EP1819627B1 - Dispositif de levage - Google Patents

Dispositif de levage Download PDF

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Publication number
EP1819627B1
EP1819627B1 EP05799624A EP05799624A EP1819627B1 EP 1819627 B1 EP1819627 B1 EP 1819627B1 EP 05799624 A EP05799624 A EP 05799624A EP 05799624 A EP05799624 A EP 05799624A EP 1819627 B1 EP1819627 B1 EP 1819627B1
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EP
European Patent Office
Prior art keywords
lifting device
lower frame
load lifting
tensioning
tensioning elements
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EP05799624A
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German (de)
English (en)
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EP1819627A1 (fr
Inventor
Franz Ehrenleitner
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Individual
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Individual
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C13/00—Other constructional features or details
    • B66C13/04—Auxiliary devices for controlling movements of suspended loads, or preventing cable slack
    • B66C13/08—Auxiliary devices for controlling movements of suspended loads, or preventing cable slack for depositing loads in desired attitudes or positions
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C1/00—Load-engaging elements or devices attached to lifting or lowering gear of cranes or adapted for connection therewith for transmitting lifting forces to articles or groups of articles
    • B66C1/10—Load-engaging elements or devices attached to lifting or lowering gear of cranes or adapted for connection therewith for transmitting lifting forces to articles or groups of articles by mechanical means
    • B66C1/12—Slings comprising chains, wires, ropes, or bands; Nets
    • B66C1/20—Slings comprising chains, wires, ropes, or bands; Nets specially adapted for handling vehicles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C13/00—Other constructional features or details
    • B66C13/04—Auxiliary devices for controlling movements of suspended loads, or preventing cable slack
    • B66C13/06—Auxiliary devices for controlling movements of suspended loads, or preventing cable slack for minimising or preventing longitudinal or transverse swinging of loads

