Crane with adjustable floating ballast

Abstract

To improve CO2 balance when using a crane without sacrificing stability.SOLUTION: The present invention relates to a crane, particularly a lattice boom mobile crane. The crane has an upper rotating body that can rotate around a vertical rotation axis and a floating ballast connected to the upper rotating body via a floating ballast guide. The floating ballast guide includes a drive device that changes the distance of the floating ballast from the rotation axis of the upper rotating body. The floating ballast guide is connected to the upper rotating body via at least one force transmission member. The force transmission member is configured to partially unload the floating ballast guide with an unloading force opposing the weight force of the floating ballast, thereby introducing a corresponding reaction force into the upper rotating body.SELECTED DRAWING: Figure 2

Description

[Technical field]

[0001] The present invention relates to a crane, in particular a lattice boom mobile crane according to the prefabricated part according to claim 1. [Background technology]

[0002] In addition to the mobile undercarriage, the upper rotating body rotatably mounted on the undercarriage, and the lattice boom swingably mounted on the upper rotating body, large lattice boom cranes often have an additional derrick boom swingably mounted on the upper rotating body. The derrick boom is usually connected to the main boom via a length-adjustable guy in a hoist adjustment style, and is further connected to an additional guy block via a guying system. The guy block connected to the upper rotating body is then connected to the upper rotating body via a length-adjustable hoist adjustment mechanism. This increases the guying angle of the main boom.

[0003] To counter the load torque caused by the load lifted via the main boom, a counterweight arrangement, also known as upper bed ballast, typically comprises several stackable counterweight plates and is present at the rear of the upper bed. For assembly and disassembly of the main boom and for lifting particularly heavy loads, a floating ballast can be provided in addition to the upper bed ballast, which is connected to the tip of the derrick boom via further guys, typically in the form of steel rods, and generates an additional counter torque to counter the load torque. The floating ballast can be held suspended above the ground or seated on a movable ballast carriage so that the upper bed can be rotated even when floating ballast is used. The floating ballast typically comprises a support plate with several counterweight plates stacked on it. The guys are provided with variable length cylinders.

[0004] So that the distance of the floating ballast to the rear of the upper rotating body or to the rotation axis of the upper rotating body can be adjusted in particular continuously and thus the counter torque occurring for the respective lifting operation can be adapted, it is known, for example from German patent application no. 10 2018 102 025, for the floating ballast to be connected to the rear of the upper rotating body via a swinging and folding floating ballast guide, which comprises two articulated lattice sections and, as drive device, one or more hydraulic cylinders for folding the lattice sections in and out and thus for reducing or increasing the floating ballast radius.

[0005] In floating ballast operations with adjustable floating ballast guides, a relatively large upper bed ballast is necessary to ensure the stability of the crane, especially with respect to tilting of the entire crane perpendicular to the undulating surface (i.e. the surface on which the load is undulating). Such loads are caused for example by side winds. Due to the usually very long jib systems of such cranes, large forces and torques can occur here.

[0006] The floating ballast is connected to the upper rotating bed via the floating ballast guide and the derrick boom. However, the connection between the two is relatively "soft", especially when the floating ballast is set to a large radius. Thus, the floating ballast perpendicular to the boom system's undulating surface can only provide little stability against tipping of the crane. This is made possible by the upper rotating bed ballast. Each stack of the upper rotating bed ballast has its own center of gravity. The entire upper rotating bed ballast has a center of gravity, which is generally also located on the boom system's undulating surface, but always has an associated distance to the lateral tipping edge of the crane, which is determined by the undercarriage or support. The upper rotating bed usually supports the upper rotating bed ballast rigidly, which can increase the stability against lateral tipping.

[0007] For current crane operations, the CO2 balance sheet is a relevant indicator. The transport of heavy counterweight elements is a particularly disadvantageous factor. Heavy counterweight elements quickly lead to overloading of the transport vehicle, which means that additional transport vehicles have to be used, thus worsening the CO2 balance. Summary of the Invention [Problem to be solved by the invention]

[0008] In order to reduce the total number and mass of counterweight plates used, their distance from the axis of rotation of the upper body or the rotating assembly (i.e. the lever arms) must be increased accordingly. However, the mass of the floating ballast is usually already optimally utilized. It would still be conceivable to use a stability-related upper body ballast with a larger radius. However, the required lengthening of the upper body may have a negative effect on the adjustability of the suspension ballast. Shifting the upper body ballast to the floating ballast (which is at a greater distance from the axis of rotation of the upper body than the upper body ballast) is, on the other hand, problematic, since the above-mentioned stability against lateral overturning is no longer ensured.

