according to claim 1, wherein the transmission allows the frames to move in a domain, the domain having a first boundary and a second boundary, wherein the transmission further has security arrangement that is arranged to bias the transmission from not reaching the first and/or second boundary.

10. A hoisting device for balancing a load lifted comprising: a hoisting line connected to the hoisting device; a connection unit suspended to the hoisting line; a transmission coupled to the connection unit, the transmission having a spring force balancing arrangement with one or more pivoting arms and with one or more configurable gas- or hydro-pneumatic springs, a load carrying unit connected to the transmission, which can carry or support the load.

11. A hoisting device according to claim 9, comprising an actuator coupled to the transmission.

12. A method for carrying a load with a hoisting device, the method comprising: connecting a connecting unit of a heave balancing device according to claim 1 to the hoisting line of the hoisting device; carrying a load by connecting a load to the carrying unit of the heave balancing device; configuring the gas- or hydro-pneumatic spring to the load.

13. Method for carrying a load by a hoisting device by hoisting the load via a transmission that has a pivoting arm and configurable gas- or hydro-pneumatic spring, the transmission coupling the load by spring balance to the hoist.

14. Method according to claim 12, further comprising, dependent on the load and/or dependent on the non-linear behavior of the gas or hydro pneumatic spring in operation and/or to secure safe operation of the hoisting device: configuring the gas- or hydro-pneumatic spring to the load; and/or positioning of one or more pivoting points in the transmission; and/or extending one or more arms of the transmission; and/or actuating the one or more actuators.

15. (canceled)

16. (canceled)

17. A device according to claim 4, wherein: the first and second frames extend generally along the guideline and the pivoting arms extend on opposite sides of that guideline; and/or the pivoting points positioned generally symmetrically around the guideline; and/or wherein the two arms are connected by a pivoting point to the first and second frame respectively.

18. A device according to claim 5, wherein the transmission comprises one or more extendable pivoting arms; and/or the transmission comprises at least two configurable gas- or hydro-pneumatic springs, wherein each of the gas springs is connected via a pivoting point to the first or the second frame and to a pivoting point on the arms of the transmission.

19. A device according to claim 7, wherein the leverage unit comprises a rotating element having a thread with a variable pitch, wherein the gas- or hydro-pneumatic spring is connected to the rotating element and is also connected to the first or second frame.

20. A device according to claim 8, wherein: the actuator is connected to the leverage unit; and/or the actuator is connected to one of the frames; and/or the actuator is connected to two arms of the transmission; and/or the actuator is arranged to provide a compensating force to compensate for spring balance deviations as a result of non-perfect gas- or hydro-pneumatic spring behavior; and/or the actuator is arranged to drive the transmission; and/or the actuator is arranged to act on the cylinder of the gas- or hydro-pneumatic spring in the opposite direction of the force of the gas of the gas- or hydro-pneumatic spring; and/or the actuator is driven by a control system which receives signals from a motion reference unit; and/or the actuator is a throttle valve of the gas- or hydro-pneumatic spring, controlling the flow of the oil between the piston of the cylinder and the gas volume and/or the flow of the gas.

21. A device according to claim 9, wherein the security arrangement comprises one or more springs; and/or the security arrangement comprises one or more actuators; and/or the first, second or both boundaries are extremities of the movement by the transmission; and/or the security arrangement comprises a toothed track on one of the frames; and/or the security arrangement comprises a unit for controlling the configurable gas- or hydro-pneumatic spring; and/or the security arrangement is arranged to increase the return force when the transmission has moved at least 50% from a default or middle position toward one of the boundary positions.

22. Method according to claim 13, further comprising, dependent on the load and/or dependent on the non-linear behavior of the gas- or hydro-pneumatic spring in operation and/or to secure safe operation of the hoisting device: configuring the gas- or hydro-pneumatic spring to the load; and/or positioning of one or more pivoting points in the transmission; and/or extending one or more arms of the transmission; and/or actuating the one or more actuators.

Description

[0063] Although the drawings show several embodiments, the invention is not limited to the shown embodiments.

[0064] FIG. 1 shows a schematic hoisting device with heave balancing device according to a first embodiment with a rhombus arm arrangement.

[0065] FIG. 1a shows a schematic hoisting device with heave balancing device according to a second embodiment with an actuator placed onboard the hoisting device.

[0066] FIG. 1b shows another schematic hoisting device with heave balancing device according to a third embodiment having a double rhombus arm arrangement.

[0067] FIG. 1c-e show a schematic hoisting device with heave balancing device according to a first embodiment with a rhombus arm arrangement, in various situations.

[0068] FIG. 1f shows a schematic heave balancing device incorporated in a hoisting device according to an embodiment.

[0069] FIG. 1g shows a schematic heave balancing device according to an embodiment.

[0070] FIGS. 2a-d show prior art embodiments.