Definitions

  • the invention relates to a lifting device, in particular for the automotive industry, with a top frame and a lower frame arranged thereunder according to the preamble of claim 1 and EP 123 846 A ,
  • Lifting devices are used to lift and transport heavy loads, especially car bodies in the automotive industry, and must therefore withstand high loads. On rails coming down from the ceiling of production halls such lifting devices are movably mounted and transport the vehicle body to be manufactured from one work step to the next. In most cases, the load lifting device and the load hover over the heads of many workers who weld, assemble, cabling, etc. at the bottom of the body.
  • a load lifting device is for example from the EP 1 106 563 B1 known. It consists of a top frame, a subframe and provided therebetween, connected to a drive traction cables. The traction cables are guided over pulleys on a motor-driven drum. In addition to fully vertical ropes, ropes are also provided, which extend partially obliquely to the vertical. Such a cable extends from the upper frame obliquely to the sub-frame, where it is steered around a roller and then extends vertically in the direction of the upper frame, where it is then connected to the same drive, which is also intended for the vertical cables. The partially inclined ropes serve to increase the stability of the sub-frame and the load hanging thereon.
  • the DE 23 19 647 discloses a crane for lifting loads.
  • a loading member on which the loads to be transported are attached, hangs on lifting ropes whose suspension points are in the carriage of the crane.
  • auxiliary cables are provided which are guided to a separate cable drum and which extend obliquely both to the longitudinal direction and to the transverse direction of the loading member.
  • the loader itself is rectangular and all ropes, ie both auxiliary and hoisting ropes, engage in the corner areas of the loader. This design is designed to allow accurate load placement without causing larger pendulum motion. A pivoting of the load about a horizontal axis is not provided and with such a device also difficult and limited possible. All ropes or rope lengths would have to be coordinated in such a maneuver in a strictly defined manner to each other.
  • the US 4,705,180 discloses a lifting device consisting of vertically arranged pull ropes and in addition to four auxiliary ropes extending substantially along the edges of a pyramid to the loading platform. As in the previous publication, all ropes in the corner areas of the loading platform also attack here. A pivoting about a horizontal axis is not intended with such a device and also not possible, since all four traction cables are wound on the same cable drum.
  • the US 5,769,250 (or the corresponding EP 0 793 615 B1 ) discloses a lifting device in which a loading platform can be raised or lowered by means of cables. All ropes acting in this device are aligned obliquely to the horizontal, wherein in each case a traction means, consisting of a roller attached to the loading platform and a revolving rope, engages in a corner region of the loading platform. In the area of the shorter sides of the loading platform are located between the arranged in each corner pulleys two more pulleys, run around the additional auxiliary ropes.
  • the device disclosed in this document is based on the use of four identical but mechanically independent control mechanisms, which are tuned to a travel information of each auxiliary cable and the respective rotational speed of the motor connected to the auxiliary cable or the drum. It can be damped by such a device occurring in a horizontal plane vibrations, however, a pivoting of the position platform to a horizontal axis is not possible and not intended.
  • the present invention has the object to achieve these objectives and to avoid the problems known from the prior art, and to propose a load lifting device which ensures a high stability of the lower frame including receiving frame against forces acting on it, has a low dead weight and thereby at the same time provides the best possible safety for the people working on the lifting device, and which can be pivoted about a horizontal axis.
  • a load lifting device which ensures a high stability of the lower frame including receiving frame against forces acting on it, has a low dead weight and thereby at the same time provides the best possible safety for the people working on the lifting device, and which can be pivoted about a horizontal axis.
  • large pivoting angle should be feasible and complicated control and regulating mechanisms are bypassed by a simple basic design.
  • the slackening of traction means should be prevented.
  • the drive of the traction means is hydraulically coupled to a pressure accumulator. This can be achieved effectively shock and collision shocks.