[0009] Against this background, the basis of the present invention is to improve the CO2 balance of the use of this type of crane without making any sacrifices in terms of stability. [Means for solving the problem]

[0010] According to the invention, this object is achieved by a crane having the features of claim 1. Advantageous embodiments of the invention emerge from the dependent claims and the following description.

[0011] Claim 1 Therefore, a crane, in particular a lattice boom mobile crane, is proposed, which comprises a rotating upper body rotatable about a vertical axis of rotation and a floating ballast connected to the rotating upper body via a floating ballast guide, which comprises a drive for varying the floating ballast radius, i.e. the distance of the axis of rotation of the floating ballast or the rotating upper body, respectively, from the center of the rotating assembly. The crane may be a crawler crane.

[0012] According to the invention, the floating ballast guide is connected to the upper rotating body via at least one force transmission member configured to partially unload or release the floating ballast guide by means of an unloading force countering the weight force of the floating ballast, thereby introducing a corresponding reaction force into the upper rotating body.

[0013] The reaction force introduced into the superstructure has a component acting in the direction of the weight force of the floating ballast. Depending on the magnitude and the position of application of this force, the superstructure ballast, which is fixed to the superstructure, can consequently be completely or partially replaced.

[0014] This allows counterweight plates, which otherwise form the upper body ballast, to be laid or stacked entirely or partially on the floating ballast without compromising the stability of the crane. The reaction force introduced to the upper body via the force transmission members can act as a lateral stabilizer preventing the crane from tipping over to the side. Relocating the counterweight plates from the upper body to the floating ballast increases the distance from the lever arm or the rotation axis of the upper body, so that fewer counterweight plates must be used to generate the same counter torque reacting to the load torque. Furthermore, sufficient installation space is available on the floating ballast to stack any number of counterweight plates. This eliminates the need to transport the counterweight plates to the construction site, thus saving CO2.

[0015] This reaction force or its downward force component can be of small magnitude compared to the weight force of the entire floating ballast and the floating ballast guide. Therefore, when the floating ballast radius is large, all components engaged or unloaded by the weight force of the floating ballast remain equally high and loaded in the same direction. Therefore, the floating ballast guide does not change its swing direction about its horizontal axis on the upper rotating body (i.e., the unloading force generated by the force transmission member is not enough to overcome the weight force of the floating ballast and the floating ballast guide and push the floating ballast guide upwards).

[0016] With the force transmission members provided in accordance with the present invention, upper bed ballast can be selected to be significantly reduced, or best yet, eliminated entirely, and replaced with a constant or variable reaction force.

[0017] In the following description, when referring to a reaction force replacing or supplementing the upper rotating body ballast, strictly speaking, this refers to the downward component of the reaction force acting in the direction of the weight force of the floating ballast. The direction of action of the reaction force depends on the arrangement and design of the force transmission members and, if applicable, the position of the suspended ballast guides, and is not limited to a specific angle; for ease of explanation, in the following, only the reaction force is generally referred to.

[0018] In one possible embodiment, it is conceivable that the force transmission member is not part of the drive of the floating ballast guide. For example, the drive can include one or more hydraulic cylinders which connect the floating ballast guide to the upper rotating body. In this case, these hydraulic cylinders can also introduce some reaction force to the upper rotating body. However, in the case of these hydraulic cylinders, and more generally in the case of the drive of the floating ballast guide, it is expressly not a matter of the force transmission member according to the invention. It is provided additionally and serves for the targeted introduction of a constant or variable reaction force to the upper rotating body, and not for adjusting the floating ballast or the floating ballast guide.

[0019] In another possible embodiment, it is conceivable that the force transmission member is connected to a support device attached to the rear of the upper rotating body, preferably projecting or protruding rearward from the upper rotating body. The support device can constitute or comprise a support frame attached to the rear of the upper rotating body. This allows the distance of the connection point of the force transmission member to the rotation axis of the upper rotating body to be extended rearward and also its height above the ground to be reduced, so that sufficient installation space is available for the force transmission member between the support device and the floating ballast guide. Due to the cantilever support device, the reaction force introduced into the upper rotating body also acts on the upper rotating body with a larger lever arm, and is therefore even more favorable than when a upper rotating body ballast is used.