[0071] FIG. 3 shows a schematic heave balancing device according to a 4.sup.th embodiment in more detail.

[0072] FIG. 4a shows the schematic heave balancing device of FIG. 3 in a different position.

[0073] FIG. 4b shows the schematic heave balancing device of FIG. 4a in a different position.

[0074] FIG. 5 shows a schematic hoisting device with heave balancing device according to a 5.sup.th embodiment with a single extension spring.

[0075] FIG. 6a shows another schematic hoisting device with heave balancing device according to a 6.sup.th embodiment with a single compression spring engaged as an extension spring.

[0076] FIG. 6b shows a schematic hoisting device with heave balancing device according to a 7.sup.th embodiment with a single extension spring having connection points on the arms.

[0077] FIG. 6c shows a schematic heave balancing device according to a 8.sup.th embodiment comprising two compression springs.

[0078] FIG. 6d shows a schematic hoisting device with heave balancing device according to a 9.sup.th embodiment with two compression springs and two rhombus arm arrangement.

[0079] FIG. 6e shows a schematic hoisting device with heave balancing device according to a 10.sup.th embodiment, wherein the leverage unit is formed by a rotating element.

[0080] FIG. 1 shows an embodiment of a heave balancing device 1 according to an aspect of the invention. The heave balancing device 1 is lifted by a hoisting line 9, formed by a wire. In this embodiment, heave balancing device 1 is lifted by a crane or hoisting device 10 mounted on a floating vessel 11. Although in this application a crane 10 is used to illustrate the invention, clearly any kind of support structure on a heaving ship can be used. In this embodiment, the heave balancing device is positioned to replace a part of the hoisting line 9.

[0081] The heave balancing device 1 will transform an existing non-spring-balanced crane, in this case a crane 12 on a vessel 11, into a crane that operates using balanced heave compensation. The heave balancing device 1 of this embodiment allows to add a balanced heave compensation feature to existing high-load cranes without having to make costly adaptations to the existing crane equipment. In this case the heave balancing device is connected to the system (vessel 11) that experiences heaving.

[0082] The heave balancing device could also be connected and disconnected to any type of mechanical support or suspension system which is mounted on the ground or for example onto an off-shore platform as illustrated in FIG. 1d.

[0083] In this application a heave balancing device 1 can be a device that balances a load at different positions or can be a device that generally balances the load, preferably by spring loaded means. Embodiments of the heave balancing device comprise balancing a load at different positions of the heave balancing device, the balancing force being provided for the most part by spring loaded means, preferably (gas- or) hydro-pneumatic spring systems. Preferably loads of over 10 tons, preferably over 20 tons, and more preferably over 30 tons are supported and balanced using a heave balancing device 1.

[0084] In FIG. 1, the heave balancing device 1 has a connection unit 22 that connects to the drive element 9 of the hoisting device. The connection unit 22 is a ring, which forms an integral part of a first frame 2. Further a carrying unit 32, also formed by a ring, is connected to the load. The carrying unit 32 is an integral part of a second frame 3. The frames 2 and 3 can move with respect to each other. In this embodiment, the transmission comprises a guide, preferably linear, for guiding the movement of frames 2 and 3 with respect to each other. In the embodiment, the hoisting point and load carrying point will be arranged on a vertical line and the guide allows movement along this vertical line.

[0085] In the embodiment, the transmission, comprising the guide, allows moving connection unit 22 with respect to carrying unit 32 by increasing or reducing the distance, indicated by an arrow 28, between those two suspension points 22,32. In balanced operation the suspension points are oriented along the vertical line, here the guideline 208. Preferably the transmission comprises one or more arms for transferring forces between the suspension points, the arm being positioned non-parallel, preferably at an angle between 10-170 degrees, with respect to the guideline 208/the direction of the guide. In use the arms are at an angle with the vertical direction. Preferably one or more arms are pivotable with respect to a first frame 2 or second frame 3.

[0086] Preferably the heave balancing device 1 comprises at least one transmission having a leverage unit 50,51 and a pneumatic spring 4. The leverage unit is preferably a linear leverage unit and more preferably a pivoting arm 50,51. The pivoting arm is connected to one of the frames 2,3 or to both. The spring 4 is preferably a gas or hydro-pneumatic spring. In this embodiment the arms 50,51 and the spring 4 are connected to the first frame by means of a pivoting connection point. The pneumatic spring and the leverage unit cooperate to result in an upward force that is generally constant over the stroke of the pneumatic spring. The leverage unit and spring are therefore arranged in a spring balance configuration. Preferably, the spring approximates perfect (Hooke's law) behavior, where the spring force is linear to the stroke. In combination with a pivoting arm, this results in a spring balanced system.

[0087] In this embodiment the leverage unit and the pneumatic spring art part of the spring force balancing arrangement. In embodiments the spring force balancing arrangement is arranged to compensate for changes in the load. Examples of compensating for change in the load are allowing, in operation, moving of the pivoting point of the arm, thereby changing the length of the arm of the applied force. Another embodiment can have an arm that has a variable length.