  • the drive for the traction cables and the drive for the bracing cables are hydraulically connected to each other with respect to the power supply via a pressure accumulator. Although they are mechanically decoupled with respect to the rotation, but can be powered by the same energy source.
  • the drive for the traction cables and the drive for the tensioning cables are completely separated from each other.
  • a first motor is used to drive the vertical ropes, while the second motor is used to unwind the inclined ropes or bracing cables.
  • this drive does not have a constant gear ratio between the lifting movement and the rotary drive.
  • the ratio of the first motor is constant, resulting in the lowest possible drive power.
  • a 2-axis control can be used, or it can be a corresponding readjustment, by detecting a relative displacement of two, for example via a preloaded spring coupled elements to each other, for example by inductive data acquisition, holding the tension cables at a constant voltage. If the lifting motor fails, the second motor can now hold the load. Required are only correspondingly claimable traction means, a reliable transmission and appropriately designed brakes. It is not necessary that the second motor can lift the load.
  • the load lifting device is characterized in that for tilting the subframe at least one vertical traction means has a drive independent of the other vertical traction means.
  • the vertical traction system has two or more motors, so that e.g. two traction means are wound by a single motor, while the rest are driven by another motor.
  • all traction means have their own engine, which allows tilting in all directions.
  • the pivoting or tilting of the subframe is similar to playing with a string puppet figure.
  • At least one biasing means running obliquely to the vertical has a drive independent of the other biasing means extending obliquely to the vertical. If the load is tilted by a plurality of independently controllable drives in the traction system, the required tension in all bracing means can be maintained by this measure without one of the bracing means becoming slack.
  • the system is determined kinematically consisting of upper frame, subframe, traction means and Verspannstoff, preferably kinematically overdetermined. This ensures stability with respect to forces acting horizontally on the subframe and rotation about the vertical.
  • the tensioning means engage the subframe at two points, wherein the connecting line between the two points of attack in essentially by the vertical projection of the center of gravity of the subframe in the points of attack comprehensive horizontal plane goes.
  • the bracing means engage the subframe at at least three points, the outer contour of the at least three points of attack enclosing the vertical projection of the center of gravity of the subframe into the horizontal plane comprising the points of application.
  • the contour of the biasing means projected vertically into the horizontal plane of the center of gravity of the subframe encloses the center of gravity of the subframe.
  • Fig. 1 . 2 and 3 show schematically from various points of view (without pulleys, drums and motors) a load lifting device with a top frame 1, a lower frame 2 arranged underneath, which is held by ropes 3, 4 on the upper frame 1.
  • the upper frame 1 can, as in Fig. 7 indicated, provided with a movable rail 7 on a corresponding suspension 6 or be attached directly to the ceiling of an assembly hall.
  • the frames 1, 2 are usually quadrangular, but they could also triangular, rounded, circular, oval or take any other form and optionally be provided with braces. You can run as a three-dimensional framework and / or be integrally connected to the receiving frame 8
  • the cable system consists of a group of substantially vertical ropes 3 and a group of obliquely to the vertical ropes 4.
  • a rotation about a horizontal axis which consists of vertical ropes 3 group have at least three, attacking at the corners of a triangle ropes.
  • four or more vertical cables 3 are of course used, on the one hand for safety and stability reasons, on the other hand almost exclusively rectangular, preferably rectangular sub-frames 2 are used.
  • the traction cables 3 preferably engage in the region of the corners or in the region of the outer edges of the frames 1, 2 and are arranged so that all traction cables are loaded with the same load substantially equal.
  • the center of gravity of the structure carried by the cables consisting of the support frame 8 for the load and the load 9 itself, is substantially below the center of gravity of the subframe 2.
  • the obliquely to the vertical ropes 4 are also called bracing cables. They serve to increase the stability of the load lifting device relative to the forces acting on the lower frame 2 and the receiving frame 8 for the load and thus to suppress a rocking or swinging of the lower frame 2 with respect to the upper frame 1. Such forces occur, for example, as a result of accelerations or delays when starting from one workstation to the next, with the inertia of a load weighing several tons coming to bear. Much less impact on people or tools transferred from forces.