[0020] Also, the fact that the support device is mounted to the rear of the upper rotating body includes the case where the attachment points of the support device are located wholly or partially on the sides of the upper rotating body. Optionally, the support device can be connected to a luffing shaft on which a floating ballast guide is mounted on the upper rotating body so that it can swing.

[0021] In another possible embodiment, at least two force transmission members are provided, which are arranged transversely, in particular mirror-symmetrically, with respect to the undulating plane extending through the axis of rotation of the upper rotating body. In this way, a corresponding reaction force can be introduced laterally to the rear part of the upper rotating body, generating an optimal stabilizing effect against the lateral tilt of the crane. The force transmission members can be coupled or synchronized with each other or can operate or act independently of each other.

[0022] In another possible embodiment, it is provided that the floating ballast guide comprises two lattice sections hinged to one another via a swivel joint, the first lattice section being pivotally connected to the rear part of the upper rotating body about the horizontal hoisting axis. Preferably, the actuator comprises one or more hydraulic cylinders pivotally connected to one lattice section. Possible embodiments of the floating ballast guide are disclosed in German patent application no. 10 2018 102 025, the contents of which are expressly referred to. The floating ballast guide can have, for example, more than one lattice section or more than one swivel joint, in order to be able to further reduce the possible minimum distance of the floating ballast from the center of the rotating assembly.

[0023] In another possible embodiment, it is conceivable that the force transmission member is pivotally connected to a first lattice section, preferably hinged to the upper rotating body, and to one of the aforementioned lattice sections of the floating ballast guide, while the drive device can comprise one or more hydraulic cylinders connecting the second lattice section to the upper rotating body.

[0024] In a further possible embodiment, it is conceivable that the magnitude of the unloading force, i.e. in particular the normal force component of the unloading force (see introductory remarks on reaction forces) that can be applied by the force transmission member, is smaller than the weight force of the floating ballast, so that the floating ballast is only unloaded or released and is not lifted against the weight force, thus the floating ballast continues to act against the load torque.

[0025] In a further possible embodiment, the magnitude of the unloading force that can be applied by the force transmission member may be constant. This of course also applies to the corresponding reaction force. This means that it is not possible to actively vary the unloading force or the counter force, in particular for a constant position of the floating ballast guide. On the other hand, it may be true to vary the applied unloading force or the reaction force with the position of the floating ballast guide, for example in the case of passive force transmission members, since this changes the distance between the floating ballast guide and the support device.

[0026] Alternatively, the magnitude of the unloading or reaction force that can be applied by the force transmission member can be varied. In particular, this can mean that the unloading or reaction force can be varied in a targeted manner when the floating ballast guide is in a constant position. Preferably, the magnitude of the unloading or reaction force can be controlled, for example, by the crane control and / or the load torque limiting. This allows the reaction force acting on the upper body to be variably adjusted as required, for example depending on the targeted operation of lateral stability or on the specific lifting task. In the case of a controllable force, the force transmission member can also be controlled in such a way that a defined, constant or minimum force is established regardless of the position of the floating ballast guide.

[0027] In another possible embodiment, the force transmission members may be permanently connected to the floating ballast guide and the upper rotating body, so that in the case of passive force transmission members the force can be permanently applied, whereas in the case of actively controllable or adjustable force transmission members the force generated can be specifically activated or deactivated or adjusted.

[0028] In another possible embodiment, the force transmitting member may comprise a spring device.

[0029] In a further possible embodiment, the force transmission members may be hydraulically actuated to actively generate the unloading or reaction force, in particular may comprise hydraulic cylinders. The latter includes the case where the force transmission members are hydraulic cylinders. The force transmission members can preferably be controlled or adjusted by the crane control system in such a way that a predefined unloading or reaction force is established. The unloading or reaction force can be set, for example, automatically by the crane control system and / or a load torque limiter and / or manually by the crane operator. Preferably, at least two force transmission members of the hydraulic cylinder type are provided. Advantageously, these are not hydraulically connected to one another. The hydraulic cylinders are preferably force-controlled. Each hydraulic cylinder thus independently introduces its reaction force into the upper rotating body.