[0088] Alternatively, other systems which perform a similar balancing function (for example 4 armed (hydro-pneumatic systems or systems with a single (hydro) pneumatic spring) can also be used. Further examples of other possible balancing systems are also provided (FIG. 6a-e). Alternatively, the heave balancing device 1 comprises a transmission having a rotating member with both a fixed and a variable pitch. Alternatively, the spring itself is the transmission, by way of a changing angle when the position of the load changes.

[0089] In FIG. 1, the transmission couples the connection unit 22 to the carrying unit 32, preferably by coupling the first frame 2 to the second frame 3. In FIG. 1 the transmission of the heave balancing device 1 has two leverage units in the form of arm assemblies 50,51, each comprising two pivoting arms connected by pivoting points. The two arm assemblies together form a rhombus arm arrangement. The arm assemblies 50, 51 allowing pivoting of one or more arms. In this embodiment, a double (gas- or) hydro-pneumatic spring system 4 is provided. In this embodiment, each arm assemblies 50,51 has a (gas- or) hydro-pneumatic spring system 4. The (gas- or hydro)-pneumatic spring system 4 is configurable. It comprises a gas volume that is connected to the spring by a valve system. By filling or unloading gas from the cylinder, or by changing the amount of oil between the gas and the cylinder, the gas pressure can be increased and decreased. This allows configuring the spring force. A (gas- or) hydro-pneumatic spring may have behavior close to a linear spring constant.

[0090] In the shown embodiment the heave balancing device 1 includes an actuator 5. The actuator 5 can provide a force additional to the spring-loaded means. The additional force can compensate for non-linear behavior of the spring-loaded means or can provide a force for biasing the load towards a default position of the heave balancing device. The additional force can also bring about movement of the first and second frame, thereby lifting/lowering the load in the vertical direction. In the shown embodiment the actuator is connected to the first and second frame. Actuation results in direct movement of the first frame with respect to the second frame, while the transmission is also moved.

[0091] In embodiments of the heave balancing device according to the invention, movement of the ship along the z-axis is compensated by use of the spring balancing arrangement that is part of the transmission. The heave balancing device 1 comprises the spring or arm. The heave balancing device will have a state in which the spring is connected not-in-line with the load, in such a way that a change in the position of the load does not change the elongation of the spring along a linear characteristic. The spring is configured in such a way that a change in the force of the spring is (substantially) counteracted by the transmission, in particular the leverage unit. According to the invention the leverage unit and pneumatic spring are arranged to provide a torque to generally balance a torque provided by the load. In embodiments the load is, additional to being compensated for heaving motions by the heave balancing device 1, held by towlines to control the movement of the load in the X and Y directions (perpendicular to the Z-position that is balanced) or other conventional means to control the movement of the load in the X and Y directions such as actuation of the tip of the crane.

[0092] The heave balancing device 1 allows movement of the ship 11 in the z-direction to be compensated. The heave balancing device according to the invention will result in the load remaining generally at the same (absolute) height during heaving (and/or rolling or pitching) motions, as shown in FIGS. 2a and 2b.

[0093] FIG. 1a shows a very similar embodiment as the embodiment of FIG. 1. However, in figure la the actuator 512 is positioned on the hoisting device 10. A line 513 connects the actuator 512, here embodied by a actuated reel, to frames 3 or directly to the load 8, here a connection 514 on second frame 3. The embodiment of FIG. 1a generally provides the same operation as FIG. 1, but shows that the actuator can be separate from the heave balancing device. This has the benefit the part of the heave balancing device hoisted under line 9 can be relatively small.

[0094] In embodiment the position of the ship the load of the heave balancing device 1 is monitored controlled. On the basis of the measured data an actuator can adjusts a tool (for example, a winch, a pneumatic arm system) accordingly. Preferably the monitoring and control system comprises a motion reference unit which is preferably located within the heave balancing device.

[0095] In FIG. 1b, a transmission is shown comprising four arm assemblies. Two arm assemblies 63,64 are shown in the front view forming a rhombus arrangement. A second pair of arm assemblies of which one arm assembly 65 is visible in the front view is arranged similarly in a rhombus arrangement. This embodiment with two sets of arm assemblies has two rhombus arm arrangements. In this set up four (hydro) pneumatic springs are arranged to provide a balancing force. The four (hydro) pneumatic springs are connected between first frame 2 and the force guiding and pivoting points on the four arm assemblies. This embodiment has the benefit the heave balancing device can be stronger in order to balance larger loads. Embodiments with three or more rhombus arm arrangements are possible in order to balance very heavy loads.