  • the group consisting of obliquely tensioned ropes 4 must also comprise at least three ropes, which act on at least two points 5 on the subframe 2 with sufficient biasing force of the ropes.
  • the three bracing cables 4 must lie in different vertical planes. For example, they can be as in Fig. 3 shown, with just any of the four ropes 4 would be inconceivable.
  • at least two as far as possible from each other remote attack points 5 must be provided both on the subframe 2 and on the upper frame 1.
  • the three vertical cables 3 prevent rotation about the horizontal axes and displacements along the vertical, while the three bracing cables 4 suppress displacements along the horizontal directions and rotations about the vertical.
  • Such a system is also referred to as kinematically determined in mechanics.
  • the lower frame 2 and the upper frame 1 are quadrangular, the vertically extending ropes 3 attack at the corners and the obliquely to the vertical ropes 4 at opposite side edges of the quadrangle.
  • a pair of cables is provided for two opposite sides of the quadrilateral, wherein the points 5 of the two Verspannseile 4 of a pair coincide and form the two Verspannseile starting from the common point 5, a V-shaped structure.
  • the belonging to this pair of cables ropes 4 are symmetrical with respect to the vertical plane through the common point 5 and by the on the opposite side of the sub-frame 2 located attack point 5 of the other pair of cables goes.
  • the load is evenly distributed over all the tensioning cables 4.
  • Clamping cables 4 of equal length also represent a preferred embodiment for the following reason: With the same length, all the tensioning cables 4 can be wound up with a single drive. In contrast, at different angles to the vertical and therefore different cable lengths, a separate drive with different rotational speed would have to be provided for each tensioning cable 4 in order to prevent ropes becoming limp when lifted.
  • the connecting line between the points 5 on the sub-frame 2 is preferably substantially by the projection of the center of gravity of the sub-frame 2 in the horizontal plane containing the points 5 ( Fig. 3 ) or is located at unevenly distributed load above the expected center of gravity.
  • the tensioning cables 4 take over the load without causing a strong pivoting of the receiving device 8 together with the load 9. Since the center of gravity of the load 9 is far below the sub-frame 2, deviations of a few centimeters hardly affect.
  • the sub-frame is anyway designed so that its center of gravity is substantially above the expected center of gravity of the load.
  • the center of gravity of the subframe 2 should in any case lie within an outline created by the vertical projection of the tensioning cables into the plane of the subframe 2.
  • the outer outline the attack points 5 the projection of the center of gravity of the sub-frame 2 in the attack points 5 comprehensive horizontal plane encloses.
  • FIG. 3 Another variant (not shown) is the in Fig. 3 shown tetrahedron by 45 ° to rotate through the center of the quadrilateral vertical axis and move the points 5 to the corners of the frame. This gives the bracing even stronger inclination, resulting in better stability. However, it comes at the corners when using pulleys 10 to space problems that can be solved by slight displacement of the points 5.
  • guy ropes are possible, e.g. 8, which run along the edges of two interpenetrating tetrahedra.
  • the important thing is that the bracing cables give the system stability and can absorb the entire load if the vertical system fails.
  • the group consisting of Verspannstoffn 4 has a separate from the drive of the vertical traction means 3 drive.
  • the two groups are therefore drivingly decoupled from each other completely. This does not mean that the drive for the Verspannstoff 4 operates independently. He must "go along” and maintain the tension in the tensioning means when lifting and lowering the load.
  • the drive of the vertical traction means has a constant gear ratio between the lifting movement and the rotation of the drum 11 to be wound up with the traction means.
  • the drive for winding the oblique biasing means has no constant gear ratio between the lifting movement and the rotation. Since in normal operation but only small forces are to be transmitted - the lifting movement is indeed mainly by the vertical Ceiffenantrieb -, this is not a problem. It is only a control of this drive necessary to the Verspannstoff 4 at any time of the raising or lowering operation in to keep it taut and thus provide stability.
  • a 2-axis control with corresponding sensors can be used to determine the absolute position of the tensioning means.
  • a readjustment can also be due to a displacement of two elements zueinender, for example via a preloaded spring, wherein the displacement can be determined by an inductive system, take place.