[0030] Furthermore, a combination of passive and active force transmission members is also conceivable, for example a combination of a spring device and a hydraulic cylinder.

[0031] In a further possible embodiment, the value of the unloading force or reaction force generated by the force transmission member is transmitted to a load torque limiter of the crane and is preferably in particular controllable and variable by said load torque limiter, which can be part of or be performed by the crane control device.

[0032] Alternatively or additionally, an auxiliary system may be provided that controls or adjusts the force transmission members so that the floating ballast is a constant distance from the ground. Preferably, the floating ballast should always be close to the ground so that it can be lowered quickly and before the boom system of the crane tips backwards.

[0033] Such a support system can be used, for example, in the construction of wind turbines. To achieve the required load, so much floating ballast can also be applied that there is a risk of the boom system of the crane tipping backwards after lowering the load. In this case, the crane lowers the floating ballast preferentially, and the assistant crane removes the counterweight plates from the lowered floating ballast. The crane can then pick up the floating ballast again and move it. The boom system and the floating ballast are then balanced again. In the inventive solution, the optionally provided assistant system can actively control the force transmission members and take off force components from the boom system (unloading force) and simultaneously introduce them as force components into the upper rotating body (reaction force). This allows the boom system to be returned to equilibrium without removing or stacking counterweight elements from the floating ballast.

[0034] In a further possible embodiment, at least two force transmission members can be controlled or adjusted independently of one another. Preferably, at least two force transmission members are provided in the form of hydraulic cylinders. Advantageously, they are not hydraulically connected to one another. The cylinders are preferably force-controlled. In this way, each hydraulic cylinder independently introduces its reaction force into the upper rotating body.

[0035] In another possible embodiment, the crane may further comprise a derrick boom coupled to the upper rotating bed, which is connected to the floating ballast via a first guy and to the upper rotating bed via a second guy, in particular via a guy block. The derrick boom and / or the main boom can be secured against tilting backwards by hydraulic support cylinders, whereby the forces acting on the respective booms are preferably readjusted with the boom movements.

[0036] In a further possible embodiment, the superbed may be equipped with a stationary superbed ballast with a stackable counterweight element in addition to the floating ballast, preferably the counterweight element being optionally stackable on the floating ballast, or the superbed may not be equipped with a superbed ballast, but the superbed ballast may be completely replaced by a reaction force that may be applied via a force transmission member.

[0037] Further features, details and advantages of the invention will become apparent from the following description of exemplary embodiments with reference to the drawings. [Brief description of the drawings]

[0038] [Figure 1] FIG. 1 is a side view showing a first embodiment of a crane according to the present invention. [Diagram 2] FIG. 11 is a side view of a portion of a second embodiment of a crane according to the present invention. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0039] FIG. 1 shows a side view of a crane 10 according to a first embodiment. The embodiment shown here is a lattice boom mobile crane 10, which comprises a mobile undercarriage 12 with a crawler chassis and an upper rotating body 14 mounted on the undercarriage 12 for rotation about a vertical axis. A lattice boom serving as a main boom 15 for lifting a load is mounted on the upper rotating body 14 so as to be swingable or hoistable about a horizontal axis. A derrick boom 16 is mounted on the upper rotating body 14 behind the main boom 15 for swinging about a horizontal axis.

[0040] The derrick boom 16 is connected to the main boom 15 via a length-adjustable guy 33. The tip of the derrick boom 16 is connected to the floating ballast 20 via a first guy 31, which counteracts the load torque generated by the lifted load with a corresponding counter torque. The mass of the floating ballast 20 therefore acts on the tip of the derrick boom 16 via the first guy 31. Through a second guy 32, the derrick boom 16 is connected to a guy block 17 attached to the upper rotating bed 14 so that it can swing about a horizontal axis. The guy block 17 is in turn connected to the upper rotating bed 14 via a length-adjustable hoisting strand. The main boom 15 is hoisted up and down by the length-adjustable guy 33.