[0096] The load may have a targeted landing site 800. FIG. 1c shows an embodiment of the heave balancing device 1 of FIG. 1, wherein the targeted landing site 800 is a platform under sea level. In FIG. 1d, the targeted landing site 800 is on a vessel, and the hoisting device 10 is provided on a platform 11. In FIG. 1e, the targeted landing site 800 is on a vessel, and the hoisting device is provided on another vessel 11.

[0097] FIG. 1c shows the heave balancing device 1 of FIG. 1 with additional sensors 100-105. Here, sensors can include active and passive elements, e.g. a mirror. Sensors 100-105 are disposed at various locations on and around the illustrated system, such as sensor 100 on the first frame 2, sensor 101 on the load 8, sensor 102 on the targeted landing site 800, sensor 103 at the tip of the crane 10, device location 104 at the base of the hoisting device 10, sensor 105 on the vessel 11. These sensors may be for example motion sensors or position sensors, including distance meters, motion reference units, GPS devices, etc.. The information provided by the sensors can allow for active compensation if needed.

[0098] FIG. 1d shows a different possibility of employing the heave balancing device 1 of FIG. 1. Here, the targeted landing site 800 is on a vessel, and the hoisting device 10 is provided on a platform 11. Again, various measuring sensors 100-105 may be employed at various points similar to FIG. 1c. As the vessel heaves 12, the load is moved vertically together with the vessel allowing onboarding or deloading of the load despite the heaving.

[0099] FIG. 1e shows a further possibility of employing the heave balancing device 1 of FIG. 1. Herein, the load 8 is transported to a targeted landing site 800 on a vessel, while the hoisting device is disposed on another vessel 11.

[0100] FIG. 1f shows an embodiment of the heave balancing device 1 being incorporated within the hoisting device 10 on the vessel. In this embodiment, the heave balancing device 1 is fully integrated within the crane 10. In this embodiment, the device 1 is turned upside down when compared with the embodiments of FIGS. 1-1e. Connection unit 22 is positioned, preferably attached, to the floor of the crane 10. Carrying unit 32 comprises a pulley illustrated schematically. The pulley will experience an upward force as a result of the heave balancing device 1. The load 8 is suspended from a line, and the line is lead over the pulley, which can move up and down 28. When the pulley of the heave balancing device 1 moves down, the load 8 can move downwards relative to the tip of the crane 10. When the pulley moves up, the load 8 is also pulled up relative to the crane 10. Once the springs of the heave balancing unit 1 of FIG. 1f are configured to the actual load 8, the heave balancing unit 1 can provide decoupling by generally spring balancing at multiple angles of the arms with respect to the frame of the heave balancing device 1. A benefit of this embodiment is the maximum hoisting height of the crane is not affected by the heave balancing device 1 between the crane hook and the load. In this embodiment, in comparison with the embodiments of FIGS. 1-1e, the heave balancing device is to be designed to allow a longer stroke, as a result of the hoisting line being guided at an angle, here about 45 degrees. Also not the full weight of the load 8 is carried by the heave balancing unit 1 in this set-up, allowing the design of a less rigid device 1 in comparison with FIGS. 1-1e.

[0101] FIG. 1g shows an embodiment of two or more heave balancing devices 1 being used to balance a load 8 on a vessel 11 by providing a balanced upward pushing force. Also in this embodiment, the heave balancing devices 1 are sandwiched between the load 8 and the support 11 transferring the forces between opposite side of the heave balancing device 1. The carrying unit 32 preferably makes a small, point contact with the load 8. The connection unit 22 is supported, e.g. directly attached, to the floor of the vessel. The two or more heave balancing devices 1 compensate the heaving motion 12 of vessel 11, such that the load 8 stays substantially at the same height and substantially horizontal. There may be more than two devices, like for example three devices in a triangular configuration.

[0102] FIG. 3 shows a more detailed embodiment of heave balancing device 1. The heave balancing device 1 comprises a first frame 2 having a connection unit 22 for suspension to a hoisting device. The heave balancing device 1 further comprises a second frame 3 having a carrying unit 32 for suspending or supporting a load. The first frame 2 and second frame 3 move with respect to each other along a linear guideline 209, said linear guide provided by a transmission. Preferably the connection unit 22 and/or the carrying unit 32 are positioned on the guideline 209. Preferably, in operation, the guideline 209 is generally parallel to the gravitational force, although in some embodiments, as result of heaving, this can change.

[0103] The transmission has one or more force application points, such as pivot connections 41, preferably outside linear guideline 209, preferably arranged symmetrically around the guideline. Force application points are preferably arranged so the force field is guided symmetrical around the guideline. Preferably forces transmitted through said one or more force application points are not in line with, that is non-parallel to, the guideline 209. Preferably the orientation of the (hydro-)pneumatic spring 4 said forces change when frames 2 and 3 move with respect to each other and/or when the distance between the connection unit and the carrying unit changes.