  • the rotational speed of the motor can be readjusted via a control unit.
  • Controls to keep a certain (rope) voltage over the rotational speed of a motor constant, are well known in the art and need no further explanation.
  • the characteristic of separate drives means that two birds are killed at the same time: the stability of a lifting device is increased by the use of bracing cables, while at the same time without significant weight gain - for the realization of this measure, only one additional, compared to the lifting motor, is much smaller dimensioned motor and a drum required - much more safety for the workers and the load to be kept is guaranteed.
  • Fig. 4 . 5 and 6 show a load lifting device with a tilted sub-frame 2.
  • the vertical traction system that is that which consists of vertical traction means.
  • two of the four vertical Traction means operated by separate motors.
  • the sub-frame 2 can be tilted, for example, to allow workers access to hard to access body parts. If like in Fig. 6 illustrated the connecting line of two points 5 simultaneously represents the axis of rotation during tilting, it is sufficient if the Verspannstoffsystem has a single motor.
  • the traction means and Verspannstoff are usually out of the direction of the lower frame 2 coming over pulleys 12 or directly on grooves or guides provided with drums 11.
  • the drums 11 serve to wind up the tension and tensioning means and are operated by motors 13.
  • Pulleys 12, drums 11 and motors 13 are mounted or mounted on the upper frame 1.
  • slightly inclined leadership of the vertical traction means is due to obliquely guided grooves in the drums 11 and thus changes slightly when lifting and lowering the load.
  • Fig. 13 to 15 the detailed embodiment of the opening in a single point 5 on the lower frame 2 clamping means in different views.
  • these are simple ropes, however, as already mentioned above, pulley-type or tensioning and tensioning means consisting of bands can also be used.
  • Fig. 13 shows only a section of the sub-frame 2, but on the opposite side of the sub-frame, the connection of the other two Verspannseile identical, preferably formed mirror-symmetrical.
  • the two Verspannseile 4 form more or less a pair of pointers, which has the same axis. Under pointer pair are understood in this application, two straight lines that lie substantially in one plane and emanate at least approximately from a single point. It can be clearly seen that the two Verspannseile 4 transition at its end in a joint 14, which allow the rotation of the lower frame 2 with respect to the Verspannseile 4 about an axis 15 through the two opposite points of attack 5 of the two Verspannseile 4 on the subframe is defined. In the illustrated embodiment, this is a universal joint, one axis of which is normal to the axis of rotation 15 and normal to the vertically extending traction means 3 and the second axis is aligned substantially normal to the Verspannstoff 14. The end of the Verspannstoff 4 is attached to brackets 16 which form part of the universal joint and are rotatable about the same axis. Of course, also conceivable hinges, ball joints and the like.
  • the imaginary extensions of the cables or the straight lines defined by the bracing means 4 intersect each other at a point which lies on the axis of rotation 15. Slight deviations from this requirement are permissible as long as the clamping means remain taut when the subframe is swiveled. In other words, the changes in position of the ends of the bracing means occurring during pivoting of the subframe must be smaller than the length changes of the bracing means made possible by the self-elongation. However, in order to define a horizontal axis of rotation 15, the bracing cables must engage at least approximately at a common point on the upper frame.
  • connection of the traction means 3 is preferably also via universal joints, however, is sufficient for pivoting about the rotation axis 15 and a simple hinge or a simple anchoring of the traction means 3 on the subframe. 2
  • a frame in the pivoted state shows Fig. 16 ,
  • the traction means which engage on one side of the subframe, have one of the traction means, which act on the other side of the subframe, independent drive.
  • Fig. 17 shows it is not essential that the common point of attack 5 two Verspannseile 4 is arranged centrally on the lower frame between the points of attack of the traction cables 3.
  • Fig. 15 is the axis of rotation 15 defined by the two points 5 of the Verspannseile 4 not above the geometric center of gravity of the subframe 2.
  • the traction cables 3 are not arranged in the corner region of the loading platform, but each form together with the point of application 5 of two Verspannseile 4 a so-called.
  • Triple point A third pull rope is laterally spaced from the axis of rotation 15 in the region of the outside of the subframe 2. This embodiment is preferred because only one laterally spaced pull rope must be actuated for pivoting the load, which also has its own drive for this purpose.