[0041] Both the main boom 15 and the derrick boom 16 are held "tip-back" in the illustrated example by hydraulic guy supports or support cylinders 18. However, these guy supports 18, which move with the hoisting motion of the respective booms 15, 16, are limited in force and are not particularly configured to hold the large mass of floating ballast 20 suspended above the derrick boom 16 at a large floating ballast radius. The function of the guy supports 18 is to act as a reaction force or stop to secure the booms 15, 16 at the rear.

[0042] In the embodiment of Figure 1, the crane 10 is equipped with an upper bed ballast 50, which comprises two stacks of counterweight elements rigidly mounted laterally at the rear 13 of the upper bed 14. However, due to the function of the force transmission members 40 described below, the height of these ballast stacks is significantly reduced compared to known cranes.

[0043] In order to allow the floating ballast 20 or the floating ballast radius to be variably and continuously adjusted during operation, the floating ballast 20 is connected to the rear part 13 of the upper rotating body 14 via an adjustable floating ballast guide 22. In the embodiment shown here, the floating ballast guide 22 comprises two lattice sections 24, 26 pivotally connected to each other via a horizontal swing joint 23, i.e. a first lattice section 24 mounted on the rear part 13 of the upper rotating body so as to be pivotable about the horizontal hoisting axis 21, and a second lattice section 26 articulatedly connected to the floating ballast 20 (see FIG. 2). One or more hydraulic cylinder type drives 28 are used to fold and unfold the two lattice sections 24, 26 of the floating ballast guide 22, thereby changing the floating ballast radius. One or more hydraulic cylinders 28 are swingably attached to the rear part 13 of the upper rotating body or to the first lattice part 24 and the second lattice part 26. When the drive device (hydraulic cylinder 28) is fully extended or the floating ballast guide 22 is fully folded, the distance of the floating ballast 20 to the rotation axis of the upper rotating body, and therefore the counter torque generated by the floating ballast 20, is maximum.

[0044] With the variable floating ballast operation with the existing swinging floating ballast guides 22, a relatively high superstructure ballast 50 would be required in known cranes to ensure stability in all directions, i.e. 360°. These 360° referred to here mostly involve little to no swinging of the superstructure 14, but rather tilting the entire crane 10 laterally with respect to the undulating surface. The floating ballast 20 is connected to the superstructure 14 via the floating ballast guides 22 and the derrick boom 16. Both connections are "soft", especially when the floating ballast 20 is set to a large radius. Thus, the floating ballast 20 perpendicular to the undulating plane of the boom system can only provide a small amount of stability against tipping of the crane 10. Whereas in conventional cranes, this is made possible by the superstructure ballast 50 rigidly attached to the superstructure 14.

[0045] For the sake of explanation, some general remarks are made about the stability of the crane 10 at this point. The undercarriage 12 has tipping edges in the area of ​​the rollers on which the crawler tracks run. These tipping edges form a rectangle with four tipping edges extending along and between the two crawler tracks. To prevent the crane 10 from tipping over, its overall center of gravity must always be within these tipping edges. For this purpose, the crane control 60 normally monitors a load torque that tends to tilt the crane 10 forward, i.e. in the direction of the load on the main boom 15. This load torque is countered by a counter torque or ballast torque resulting from the mass of the upper rotating body ballast 50 and the floating ballast 20 (and of course the floating ballast guides 22). If the upper rotating body 14 rotates 360° around the undercarriage 12, the tipping edges to be considered or the relative position of the center of gravity within the tipping edges also regularly change.

[0046] Furthermore, the stability of the boom system consisting of the main boom 15 and the derrick boom 16 must also be considered. The load torque "wants" to move the main boom 15 forward in the direction of the load. This is prevented by the adjusting guy 33 that connects the main boom 15 to the derrick boom 16. The derrick boom 16 is held by the floating ballast 20 on the one hand via the first guy 31 and by the guy block 17 on the other hand via the second guy 32, which determines the lever arm to the swing point of the derrick boom 16.

[0047] In crane operation, as explained at the beginning, it must also be taken into account that, independently of the rotational position of the upper rotating body 14, the entire crane 10 may tilt laterally out of the boom system's landing plane, e.g. due to cross winds.

[0048] Typically, a large mass of floating ballast 20 is required primarily for raising or lowering the boom system, while a smaller floating ballast 20 is often sufficient for the actual lifting of the load. Thus, when there is no load on the main boom 15, the weight of all the floating ballast 20 is usually so high that there is a risk of the crane 10 tipping backwards. Therefore, in such a situation, i.e. when lowering or placing a load, the counterweight plate needs to be removed from the floating ballast 20 or the steep jib position cannot be approached with a given ballast effect.