[0104] In this embodiment, the transmission comprises two leverage units in the form of arms assemblies 50, 51. Arm assemblies 50,51 work simultaneously and identically, thus for clarity's sake, the mechanical parts are labelled on the left-hand side and the virtual construction lines and forces are shown on the right-hand side of FIG. 3. Left hand arm assembly 50 comprises an arm part 7 and a balancer arm 6. Arms 6,7 are connected to each other via a pivoting point 41. In the embodiment shown in FIG. 3, a force guiding point is pivoting point 41.

[0105] The heave balancing device 1 comprises a first frame 2. On the frame engagement points are provided. Engagement point 21 is a pivot point that allows pivoting of arm 7. Engagement point 22 is a connection unit for suspension to a hoisting device.

[0106] Through pivot point 21 and pivot point 31, a virtual construction line 205 along the z axis and parallel to the guideline 209 can be constructed, along the direction of the lifting force of first frame 2 on first arm part 7, and along the direction of movement of pivot point 21 with respect to second frame 3.

[0107] The (hydro) pneumatic spring system 4 is connected to first frame 2 via pivoting connection point 42. The (hydro) pneumatic spring system 4 comprises a cylinder 401, a hydraulic connection 402 and a hydraulic accumulator 403. The (hydro) pneumatic spring system can be configured. The system 4 allows setting the spring force of the (hydro) pneumatic cylinder 401. One chamber of cylinder 401 may be connected to a hydraulic accumulator and will have a relatively high pressure of up to 300 bar or even 600 bar, the other chamber on the opposite side of the piston of cylinder 401, chamber 43, may have a limited, relatively low pressure, for example 1-10 bar at minimum compression of the spring. When compressed, the gas pressure in the chamber with relatively low pressure increases. This helps to prevent the heave balancing device to suddenly reach end of stroke and it allows for better balance given the non-linear and adiabatic characteristics of a gas spring.

[0108] First frame 2 comprises a guide that guides a second frame 3. The second frame 3 is guided in a direction along the z-axis and parallel to guideline 209, allowing for the hoist connection point and the load connection point to move with respect to each other.

[0109] The second frame 3 has pivot points. Pivot point 31 is connected to the balancer arm 6 of arm assembly 50. Balancer arm 6 can pivot with respect to pivot point 31.

[0110] Through point 31, a virtual construction line 201 along the z-axis can be constructed, representing movement of point 31 with respect to first frame 2 and the forces (such as due to gravity) exerted upon pivot point 31 in the z-axis. Preferably both points 31 and points 21 are positioned at similar radial distances from the guideline 209, located along virtual construction line 201 to allow for a balanced configuration. Preferably virtual construction line 201 is in a radial direction away from guideline 209 positioned between point 42 and point 41: locating point 41 not on construction line 201 but a bit closer towards guideline 209 (or farther away from point 41) allows for even better balance. Arms 6 and 7, part of the transmission, are connected at pivot point 41. In this embodiment pivot point 41 also forms a point of force application for (hydro) pneumatic spring system 4.

[0111] The (hydro) pneumatic spring system 4 is arranged as a pulling device. The spring force is applied between application points 41 and 42. Along points of spring force application 41 and 42, a virtual construction line 206 can be drawn and a force 207 is shown. The downward force 202 induced by the load on frame 3 is balanced by the upward force 208 induced via the pneumatic spring 401 on frame 3. The upward force 208 will remain (substantially) equal to the downward force 202 when the distance between the connection unit 22 and carrying unit 32 changes. With reference to FIG. 3, FIGS. 4 and 4b show the working of the spring force balancing arrangement. In FIG. 4 the distance between the connection unit 22 and carrying unit 32 is increased compared to FIG. 3, the extension of the springs is smaller and therefore the spring force is smaller but due to the leverage unit, embodied by the arm assemblies 6,7, the upward force 201 will remain (substantially) equal to downward force 202.

[0112] In FIG. 4b the distance between the connection unit 22 and carrying unit 32 is decreased compared to FIG. 3, the extension of the springs 401 is longer and therefore the spring force is larger but due to the leverage unit, the arm assemblies, the upward force 201 will remain (substantially) equal to downward force 202. The increasing/decreasing spring force as a result of the extension is leveraged by the leveraging unit in such a way that its vertical component 208, acting on frame 3, remains equal to the load force acting on frame 3 over a range of distances between connection unit 22 and carrying unit 32. When the ship is heaving (or pitching or rolling) the vertical position of the connection unit 22 changes, but since force 202 and force 201 are equal, due the inertia of the load (and in some cases action of the actuator 5), the movement of the connection unit 22 is substantially decoupled from the load. The vertical position of the load will remain substantially constant helped by the inertia of the load, and instead, the distance between connection unit 22 and carrying unit 32 will change.