  • the Fig. 18 and 19 show the side and front view of the device according to the invention.
  • FIGS. 20 and 21 shows FIGS. 20 and 21 in detail.
  • Fig. 13 This is also a universal joint, wherein the traction means 3 is connected to the sub-frame 2 via an axis 17 which is identical to an axis of the universal joint.
  • FIGS. 22 to 25 In order to reach the pivoted state, in this preferred embodiment, only the traction means spaced from the axis of rotation 15 must be actuated. The length of all other tension and tensioning means remains constant. As can be seen from the detailed views, the joint in the triple point is connected to the subframe such that the subframe is rotatable with respect to the joint about the axis of rotation 15. In order to perform a simple pivoting in the other direction, a fourth traction means can be provided which engages on the opposite side of the subframe.
  • the axis of rotation 15 defined by the points of application 5 of the bracing cables 4 is oriented parallel to the vehicle longitudinal axis.
  • any orientation is possible, however, especially in the vehicle end assembly pivoting only about the vehicle longitudinal axis and in the vehicle immersion pivoting transverse to the vehicle longitudinal axis of importance.
  • further tensioning and tensioning means may be provided in order to increase safety or to improve the stability. In this context, reference is made to the front part of the description.
  • the Fig. 26 shows a preferred embodiment of the invention.
  • the drive When lifting and lowering the subframe, cables of the tensioning and tensioning means are rolled up or down on motorized drums.
  • the drums for the traction means and the drums for the tensioning means are mechanically coupled with respect to the rotational movement.
  • two mechanically independent drum drives are needed for the traction means. See for example Fig. 17 for the two ropes opening in the triple points a motor 30 and for the laterally arranged rope an independent motor 30 '.
  • the preload force must be greater than the transverse forces acting on the subframe.
  • Indicated at 18 is a motor-driven drum for traction means (the motor is not shown for clarity, but its effect indicated by the circular arrow), which is rotatably connected to a threaded nut 19.
  • the threaded nut 19 during rotation of the drum 18 displaces a threaded spindle 20 prevented from rotating.
  • the threaded spindle 20, acts on the piston of a hydraulic cylinder 21 which, for energy storage, transfers its contents to a pressure-biased accumulator 22, e.g. a bladder accumulator, piston accumulator, diaphragm accumulator, spring accumulator u.
  • a pressure-biased accumulator 22 e.g. a bladder accumulator, piston accumulator, diaphragm accumulator, spring accumulator u.
  • the reservoir also contains compressible or (spring) elastic means which can also absorb or dampen shocks.
  • Fig. 27 to 29 show a possible embodiment of a drum, in the interior of the hydraulic cylinder is integrated.
  • the helical grooves for tension or tensioning cables are denoted by 25.
  • the connection device 26 is shown for a motor, the spindle nut 27, which acts on the spindle 28 and the hydraulic cylinder 29, the piston is displaced during the rotation of the drum 18 of the spindle 28.
  • the spindle nut 27 which acts on the spindle 28 and the hydraulic cylinder 29
  • the piston is displaced during the rotation of the drum 18 of the spindle 28.
  • other known to those skilled transfer mechanisms of a rotary motion in a translational movement are conceivable.
  • Fig. 17 are the drums, from which the Verspannseile 4 are unrolled, mechanically coupled in their rotational movement. Their length can therefore only ever be changed to the same extent. Therefore, in this case in Fig. 26 and 30 provided only a single cylinder. However, a plurality of mechanically coupled and therefore concurrent drums may be connected to the illustrated drum 32 (in Figs Fig. 17 indicated).
  • each driven drum or drum group could also have their own separate accumulators from the others.
  • the drives for tension and Verspannstoff are in the above embodiment still mechanically independent of each other, ie in the sense that they perform independent rotational movements, only and the energy required for the drive is provided by a single motor.
  • a pressure accumulator is not for use in a system according to Fig. 17 limited. Any conceivable arrangement, number and combination of tension cables and, if appropriate, tensioning cables can be improved by the use of a pressure accumulator with respect to their damping properties.
  • the inventive design represents a cost and energy-saving measure.
  • Another advantageous effect of this embodiment is that strong shocks, collisions u. Like. Can be collected by the hydraulic system.
  • the pressure accumulator acts as a buffer and protects the entire construction from damage.