[0049] In principle, it is possible to provide a two-part floating ballast 20 (first floating ballast part), for example with a floating ballast frame on which a transverse stack of two counterweight plates can be arranged, and a second floating ballast part which can be removably connected to the first floating ballast part, which are connected and act with their full mass for weight strokes or for lifting the boom. For the actual crane operation and "normal" load lifting, the lighter second floating ballast part can be removed from the first floating ballast part. This is advantageous in the work flow at the construction site. However, such a solution does not result in a reduction in the counterweight plates to be transported to the construction site, since even if the ballast weights of the first floating ballast part are only required for erecting the main boom 15, they still have to be transported to the construction site.

[0050] Therefore, maximum counterweight torque is required to raise the boom 15 (with luffing jib if necessary). To reduce the mass of the upper bed ballast 50 and the floating ballast 20, their distance from the upper bed's axis of rotation would have to be increased, which would, however, entail the drawbacks mentioned earlier.

[0051] According to the invention, the floating ballast guide 22 is therefore connected to the upper rotating bed rear part 13 via one or more force transmission members 40. In the example shown here, two force transmission members 40 of the hydraulic cylinder type are arranged at the same distance from an undulating plane that runs centrally through the axis of rotation of the upper rotating bed. A support device 42 is attached to the upper rotating bed rear part 13 and projects radially rearward therefrom. The force transmission member 40 is connected in an articulated manner to both the support device 42 and to the floating ballast guide 22, in the example shown here at the first lattice part 24 of the floating ballast guide 22. The connection point of the force transmission member 40 is located at the rear end of the support device 42 and further below the articulation point 21 (see FIG. 2) of the floating ballast guide 22.

[0052] Alternatively, only a single force transmission member 40 may be provided, in particular arranged in the contoured surface. Furthermore, more than two force transmission members 40 may be provided.

[0053] By means of the force transmission member 40, i.e. in the embodiment shown here by a corresponding pressurization of the hydraulic cylinder 40, a defined unloading force F1 can be generated, which is the weight force F of the floating ballast 20. g , unloading the floating ballast guide 22 and in particular the ballast guy 31. A corresponding counter force F2 (reaction force to the unloading force F1) acts in the opposite direction, i.e., towards the support device 42, thus loading the superstructure 14. This reaction force F2 can be used as a replacement for the entire superstructure ballast 50 or at least a part thereof.

[0054] 2 shows a second embodiment of the crane 10 according to the invention in a lateral section in the region of the superstructure 14 and the floating ballast 20, whereby, in comparison with the first embodiment, the superstructure ballast 50 is not attached to the superstructure 14. FIG. 2 also shows the force F g , F1 and F2 are shown.

[0055] According to the invention, the upper bed ballast 50 is thus no longer at least completely formed by the corresponding counterweight plate, but is in particular replaced or supplemented by the force transmission member 40. As a result, the saved counterweight plates of the previous upper bed ballast 50 can now be stacked on the floating ballast 20, for example on the above-mentioned first floating ballast part, to increase the height of the corresponding counterweight stack. There is now sufficient installation space. Due to the now increased lever arm (distance to the pivot axis of the upper bed), fewer counterweight plates are required to generate the same counter torque. In this way, unnecessary counterweight plates do not have to be transported to the construction site, and therefore CO2 can be saved.

[0056] The force transmission members 40, in combination with the support devices 42, further serve to laterally stabilize the crane 10 by introducing a corresponding downwardly acting reaction force F2 on the upper rotating body 14 in the lateral direction of the undulating surface. In this way, the crane 10 can be effectively protected against lateral tilt.

[0057] Preferably, the hydraulic cylinders 40 are not hydraulically connected to one another and are in particular force controlled, so that each cylinder 40 independently directs its force towards the rear upper bed 13.

[0058] Preferably, the hydraulic cylinders 40 are controlled / regulated by corresponding control / regulation of the underlying hydraulic circuits for supplying the hydraulic cylinders 40. Here, the crane controller 60 can preferably control hydraulic sources, such as one or more hydraulic pumps and / or control valves, to provide desired unloading or reaction forces F1, F2 to generate a desired hydraulic pressure in the one or more hydraulic cylinders 40.