[0113] In FIG. 6d, another example of an arrangement of a pneumatic spring 4 between first frame 2 and the arms of the transmission is shown. A gas supply 48 is provided on the heave balancing device 1 for each spring 4. Here the springs 4 are pivotably connected to the first frame at a sideward distance 49. This brings the springs 4 more in line with the direction of movement of pivot point 41, thereby allowing the springs 4 to be configured smaller.

[0114] In FIGS. 5 and 6a, embodiments of the device are shown, wherein the transmission comprises arm assemblies. The first and second frame are connected via two (parallel) double armed configuration. This is a rhombus configuration of pivoting arms. The (hydro) pneumatic spring 4, arranged to supply most or all of the heave balancing force, is connected between the arms of the transmission, at the force guiding and pivoting points on the arms.

[0115] In FIG. 5 the spring is an extension spring, in FIG. 6a the same function is provided by a compression spring, configured as an extension spring. In FIG. 5 the force of the gas is exerted on the rod side of the cylinder, in FIG. 5 the force of the gas is exerted on the bottom or piston side of the cylinder. However, the working principle of the spring in both FIGS. 5 and 6a is generally equal. In both FIGS. 5 and 6a the force of the spring increases when the distance between the connection unit and the carrying unit decreases and vice versa, but due to the leveraging unit, the rhombus configuration of pivoting arms, the upward force 208 exerted on frame 3 by the spring through the leveraging unit, remains equal to downward force 202, over a range of distances between connection unit 22 and carrying unit 32.

[0116] In FIGS. 5 and 6a, the (hydro-)pneumatic spring 4 is connected to the pivoting points 41 of the two parallel arm assemblies.

[0117] In FIGS. 1, 3, 4 and 4b an actuator 5 is provided between first frame 2 and second frame 3. The actuator can have many different embodiments. In the FIGS. 1, 3, 4 and 4b the actuator is shown as a linear actuator. It can be a linear motor engaging a geared teeth. Preferably, the actuator 5 can exert force on the system to over- or under-balance it, resulting in movement. The actuator 5 can be set before the operation and kept in the same position throughout, or more preferably, monitored and readjusted throughout.

[0118] It will be clear that any masses (inter alia, also masses of the apparatus components itself) that exert a torque can be taken into account and can be balanced. For further simplicity friction is ignored, although it will be clear that in case of a large friction, the balance point of the torque system is not a point, but a level. Further for simplicity the adiabatic coefficient of a gas or hydro-pneumatic spring is ignored, although it will be clear that temperature effects are relevant in practice.

[0119] In general, a load balancing system comprises a spring-balanced system having a spring-balanced configuration. Various non-limiting examples of such a system are shown, but other variations could be used.

[0120] In the preferred embodiment, the transmission couples the first and second frame via arms outside the guideline between load connection point and hoist connection point. This allows for the system to be compact, resulting in a system that can be hung under existing hoisting cranes.

[0121] In the embodiment shown in FIG. 3, a load 8 provides a net load force 202 in the Z-direction. In this embodiment virtual construction line 201 also extends in the Z-direction. Balancer arm 6 provides an upward force at point 31. This will keep second frame 3 and load 8 in the balanced position. The net load force results in a downwards force on arm part 7 at the force guiding point and pivoting point 41, resulting in a clockwise (CW) torque around pivoting point 21. Thereby second frame 3 supplies (indirectly) a pulling force on first frame 2, resulting in a pulling force 208 along virtual construction line 205 applied at pivoting point 21. This force 208 results in an upwards force component on arm 6 at the force guiding point and pivoting point 41, resulting in counterclockwise (CCW) torque around pivoting point 31.

[0122] The torque in pivot point 21 is dependent on the force exerted on the arm 7, the length of the arm (distance between the force application point, here 41 and the pivot point 21), and the angle between the virtual construction lines 204 and 201. Similarly, the torque in 31 is dependent on the angle between virtual construction lines 201 and 203.

[0123] (Hydro) pneumatic spring 4 provides counter-torque around pivot points 21 and 31 by providing a pulling force 207 along virtual construction line 206. This pulling force 206 exerted on arm 6 at the force guiding point and spring force application point 41, results in CW torque around pivot point 31. Pulling force 206 exerted on arm 7 at point 41 results also in CCW torque around pivot point 21.

[0124] In embodiments the transmission and/or the spring force balancing arrangement comprises at least a first force application point 21 that is directly suspended to the connection unit 22 and a second force application force 31, which directly suspends the carrying unit 32, wherein the first force application point is positionally closer to the carrying unit than the second force application point. In operation such an arrangement provides for a compact arrangement. In embodiments a third force application point 41, preferably providing a partial suspension force to the carrying unit that is positioned radially outward from the guideline 209

[0125] In a balanced system, the torque due to net load weight 202 and pulling force 208 due to drive element 3, is partially or fully balanced torque due to spring force 207, with any resting force/torque imbalance negated by actuator 5. This results in no net movement of the first frame 2 with respect to second frame 3. In operation the first frame 2 can move with respect to second frame 3 without changing this balance, thereby providing a spring balanced system.