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Abstract

L'invention concerne un dispositif de levage en particulier pour l'industrie automobile, lequel dispositif comporte un cadre supérieur (1) et un cadre inférieur (2) placé en dessous, le cadre inférieur (2) étant fixé au cadre supérieur (1) par l'intermédiaire d'au moins trois moyens de traction (3) s'étendant sensiblement verticalement et d'au moins quatre moyens de croisillonnement (4) s'étendant en biais par rapport à la verticale, le cadre inférieur pouvant être déplacé verticalement par entraînement des moyens de traction (3) et des moyens de croisillonnement (4) et deux moyens de croisillonnement (4) étant appliqués sur le cadre inférieur (2) au moins approximativement en un point commun (5). L'objectif de l'invention est de simplifier et d'augmenter le pivotement. A cet effet, les extrémités des deux moyens de croisillonnement (4) forment une articulation (14) reliée au cadre inférieur (2), laquelle articulation permet la rotation du cadre inférieur (2) par rapport aux moyens de croisillonnement (4) autour d'un axe de rotation fourni par les deux points d'application (5) des câbles de croisillonnement (4) sur le cadre inférieur (2).

Claims (13)

  1. Dispositif de levage de charges notamment destiné à l'industrie de l'automobile, comprenant un cadre supérieur (1) et un cadre inférieur (2) placé au-dessous de ce dernier, ledit cadre inférieur (2) étant retenu sur ledit cadre supérieur (1) par l'intermédiaire d'au moins trois moyens de traction (3) s'étendant pour l'essentiel verticalement, et d'au moins quatre moyens de tension (4) qui s'étendent à l'oblique par rapport à la verticale, et pouvant être déplacé verticalement par entraînement desdits moyens de traction (3) et moyens de tension (4), sachant que deux moyens de tension (4) respectifs sont en prise, au moins approximativement, en un point commun (5) situé sur le cadre inférieur (2) et sachant, en outre, que les extrémités des deux moyens de tension (4) fusionnent dans une articulation (14) reliée au cadre inférieur (2) et autorisant la rotation dudit cadre inférieur (2), vis-à-vis desdits moyens de tension (4), autour d'un axe de rotation (15) défini par les deux points d'action (5) des câbles de tension (4) sur ledit cadre inférieur (2), caractérisé par le fait qu'un moyen de traction (3) respectif vient en prise, au moins approximativement, aux deux points d'action (5) définissant l'axe de rotation (15) et forme, pour chaque point d'action, un point triple avec les deux moyens de tension (4) respectifs.
  2. Dispositif de levage de charges, selon la revendication 1, caractérisé par le fait qu'au moins un moyen vertical de traction (3) présente, en vue du basculement du cadre inférieur (2), un entraînement indépendant des autres moyens verticaux de traction.
  3. Dispositif de levage de charges, selon l'une des revendications 1 ou 2, caractérisé par le fait que le système composé du cadre supérieur (1), du cadre inférieur (2), d'un moyen de traction (3) et d'un moyen de tension (4) est cinématiquement déterminé, de préférence cinématiquement surdéterminé.
  4. Dispositif de levage de charges, selon l'une des revendications 1 à 3, caractérisé par le fait que la ligne de jonction entre les deux points d'action (5) des moyens de tension (4) passe, pour l'essentiel, par la projection verticale du centre gravité du cadre inférieur (2) dans le plan horizontal contenant lesdits points d'action.
  5. Dispositif de levage de charges, selon l'une des revendications 1 à 4, caractérisé par le fait que le profil des moyens de tension (4), projetés verticalement dans le plan horizontal du centre de gravité du cadre inférieur (2), ceinture ledit centre de gravité du cadre inférieur (2).
  6. Dispositif de levage de charges, selon l'une des revendications 1 à 5, caractérisé par la présence de quatre moyens de tension (4) s'étendant, du cadre supérieur (1) au cadre inférieur (2), pour l'essentiel le long des arêtes d'un tétraèdre de préférence régulier.
  7. Dispositif de levage de charges, selon l'une des revendications 1 à 6, caractérisé par le fait que tous les moyens de tension (4) présentent pour l'essentiel la même longueur, au moins lorsque le cadre supérieur (1) et le cadre inférieur (2) occupent des positions parallèles.
  8. Dispositif de levage de charges, selon l'une des revendications 1 à 7, caractérisé par le fait que l'entraînement d'un ou de plusieurs moyen(s) de traction (3) est couplé hydrauliquement à un accumulateur de pression (22), par l'intermédiaire d'un vérin hydraulique (21, 21').
  9. Dispositif de levage de charges, selon l'une des revendications 1 à 8, caractérisé par le fait que l'entraînement d'un ou de plusieurs moyen(s) de tension (4) est couplé hydrauliquement à un accumulateur de pression (22), par l'intermédiaire d'un vérin hydraulique (21, 21').
  10. Dispositif de levage de charges, selon l'une des revendications 1 à 8, caractérisé par le fait que l'entraînement des moyens de tension (4) s'opère hydrauliquement, sous l'action de l'énergie fournie par la pression emmagasinée dans l'accumulateur de pression (22).
  11. Dispositif de levage de charges, selon l'une des revendications 8 ou 9, caractérisé par le fait qu'un circuit de sécurité, prévu entre le vérin hydraulique (21, 21') et l'accumulateur de pression (22), ferme le conduit de pression en cas de dépassement d'un écoulement de fluide déterminé.
  12. Dispositif de levage de charges, selon l'une des revendications 9 à 11, caractérisé par le fait que l'entraînement des moyens de traction (3) et l'entraînement des moyens de tension (4) sont couplés au même accumulateur de pression (22).
  13. Dispositif de levage de charges, selon l'une des revendications 8 à 12, caractérisé par le fait que les moyens de traction (3), et les moyens de tension (4) le cas échéant, sont entraînés par un ou plusieurs tambour(s) (18, 18', 32), sachant que, par l'intermédiaire d'une broche (20), le mouvement rotatoire desdits tambours agit sur le piston d'un vérin hydraulique (21, 21', 31), et inversement.
EP05799624A 2004-11-02 2005-10-28 Dispositif de levage Not-in-force EP1819627B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0183104A AT501098A1 (de) 2004-11-02 2004-11-02 Lasthebevorrichtung
PCT/AT2005/000429 WO2006047798A1 (fr) 2004-11-02 2005-10-28 Dispositif de levage

Publications (2)

Publication Number Publication Date
EP1819627A1 EP1819627A1 (fr) 2007-08-22
EP1819627B1 true EP1819627B1 (fr) 2011-10-05

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EP05799624A Not-in-force EP1819627B1 (fr) 2004-11-02 2005-10-28 Dispositif de levage

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US (1) US20080121601A1 (fr)
EP (1) EP1819627B1 (fr)
AT (2) AT501098A1 (fr)
WO (1) WO2006047798A1 (fr)

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Also Published As

Publication number Publication date
US20080121601A1 (en) 2008-05-29
AT501098A1 (de) 2006-06-15
WO2006047798A1 (fr) 2006-05-11
EP1819627A1 (fr) 2007-08-22
ATE527203T1 (de) 2011-10-15

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