[0059] The unloading force F1 and the reaction force F2 (or their vertically acting force components) are preferably proportionally small compared to the weight force of the floating ballast as a whole. Thus, all the components involved / unloading continue to be loaded at similar levels and in the same direction when the floating ballast radius is large. Also, the floating ballast guide 22 does not change its direction of rotation about the horizontal rafter axis 21.

[0060] In general, a constant or controllable force can be applied from the swivel ballast guide 22 to the upper bed 14 via the force transmission member 40. In the case of the hydraulic cylinder 40 described here, the applied force F2 can preferably be controlled and continuously adjusted during operation. Control is preferably via a crane controller of the crane 10, shown diagrammatically at 60 in FIG. 1 only (the actual position of the crane controller 60 is of course not limited to the position shown).

[0061] In the preferred case where the magnitude of the reaction force F2 can be set and specifically controlled, it can be used as a parameter variable for the load torque limiting of the crane 10. In this way, the crane 10 can be used more variably and with increased permissible loads.

[0062] Using the solution according to the invention, the upper bed ballast 50 can be selected to be substantially smaller, or best of all, can be replaced by a constant or variable force from the force transmission member or means 40.

[0063] As an alternative to being configured as a hydraulic cylinder, at least one force transmission member 40 can also be designed as a spring support. A constant force F2 or a variable force F controlled by the crane control 60 can then be applied to the rear upper body 13.

[0064] As mentioned above, an auxiliary system can be utilized in a typical crane, for example, in use in constructing wind turbines. In a preferred embodiment of the present invention, the auxiliary system can control at least one force transmission member 40 to selectively remove a particular force component F1 from the boom system and simultaneously introduce it as force component F2 into the rotating upper bed 14. In this manner, the boom system can be returned to an equilibrium state, for example, after a load has been loaded onto a structure.

[0065] Furthermore, because of the cantilever support device 42, the force F2 introduced into the rear of the upper body 13 acts on the upper body 14 with a larger lever arm and therefore acts more favorably than if an upper body ballast 50 rigidly attached to the upper body 14 were used.

[0066] The solution according to the invention can thus generate variable ballast conditions as an alternative to the upper bed ballast 50. For this purpose, a suitable control or regulation with load torque limit can be provided by the crane control 60. The possibility of continuous use of the floating ballast guides 22 creates additional variable conditions during crane operation. Thus, a divisible floating ballast 20 can be used. Also, the floating ballast radius is widely adjustable. In this way, maximum ballast or counter torque can be provided to the crane 10 for high load torque during operation with load or during assembly.

[0067] In one possible application, even the most angular boom positions can be approached. Such a condition may occur as the operating position after the load is set to the steepest position of the main boom 15. In this position, the following settings are supported: 1. The minimum free hanging condition of the floating ballast 20 in terms of the mass of the ballast and its radius for the maximum possible freedom of movement (swing, drive). This is expressed as follows: The ratio of the mass of the floating ballast 20 and its swing length is optimized. The more the floating ballast 20 is swung out, the more space the crane 10 requires at the construction site (when swinging and moving). The more floating ballast 20 is required, the more counterweight plates need to be transported to the construction site. Furthermore, the floating ballast 20 needs to be lifted off the ground frequently to allow the crane 10 to rotate and move freely. 2. High bearing force on the unloading force transmission member 40 between the floating ballast guide 22 and the rear of the upper rotating body 13 (force components F1, F2). [Explanation of symbols]

[0068] 10. Crane 12 Undercarriage 13 Rear of upper rotating body, rear 14 Upper rotating body 15 Main Boom 16 Derrick Boom 17 Guy Block 18 Support cylinder 20 Floating Ballast 21 Relief axis 22 Floating ballast guide 23 Swing joint 24 First Lattice Section 26 Second Lattice Section 28 Drive unit (hydraulic cylinder) 31 First Guy 32 The Second Guy 33 Adjustable length guy 40 Force transmission member 42 Support device 50 Upper rotating body ballast 60 Crane control device 311 Floating Ballast Hoist Cylinder F g Floating ballast weight force F1 Unloading Force F2 reaction force

Claims

1. An upper rotating body (14) capable of rotating about a vertical axis of rotation; A floating ballast (20) connected to the upper rotating body via a floating ballast guide (22), A crane, wherein the floating ballast guide (22) includes a drive (28) for varying the floating ballast radius, The floating ballast guide (22) is adapted to absorb the weight force (F ｇ ) and thereby generates a corresponding reaction force (F ２ a force transmitting member (40) connected to the upper rotating body (14) via at least one force transmitting member (40) configured to introduce a force to the upper rotating body (14); The force transmission member (40) comprises a spring member. A crane (10).

