EP1640309B1 - Hoisting gear, particularly the rope arrangement - Google Patents

Description

The invention relates to a hoist for a handling device of standardized containers, especially containers, with several cable drums, with up and unwound from the cable drums ropes, which are connected to a lifting and lowered by the hoist load traversed such that the ropes of individual pairs of Ropes together form an angle to the pendulum damping in and across the direction of travel of the hoist, the hoist is substantially horizontally movable.

When transporting a load suspended on a handling device, for example a standardized container such as a container, it can be observed that the load reciprocates during the movement of the handling device, in particular during startup and braking, due to the effect of the inertial forces.

Such swinging of the load must be prevented, as this is a safety hazard to ground personnel and may result in wear, material fatigue or even crash of the load due to uneven loading of the handling equipment.

In addition, it is necessary to design the handling device such that elongated loads are accommodated, which are not aligned horizontally, d. H. are tilted along its longitudinal axis. This is the case, for example, when containers are to be picked up by a truck by means of the handling device and the container is not arranged horizontally on the truck. This occurs, for example, when the truck itself is inclined, as would be the case on a ramp, or when the combination of tractor-trailer and semitrailer leads to a non-horizontal course of the cargo area. In these cases, it is necessary to lift the load at its ends and unevenly to compensate for the skew. Here, too, a swinging of the load is to be avoided.

In order to prevent or reduce the oscillation of the load and to prevent an oblique position of loads, various proposals are already known in the art.

For example, US Pat. No. 3,837,503 discloses a hoist in which, to avoid a pendulum load, the cables of the cable drums in the direction of the load receiver form a tapered angle with one another. Although this makes it possible to prevent a pendulum of the load in the direction of travel to some extent, but no compensation of an inclination of the load is provided.

From DE 37 09 960 A1, however, a device for a crane is known, in order to avoid a pendulum load, the guide cables to run approximately pyramid-shaped from the cable drums on the load-carrying means or the hook, d. H. in the direction of the load bearing form a tapered angle with each other. Although this makes it possible to prevent oscillation of the load in and across the direction of travel to some extent, however, a complex hydraulically adjustable supporting part is provided on the load receiving means to compensate for an inclined position of the load. In addition, the device allows only a balance of an inclination by off-center suspension or tilted during movement load. A targeted inclusion of an obliquely arranged load, as mentioned above, is not possible, in particular by the intended nature of the proposed "pendulum control".

DE 102 18 260 A1 discloses a hoist cable guide for a container crane, in which pivotable pulleys are used to compensate for a height-varying inclination of the cables. Due to the oblique Hubseilführung between the trolley and the spreader and a change in Hubseillängen effective oscillation damping and manipulation of the lifting device can be achieved in six degrees of freedom.

From DE 2 114 386 A a lifting device for a container is known, in which to prevent the pendulum to the attachment point on the front side tapered auxiliary ropes, which are unwound from corresponding auxiliary rope drums are used. Of these, at the same time as unwinding of hoisting ropes of drive drums, ropes of approximately the same length are unwound or wound up.

DE 43 25 946 A1 describes a damping and positioning device in which the pendulum damping force acted upon guide cables are provided in addition to the hoisting rope. The guide ropes are depending on the geometric conditions such as distance of the force generator and lifting height, the acceleration behavior of the crane drives and the mechanical load capacity of the cat and also under consideration of several motion variables such as pendulum angle, pendulum speed and acceleration and force curve controlled.
DE 44 25 777 C2 describes a hoist with at least two hoisting ropes, which run in a spread angle to each other and attached to the load crossmember. In this case, the cable drum axis and / or the attachment points of the load in the direction of travel, ie in the damping direction, so that the slope of the rope grooves of the cable drum is the same right threaded section and in the left-hand threaded section and that the spread of the hoisting ropes regardless of the height and position of the load is approximately the same size.

From US 2,190,093 a lifting system for a camera and a stage lighting is known, in which the hoisting ropes are connected via elastic elements with the load crossmember.

The object of the invention is therefore to provide a hoist for a handling device that allows a pendulum damping in and across the direction of travel of the hoist and also allows the targeted lifting oblique loads, especially elongated loads, such as containers.

This object is achieved by the reproduced in claim 1 invention.