[0126] When perturbations in the z-direction occur, for example due to heaving motions of vessel 11, the position of first frame 2 is moved as a result of movement of drive element 9. When this occurs, the balanced system will allow first frame 2 to move along the linear guideline 209 with respect to second frame 3 and due to the inertia of load 8 first frame 2 will move with respect to second frame 3, keeping the load 8 in position. Movement of the spring system 4 will keep the system in balance. It has been found that rather than having only one truly balanced (stabilized) position, the invention shows a substantially balanced system along the entire range of motion of the spring and system. In embodiments the spring system 4 allows an approximation of balance. In that embodiment the balance is achieved by action of the actuator 6. The actuator 6 can be configured to provide a force or torque in order to operate the system as a balanced system.

[0127] FIGS. 4 and 4b show examples of positions of the heave balancing device 1 in positions different from the position in FIG. 3. The second frame 3 has moved with respect to first frame 2, resulting in the heave balancing device having a different length. In FIG. 4a, a heave movement of the vessel 11 has in the crane tip moving upward, that movement being compensated for by extending the length of the heave balancing device 1 as a result of the mechanical transmission in combination with the (hydro) pneumatic spring. This then results in an upwards net movement by second frame 3 with respect to frame or support 2. In FIG. 4b, the motion of the ship resulted in the crane tip moving upward with respect to the ‘starting position’ shown in FIG. 3.

[0128] In embodiments of the invention the balance heave devices are balanced or approximately a balanced system. In embodiments, the force supplied by spring system 4 is dependent on the area of triangle of the engagement points 21, 41, 42 and the configuration of the spring system 4. The torques supplied by net load force 202 and pulling force 208 are dependent on the angle of the arms.

[0129] In FIG. 4 for example, the heave balancing device 1 moved its arms assembly, in order to increase the length of the heave balancing device 1. As a result, the arms 6,7 moved, thereby changing the angle of the force exerted by the (hydro) pneumatic spring around with respect to the arms, which results in the torque around pivoting points 31 and 21 increasing. However, the force 207 supplied by spring 4 is also smaller, as the spring 4 is more contracted in comparison to FIG. 3. This allows an overall balanced system or an approximation of a balanced system.

[0130] Similarly, in the position of FIG. 4b with respect to the ‘starting position’ of FIG. 3, the arms 6,7 move around pivot point 31, thereby reducing the torque around pivot point 21. However, as the spring 4 is more elongated, the pulling force 207 supplied by the spring 4 is also larger. This allows an overall balanced system or an approximation of a balanced system.

[0131] In the preferred embodiment, the spring characteristic of (hydro) pneumatic spring 4 can be varied, resulting in an over- or under-balanced system, with a slow movement of the load 8 as a result. This can be beneficial for placing or picking up load 8.

[0132] In embodiments the position of the pivot points with respect to the first frame 2 or the position of second frame 3 can be moved.

[0133] As the system is substantially balanced across the entire range of motion of arms 6,7 and spring 4, it has been found that near the limits of the range of motion of the (hydro) pneumatic spring 4, the (hydro) pneumatic spring 4 can be overexerted, with massive impact forces as a result. To prevent this, the system 1 must be limited in motion. Hence, a safeguarding system is required to be put into place.

[0134] In embodiments of the invention, the heave balancing device 1 has a safeguarding system. The safeguarding system is arranged to prevent the heave balancing device from moving toward an end position. By preventing the heave balancing device from reaching an end position, damage is prevented.

[0135] The security device can have many different embodiments and can comprise several units. In an embodiment the security system comprises a biased unit that biases the heave balancing system to a default position, e.g. a middle position of the second frame 3 with respect to first frame 2. In this application an ‘end position’ can be an extreme position of the arm assembly of the heave balancing device 1 in which further movement is prevented. E.g. the angle between each of the arms 6,7 and the frame can vary only between 5 and 85 degrees, or 15 and 75 degrees. Those angles form extreme positions. However, in embodiments the extreme positions are at smaller angles or a smaller range between the angles at the extreme positions.

[0136] Embodiments of the security system include, but are not limited to: a second hydro(pneumatic) spring, a damper, a (monitor and control) for the throttle valve of the (hydro) pneumatic spring 4, an actuator between load 8 and suspension point of support or first frame 2, programming the balancer 1, a connection between load 8 and target object (if present), or any combination of these. Preferably, the security mechanism both monitors the extension of the spring and/or balancer, and controls and exerts a force upon the system.

[0137] In an embodiment the security system comprises an actuator 5. In an embodiment such as FIG. 3, actuator 5 is a linear actuator and is arranged to provide a balancing force to compensate for non-linear properties of the (hydro) pneumatic spring system 4 and is arranged to also provide a return force towards a default position of the of heave balancing device 1. That return force can increase with distance of the second frame 3 from its default position.