2. the force transmission member (40) is not part of the drive (28) of the floating ballast guide (22); The crane (10) of claim 1.

3. The force transmission member (40) is attached to the rear of the upper rotating body (14), A support device (42) is connected to the upper rotating body (14) and protrudes rearward. A crane (10) according to claim 1 or 2.

4. At least two force transmission members (40) are provided, The at least two force transmission members (40) are arranged transversely to an undulating plane extending through the rotation axis of the upper rotating body. The crane (10) of claim 1.

5. The floating ballast guide (22) comprises two lattice sections (24, 26) pivotally connected to each other via a swing joint (23), The first lattice portion (24) is connected to the rear portion of the upper rotating body (14) in a manner capable of swinging about a horizontal swing axis, The drive device (28) includes a hydraulic cylinder pivotally connected to at least one of the lattice portions (24, 26). The crane (10) of claim 1.

6. The force transmission member (40) is swingably connected to one of the two lattice portions (24, 26). The crane (10) of claim 5.

7. The force introduced to one of the lattice portions (24, 26) by the force transmission member (40) is a weight force F ｇ As a result of this, an unloading torque is generated around the undulation axis (21) which is smaller than the torque generated around the undulation axis (21). A crane (10) according to claim 5 or 6.

8. The unloading force (F) that can be applied by the force transmission member (40) １ ) may be constant or variable in magnitude; The crane (10) of claim 1.

9. The force transmission member (40) is permanently connected to the floating ballast guide (22) and the upper rotating body (14). The crane (10) of claim 1.

10. An upper rotating body (14) capable of rotating about a vertical axis of rotation; A floating ballast (20) connected to the upper rotating body via a floating ballast guide (22), A crane, wherein the floating ballast guide (22) includes a drive (28) for varying the floating ballast radius, The floating ballast guide (22) is adapted to absorb the weight force (F ｇ ) and thereby generates a corresponding reaction force (F ２ a force transmitting member (40) connected to the upper rotating body (14) via at least one force transmitting member (40) configured to introduce a force to the upper rotating body (14); Actively unloading force (F １ The force transmitting member (40) generating the force can be hydraulically actuated, The force transmission member (40) is subjected to a predetermined unload force (F １ ) or reaction force (F ２ ) can be actuated or controlled by a crane controller (60) such that Crane (10).

11. The unloading force (F) generated by the force transmission member (40) １ ) or reaction force (F ２ ) may be available for load torque limiting of the crane (10); The load torque can be controlled by limiting the load torque. The crane (10) of claim 1.

12. At least two force transmission members (40) are provided, The at least two force transmission members (40) are arranged transversely to an undulating plane extending through the rotation axis of the upper rotating body, At least two force transmission members (40) are controllable or adjustable independently of each other; A crane (10) according to claim 10 or 11.

13. An upper rotating body (14) capable of rotating about a vertical axis of rotation; A floating ballast (20) connected to the upper rotating body via a floating ballast guide (22), A crane, wherein the floating ballast guide (22) includes a drive (28) for varying the floating ballast radius, The floating ballast guide (22) is adapted to absorb the weight force (F ｇ ) and thereby generates a corresponding reaction force (F ２ a force transmitting member (40) connected to the upper rotating body (14) via at least one force transmitting member (40) configured to introduce a force to the upper rotating body (14); A hinged connection is provided to the upper rotating body (14), connected to the floating ballast (20) via a first guy (31); a derrick boom (16) connected to the upper rotating body (14) via a second guy (32). Crane (10).

14. The upper rotating body (14) In addition to the floating ballast (20), a superstructure ballast (50) is provided which is stationary relative to the superstructure (14) and has a stackable counterweight element, The counterweight elements are stackable on top of the floating ballast (20). The crane (10) of claim 1.

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