The fact that the ropes of the hoist for active tilting of the lifting beam about an axis transverse to its longitudinal direction are independently up and unwound, it is possible that the load bar while maintaining the pendulum damping properties in the longitudinal direction obliquely parked normalized container or on accordingly can turn off oblique pads. This is achieved by the special geometry of the arrangement of the cable drums and ropes. Thus, the load traverse can be tilted in an active manner about its transverse axis to accommodate oblique loads or set them off obliquely. The pendulum-poor moving of the load enables accurate picking up and setting down of the load, whereby the turnaround time and also the handling costs can be minimized.

In this case, tilt angle of the load of up to 20 from the horizontal, preferably up to 12 and particularly preferably up to 8 degrees can be compensated.

Also, the ropes are divided with respect to the sides of the load crossbar in frontal and longitudinal cable pairs.

In addition, four rope pairs, i. H. a total of eight ropes intended for lifting and lowering. Per pair of traverses a pair of cables is provided in each case, wherein the ropes of the respective pair of cables either form an angle to the load spreader or tapering angle with each other.

In this case, the respective longitudinal pair of cables is connected to the ends of the longitudinal side of the load traverse and thus also at the ends of the front side.

Furthermore, a pair of cables is provided per Lasttraversenstirnseite having a tapered in the direction of the load cross-angle. It is advantageous if the ropes of the pair of cables are mounted approximately centrally on the load crosshead face. Thus, a good pendulum damping in the direction parallel to the front side and thus is achieved transversely to the longitudinal direction of the normalized container.

Preferably, the respective end-side pair of cables may be connected at about the middle of the end face of the load cross-piece with this.

Furthermore, a pair of cables is preferably provided per load crossmember longitudinal side, which has an angle which spreads or widening in the direction of the load crossmember. It is again advantageous if the ropes of the pair of cables are fastened approximately at the ends of the load crossmember longitudinal side. Thus, a good pendulum damping in the direction parallel to the longitudinal side and thus in the longitudinal direction of the normalized container is achieved.

Advantageously, the ropes of a pair of cables each run from different double rope drums. It makes sense if the ropes of a pair of cables from the respective rope groove of the double rope drum in the same direction Seilablaufrichtungen exhibit. This allows a simple construction of the cable geometry according to the invention.

Preferably, one pair of cables on the respective cable drum has a rope outlet point downwards per load traverse longitudinal side and, corresponding to each front side of the load cross-member, a cable pair has a cable outlet point upwards.

To deflect the upwardly expiring ropes of the pairs of cables, so the ropes of the pairs of cables of the load crosshead end faces, downwards pulleys are conveniently provided. Per rope umzulenkendes a pair of cables can be provided two pulleys. It makes sense if their axes of rotation are perpendicular to each other. Thus, it can be achieved that despite the arrangement of the cable drums specified below, the deviation of the inlet of the cables in the cable drums despite the angle formed thereby is less than 4 degrees.

It makes sense, if one of the ropes of a double rope drum of the respective rope groove up and the other of the ropes of the respective rope groove runs down.

It is also possible that the axes of rotation of the double rope drums of a hoist gear are arranged in alignment with each other. For this purpose, the axes of rotation of the double rope drums of the hoist gear can be arranged parallel to each other and possibly in a common plane. This results in a particularly simple manner, a compact arrangement of the structure.

In particular, the hoist two symmetrically arranged hoist gear, each having two symmetrically arranged double rope drums for receiving or dispensing of two ropes each comprise.

The separate control of the cable drum drives, for example, their hoist gear, although via an electronic control, but it may geometrically still come to deviations in the unwound pitches of acting on the different sides of the load trailing ropes and thus possibly to the occurrence of slack rope. To compensate for such small deviations of the ropes, it makes sense if some of the ropes over in the rope longitudinal direction limited elastic elements are connected to the load crossmember. For this purpose, the elastic elements may have disc springs. These can be arranged, for example, in the possibly designed as a clamping bolt-like fastening elements of the cable ends on the load crossmember. The fasteners for the remaining ropes then have rigid mounting elements instead of the disc springs.

Advantageously, the load cross-member attachment points for a load-receiving means, in particular a spreader, on.

• Figur 1 eine Ansicht eines Abschnittes einer Containerbrücke mit einem erfindungsgemäßen Hubwerk;
• Figur 2das Hubwerk aus Figur 1 in einer schematischen Seitenansicht und mit gekippter Lasttraverse;
• Figur 3das Hubwerk aus Figur 1 in einer perspektivischen Ansicht von schräg oben ohne Stützrahmen;
• Figur 4das Hubwerk aus Figur 1 in einer Seitenansicht;
• Figur 5das Hubwerk aus Figur 1 in einer weiteren Seitenansicht und
• Figur 6die Befestigung der Seile an der Lasttraverse im Detail.