[0138] In embodiments the security system can be a second winch and drive element in a split hoist configuration (e.g. the actuator 5 is placed on board of the floating object), for example shown in figure la. The transmission, the first and/or second frame will be able to move within a domain, with boundaries formed by the extreme positions at the end of a movement stroke of the frames. E.g. the stroke of the spring is limited. The security system prevents the balance heaving system 1 to approach these extreme positions/boundaries.

[0139] When the linear actuator 5 operates as a security system, the actuator 5 allows for some linear motion of first frame 2 with respect to second frame 3, but prevents movement outside the range of motion of the balancing system. The heave balancing device 1 can comprises a sensor that measures the respective position of the first frame 2 and second frame 3. On the basis of the measured distance by the sensor a suitable processor can compute a force to be exerted on the system for safeguarding the system, which force can be additional to the balancing force.

[0140] Preferably, the security system is arranged to prevent sudden movements.

[0141] In the embodiment shown in FIGS. 3, 4a and 4b, a linear actuator 5 is employed. In the scenario of FIG. 3, where the balancer is well within range of motion of the spring, the actuator shall only have to exert force if there is an imbalance within the system, to prevent movement. In scenarios 4a and 4b, where the systems are balanced but the systems are also near the limits of the range of operation for the spring, the actuator will be exerting a force such that the system carefully and smoothly obtains a configuration nearer the middle of the range of operation, such as shown FIG. 3. Since the heave balancing device substantially balances the load over a range of distances between the connection unit 22 and the carrying unit 32, the force of the actuator required to function as a security system can be very small.

[0142] In FIG. 6b, another embodiment according to the invention is shown. The (hydro) pneumatic spring 4 is connected on the rhombus configured arms 6,7 of the transmission at a distance 71 and 72 respectively from the pivoting points 41. As in previous examples, the (hydro) pneumatic spring 4 is arranged as a pulling device, and the force provide by said spring is guided through the force guiding points. The non-linear behavior of a gas spring can be (partly) counteracted by choosing an optimal position of the connection points of the spring. This leads to a better balance and therefore to a better decoupling.

[0143] FIG. 6c shows another embodiment according to the current invention. FIG. 6c is an example of an embodiment wherein the leverage unit is formed by the two pivoting pneumatic springs itself, the leverage being provided dependent on the angle a.

[0144] FIG. 6d shows another embodiment according to the current invention. FIG. 6d is an example of an embodiment engaging compression springs instead of extension springs.

[0145] In this example, the configurable pneumatic two springs 4 connect to first frame 2 and second frame 3. The pneumatic springs 4 are connected via pivoting points 601 and 602, and form the pivoting arms of the device. By changing the length of the springs and the angle a between springs and frames, first frame 2 and second frame 3 are allowed to move with respect to each other. In the shown embodiment, the angle a is, in this example, about 45 degrees. When the distance between de connection unit and the carrying unit decreases, the compression spring is further compressed and its force therefore increases but since angle alpha a also increases an increasing part of the spring force is deflected in a horizontal direction, rendering the upward force of the spring in point 602 generally equal. This works only when angle a remains larger than 5 degrees and smaller than 85 degrees. In this embodiment the area of triangle between points 602 and 601 is (inversely) correlated to the spring force in such a way the upward component of the spring force remains generally equal to the downward force of the load over a range of movement of frame 2 relative to frame 3.

[0146] This embodiment can also be executed with one spring or more than 2 springs, as is the case with most embodiments shown in other figures. When this embodiment is executed with three or more springs the point where the three springs come together can be the carrying unit, the load can be connected directly to this point and a second frame is not required.

[0147] In FIG. 6e, another embodiment according to the current invention is shown. The transmission comprises a rotating unit in the form of a pulley 81 that has a variable pitch 82. The rotating unit forms the leverage unit. The carrying unit 32 for the load is formed by a line connected to the pulley 81 of the transmission. The (hydro) pneumatic spring 4 is arranged to balance the movement in the z-direction. The first frame 83 has a pivot point 84 to which the spring 4 is connected. Spring 4 is further connected to the pulley via a wire 85 that can be wired on to the pulley at a first pitch. This will rotate the pulley. The carrying unit will however move at a leveraged amount due to the variable pitch 82. This will allow to compensate for the behavior of the spring 4, thereby providing a carrying force to the load that is close to constant, when the load moves in the z-direction.

[0148] In this embodiment, a clockwise rotation results in extension of the pneumatic spring, and a corresponding torque increase. The same rotation also corresponds in the load carrying line being wound off, resulting in an increased pitch, i.e. moment arm, with a corresponding torque increase. The variable pitch thread is arranged in such a way that a torque increase/decrease due to spring extension/compression, is (substantially) balanced by a corresponding torque increase/decrease due to the change in pitch of the load carrying line. Many other embodiments are possible.