Further features, details and advantages of the invention will become apparent from the following description of the drawing. Show it:

• Figure 1 is a view of a portion of a container bridge with a hoist according to the invention;
• FIG. 2 shows the hoisting gear from FIG. 1 in a schematic side view and with a tilted load cross-member;
• Figure 3das hoist of Figure 1 in a perspective view obliquely from above without support frame;
• Figure 4das hoist of Figure 1 in a side view;
• Figure 5das lifting mechanism of Figure 1 in a further side view and
• FIG. 6 shows the attachment of the cables to the load cross member in detail.

1 shows a view of a designated as a whole with 1 bridge crane for containers. This has in a conventional manner a substantially horizontally extending main carrier 4, along which a trolley 5 on rails 6 is movable. On the trolley 5, an upper frame 7, the so-called Katzoberrahmen is arranged, which is rotatably connected about a vertical axis with a lower frame 8, the so-called Katzdrehrahmen. At the Katzdrehrahmen 8 an inventively ausgestaltetes hoist 9 is provided. On the cat turning frame 8 and an approach 2 is suspended with a car 3. To the Hoist 9 hangs a load traverse 10, on which in turn a spreader 11 is provided for receiving a container.

As a result of the configuration according to the invention, the load cross-member 10 of the hoisting gear 9, as shown in FIG. 2, can tilt specifically about an axis transversely to the longitudinal direction of the load cross member 10, in order to be able to receive inclined oblong loads, such as, for example, a container 12 or to place it at an angle , After attaching the container 12 to the spreader 11, the cables are wound up by targeted control of the cable drums or their drives such that the load cross member 10 is aligned horizontally for the transport of the container 12. In this case, oscillation is prevented in or across the direction of travel or a pendulum damping is achieved, since the cables, in particular pairs of cables, form angles between them.

The structure of the hoist 9 will now be described with reference to Figures 3, 4 and 5. For the sake of clarity, only the hoist 9 and not the trolley frame 8 are shown in FIG.

The hoist 9 comprises four cable drums, of which two have 13, 14 and 15, 16 mutually aligned axes of rotation and of a common centrally between the cable drums 13, 14 and 15, 16 lying gear 17 and 18 and associated with respect to the double rope drums 13, 14, 15, 16 external motor 19 and 20 are driven. The double cable drum pairs 13, 14 and 15, 16 are opposite each other, so have in a preferably horizontal plane lying parallel axes of rotation. In this case, the respective drives are separately controllable, but coupled via a non-illustrated electronic control with each other to enable one hand, the targeted control of the individual sides of the hoist for tilting the load cross member 10 and on the other hand, a horizontal lifting or lowering the load cross-piece 10. Each of the double rope drums 13, 14, 15 and 16 has an inner rope groove and a spaced therefrom and laterally adjacent rope groove.

The drives and cable drums are attached to a support frame 21, which also carries to be described pulleys for deflecting the ropes. In Figure 3 was from For clarity, the representation of the support frame 21 omitted, which is shown in Figures 4 and 5, however.

The double rope drums 13 and 14 and 15 and 16 of the double rope drum pairs each have the same direction of rotation. The directions of rotation of the Doppelseiltrommelpaare 13, 14 and 15, 16, however, are opposite to each other.

Of the double rope drums 13, 14, 15, 16 run rope pairs 22, 23, 24, 25 to the load traverse 10, with which they are connected by cable fasteners 26. Per side of the rectangular in cross-section load crossmember 10, a pair of cables is provided.

The pairs of cables 22 and 23 are respectively connected to the longitudinal sides 10 A, 10 B of the load cross-member 10 and close in the direction of the spreader 10 spreading or widening angle. The respective ropes 22 A, B and 23 A, B of the cable pairs run for this purpose directly from the respective inner cable groove 14 A, 16 A and 13 A, 15 A down to the load traverse 10, wherein the cable drums 13, 14, 15, 16 are arranged on the support frame 21 such that their distance in the longitudinal direction of the load cross member 10 is less than that of the load cross member 10 itself, so that in the attachment of the cable ends at the ends of the respective load cross-member longitudinal side results in an expanding angle, the size of course the lifting height of the load cross member 10 depends. Since the ropes of the inner cable grooves, which are respectively denoted by the addition "A" expire, the arrangement of which corresponds approximately to the width of the load cross member 10, the ropes run about in a plane with the load crossmember longitudinal side to this.

The pairs of cables 24 and 25, however, are each connected approximately at the center of the respective end faces 10 C, 10 D of the load cross member 10 and form a tapering in the direction of the load cross member 10 or tapered angle. The respective ropes 24 A, B and 25 A, B of the cable pairs to run from the respective outer cable groove 14 B, 16 B and 13 B, 15 B initially upwards. In order to redirect the ropes down to the load crossmember face 10 C, 10 D, two deflection rollers 27 A, B are each per rope. 28 A, B; 29 A, B; 30 A, B; provided, the axes of rotation are each approximately perpendicular to each other and extend horizontally.

The upper pulleys 27 A, 28 A, 29 A and 30 A are above the cable drums and arranged in the longitudinal direction of the load cross-member 10 after the end faces 10 C, 10 D out. The lower pulleys 27 B, 28 B, 29 B and 30 B are located approximately at the same height with the cable drums and about in a vertical plane with the end faces 10 C, D. By the double deflection of the cables 24 A, B and 25 A, B is formed on the one of the tapered angle. On the other hand, it is possible that, despite the specified arrangement of the cable drums, the deviation of the inlet of the ropes in the rope grooves despite the angle formed thereby is less than 4 degrees. Also, the ropes are thus about in a plane with the respective load crosshead front side to this.

In addition, as will be explained below, it is achieved that the angles of the cable pairs 24 and 25 of the load crosshead end faces approximately always correspond to the angles of the cable pairs 22 and 23 of the load crossmember longitudinal sides, i. H. the changes in the angle when lifting or lowering relative to each other about the same, so that the unwound or wound cable lengths are also approximately equal for horizontally oriented load cross-member 10. The load to be lifted is thus evenly distributed on the ropes.

The cable ends of the pairs of cables 22, 23 are at the ends of the load cross-long sides 10 A, B fixed so that their attachment points with the attachment points of the cable ends of the cable pairs 24, 25 of the load cross-faces are in line, so aligned, so that they a common axis form the tilting of the load carrier 10 about an axis transverse to its longitudinal direction. In this case, the tilt axis of the load cross member 10 and the common axis formed by the attachment points are approximately parallel.

The cable ends of the cable pairs 22, 23 are connected to the ends of the load cross-member longitudinal sides via angled flaps 31. The tabs 31 are in turn fixed to tubular cross members 32 of the load cross member 10. At these cross members 32 which extend parallel to the end faces 10 C, D of the load cross member 10, 25 more tabs 41 are provided for approximately central attachment of the cable ends of the cable pairs 24, 25. At these tabs 41 and the attachment points for the spreader 11 are provided.

Despite the structure described, in particular the arrangement of the cable drums, pulleys and ropes, it comes with long rope lengths that the drain points of the rope drums of the cables of the cable pairs 22, 23 move in opposite directions to those of the cables of the cable pairs 24, 25, which is minor Differences in the angle and thus the pitch of the ropes of the end faces 10 C, D compared to the angles of the ropes of the long sides 10 A, B causes. This will be discussed below.

To compensate for such minimal deviations of the rope lengths of the ropes, the ropes 24 A, 24 B; 25 A and 25 B in each case in the longitudinal direction of the cable elastic fasteners 26 with the load cross-member 9 is connected (see Fig. 6). For this purpose, the elastic fasteners 26 disc springs 33 which are arranged within the fasteners. The fasteners 26 for the remaining ropes 22 A, 22 B, 23 A and 23 B do not have this plate spring 33 and thus behave rigidly.

The respective ropes run into the fasteners 26 and are connected there via a cable lock 34 each with an approximately horizontally extending pin 35. The bolts 35 forward the load in each case via side parts 36 to cross members 37, which together form a U-shaped bracket. At these cross beams 37 short chains 38 are attached via a in the longitudinal direction of the attachment 26, that is movable in the cable direction bolt 39, which passes through the cross member 37 each. The bolt 39 has a nut 40 which encloses the cup springs 33 between itself and the cross member 37. Thus, the fasteners 26 can also perform changes in the cable angle and at the same time cause a small length compensation on the plate springs 33. For the rigid fastenings 26 of the ropes 22 A, 22 B, 23 A and 23 B, the plate springs 33 are replaced by rigid, not shown, hollow cylinder.

In the following, rope length differences and adjusting angles obtained by way of example for different lifting heights are described.

In the raised position, the angle between the ropes 22 B and 25 A and the angle between the ropes 25 A and 25 B is about 32.5 degrees ± 0.5 degrees with horizontally or horizontally arranged traverse 10. The difference in the rope length of Rope 22 B between drain point on the cable drum 16 B and the Attachment point on the load spreader 10 and the rope 25 B between the drain point on the guide roller 29 B and the attachment point to the spreader 10 is about 2 mm, which is compensated by the elastic fasteners 26.

In the half lowered position of the load cross member 10, the angle between the ropes 22 B and 25 A and the angle between the ropes 25 A and 25 B at horizontally or horizontally oriented load traverse 10 about 10 degrees ± 0.5 degrees. The difference of the rope length of the rope 22 B between the drain point on the cable drum 16 B and the attachment point to the load cross member 10 and the rope length of the cable 25 B between drain point on the guide roller 29 B and the attachment point to the load cross member 10 is about 3mm, by the elastic fasteners 26 is balanced.

In the lowered position of the load cross-piece 10, the angle between the ropes 22 B and 25 A and the angle between the ropes 25 A and 25 B at horizontally or horizontally oriented load cross-piece 10 about 6 degrees ± 0.5 degrees. The difference of the rope length of the rope 22 B between the drain point on the cable drum 16 B and the attachment point to the load traverse 10 and the rope length of the rope 25 B between the drain point on the guide roller 29 B and the attachment point on the load cross-piece 10 is about 8 mm, the through the elastic fasteners 26 is balanced.

LIST OF REFERENCE NUMBERS

1

crane

2

boarding

3

cabin

4

cab

5

trolley

6

rails

7

Katz upper frame

8th

Katz rotating frame

9

hoist

10

Last Traverse

11

spreader

12

Container

13

Double cable drum

13A, B

cable groove

14

Double cable drum

14A, B

cable groove

15

Double cable drum

15A, B

cable groove

16

Double cable drum

16A, B

cable groove

17

transmission

18

transmission

19

engine

20

engine

21

support frame

22

cable pair

23

cable pair

24

cable pair

25

cable pair

26

cable fixings

27

idler pulley

28

idler pulley

29

idler pulley

30

idler pulley

31

flap

32

crossbeam

33

Belleville spring

34

cable lock

35

bolt

36

side panel

37

crossbeam

38

Chain

39

bolt

40

mother

41

flap

Claims (20)

1. Hoisting mechanism (9) for a cargo-handling apparatus for standardised receptacles, in particular containers (12), having a plurality of cable drums (13, 14, 15, 16), with cables (22 A, B, 23 A, B, 24 A, B, 25 A, B) which can be wound and unwound from the cable drums and which are connected to a load cross-piece (10), which can be raised and lowered by the hoisting mechanism, in such a way that the cables (22 A, B; 23 A, B; 24 A, B; 25 A, B) of individual pairs of cables (22, 23, 24, 25) form an angle with each other for damping oscillation in, and transverse to, the direction of travel of the hoisting mechanism (9), wherein the hoisting mechanism (9) can travel substantially horizontally,
   characterised in that
   the cables (22 A, 23 A, 24 A, 24 B; 22 B, 23 B, 25 A, 25 B) of the hoisting mechanism (9) can be wound and unwound independently of each other to actively tilt the load cross-piece (10) about an axis transverse to its longitudinal direction, that the cables (22 A, B; 23 A, B; 24 A, B; 25 A, B) are divided into end-face (24, 25) and long-side (22, 23) cable pairs with respect to the sides (10 A, B, C, D) of the load cross-piece, that the respective long-side cable pair (22, 23) is connected to the ends of the long side (10 A, B) of the load cross-piece (10), that the cables (24A, B; 25 A, B) of a cable pair (24, 25) form an angle with each other, which tapers in the direction of the load cross-piece (10), for oscillation damping purposes so that their attachment points lie on a line with the attachment points of the cable ends of the cable pairs (24, 25) of the load cross-piece end faces so that they form a common axis with the tilting of the load cross-piece (10) about an axis transverse to its longitudinal direction.
2. Hoisting mechanism as claimed in claim 1, characterised in that approximately in the middle of the end face (10 C, D) of the load cross-piece (10) the respective end-face cable pair (24, 25) is connected thereto.
3. Hoisting mechanism as claimed in claim 2, characterised in that for the purpose of oscillation damping the cables (22A, B; 23 A, B) of a cable pair (22, 23) form an angle with each other which widens in the direction of the load cross-piece (10).
4. Hoisting mechanism as claimed in any one of the preceding claims, characterised in that the cables (22 A, B; 23 A, B; 24 A, B; 25 A, B) of a cable pair (22, 23, 24, 25) each run off from different double cable drums (13, 14, 15, 16).
5. Hoisting mechanism as claimed in claim 4, characterised in that the cables (22 A, B; 23 A, B; 24 A, B; 25 A, B) of a cable pair (22, 23, 24, 25) of the respective cable groove (14 A, 16 A; 13 A, 15 A; 14 B, 16 B; 13 B, 15 B) of the respective double cable drums (13, 14, 15, 16) run off in the same directions.
6. Hoisting mechanism as claimed in claim 4 or 5, characterised in that for each load cross-piece longitudinal side (10 A, B) a cable pair (22, 23) has a cable run off point in the downwards direction.
7. Hoisting mechanism as claimed in claim 4 or 5, characterised in that for each load cross-piece end face (10 C, D) a cable pair (24, 25) has a cable run off point in the upwards direction.
8. Hoisting mechanism as claimed in any one of the preceding claims, characterised in that the respective end-face cable pair (24, 25) of the load cross-piece end face (10 C, D) forms an angle which tapers in the direction of the load cross-piece (10).
9. Hoisting mechanism as claimed in any one of the preceding claims, characterised in that the respective long-side cable pair (22, 23) of the load cross-piece longitudinal side (10 A, B) forms an angle which widens in the direction of the load cross-piece (10).
10. Hoisting mechanism as claimed in any one of claims 7 to 9, characterised in that the cable rollers (27, 28, 29, 30) are provided to deflect the end-face cables (24 A, B, 25 A, B) of the respective front cable pair (24, 25) downwards.
11. Hoisting mechanism as claimed in claim 10, characterised in that for each cable (24 A; 24 B; 25 A; 25 B) of the end-face cable pair (24, 25) at least two cable rollers (27 A, B; 28 A, B; 29 A, B; 30 A, B) are provided.
12. Hoisting mechanism as claimed in claim 11, characterised in that the axes of rotation (27 A, B; 28 A, B; 29 A, B; 30 A, B) of the cable rollers are approximately perpendicular to each other.
13. Hoisting mechanism as claimed in any one of the preceding claims 9 to 12, characterised in that one of the cables (22 A, 24 A; 23 A, 24 B; 22 B, 25 A; 23 B, 25 B) of a double cable drum (13; 14; 15; 16) of the respective cable groove (13 A, B; 14 A, B; 15 A, B; 16 A, B) runs off in the upwards direction and the other of the cables (22 A, 24 A; 23 A, 24 B; 22 B, 25 A; 23 B, 25 B) of the respective cable groove (13 A, B; 14 A, B; 15 A, B; 16 A, B) runs off in the downwards direction.
14. Hoisting mechanism as claimed in any one of the preceding claims 9 to 13, characterised in that the axes of rotation of the cable drums (13, 14; 15, 16) of hoisting mechanism gearing (17; 18) are disposed in alignment with each other.
15. Hoisting mechanism as claimed in any one of the preceding claims 9 to 14, characterised in that the axes of rotation of the double cable drums (13, 14; 15, 16) of the hoisting mechanism gearing (17, 18) are disposed in parallel with each other.
16. Hoisting mechanism as claimed in claim 15, characterised in that the axes of rotation of the double cable drums (13, 14; 15, 16) of the hoisting mechanism gearing (17, 18) are disposed in a common plane.
17. Hoisting mechanism as claimed in any one of the preceding claims, characterised in that the end-face cables (24 A, B; 25 A, B) are connected to the load cross-piece (10) via elements (26) which are elastic in the cable longitudinal direction.
18. Hoisting mechanism as claimed in claim 17, characterised in that the elastic elements (26) have spring washers (33).
19. Hoisting mechanism as claimed in any one of the preceding claims, characterised in that the load cross-piece (10) has attachment points (41) for a load-receiving means, in particular a spreader (11).
20. Hoisting mechanism as claimed in any one of the preceding claims, characterised in that the cable drum drives (17, 19; 18, 20) are coupled by means of an electronic control.

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