EP1948549B1 - Load-lifting apparatus - Google Patents
Load-lifting apparatus Download PDFInfo
- Publication number
- EP1948549B1 EP1948549B1 EP06804341A EP06804341A EP1948549B1 EP 1948549 B1 EP1948549 B1 EP 1948549B1 EP 06804341 A EP06804341 A EP 06804341A EP 06804341 A EP06804341 A EP 06804341A EP 1948549 B1 EP1948549 B1 EP 1948549B1
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- EP
- European Patent Office
- Prior art keywords
- load
- platform
- lifting apparatus
- bracing mechanisms
- rods
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
-
- 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 load lifting device, in particular for the automotive industry, with an upper platform and a lower platform arranged therebelow, wherein the lower platform is held on the upper platform by traction means and can be moved vertically by driving the traction means.
- 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 ropes 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 EP 0 123 846 A1 discloses a load lifting device with vertically extending hoisting ropes and the pendulum damping serving cables, each lying within a vertical plane.
- the carrying roles of the vertical hoisting ropes are each arranged on a main cat, the support rollers of the stay cables on two provided on both sides of the main cat auxiliary cats.
- the inclination of the stay cables can be changed. According to the disclosure, this is to serve, in the event that the load must be conveyed into a narrow shaft, to make the inclination of the stay cables smaller, so that their upper portions do not protrude beyond the contour defined by the hoisting ropes.
- the auxiliary crabs are moved further apart, which increased swing damping can be achieved.
- the support rollers of the stay cables fastened to the load carrier are offset along the longitudinal extent of the load carrier and arranged coaxially with each other, whereby a horizontal axis of rotation is formed with the opposite rollers.
- a pivoting of the load about the axis of rotation is not possible in this load lifting device.
- the specified ability to tilt the load in all directions is limited to minimal list and trim movements.
- the DE 3 241 380 A1 discloses a load suspension, consisting of 4 cables, which are guided so that they have inclined and vertically extending portions (in particular Fig. 4 is self-explanatory).
- the oblique sections open in pairs (V-shaped) in each case in a point of application on a relative to the load carrier block.
- the movable block can be moved with respect to the hanger in the horizontal plane in two mutually normal directions (parallel to the longitudinal extent of the load and normal thereto) and additionally pivoted in the horizontal plane.
- the movable block has two purposes to accomplish: If no pivoting or tilting of the load is desired, the relative movement of the block to the hanger serves to damp undesirably induced swinging motions.
- the movable block is connected via hydraulic cylinders to the load carrier.
- a hydraulic circuit coupled to the hydraulic cylinder provides damping when the movable block begins to move due to impacts, etc. This mechanism is intended to additionally strengthen the pendulum damping achieved by oblique bracing.
- the hydraulic cylinder or cylinders
- the block is moved relative to the load carrier. Due to the resulting imbalance, the load is pivoted accordingly.
- the US 3,653,518 A discloses a load hanger consisting of 4 ropes having substantially vertical sections and inclined sections. Starting from a common point of the subframe two ropes V-shaped apart, are deflected on the upper frame each by means of a roller in the direction of the subframe, from where it in turn deflected over a roller on a common drum on the upper frame be guided. With are called Trim actuators, which probably provide for a length compensation. The two adjacent to the sub-frame rollers are coupled together via a gear. Pivoting is not possible with this device.
- a load suspension is further known, in which at the lower platform in each case at the corners attacking, vertically extending tension cables are provided with which the lower platform is lifted.
- a stabilizing scissor-like structure connects the lower and upper platforms.
- the respective free Scherenarmende slides along provided on the upper and lower frame guides, whereby the total length of the scissor-type construction changes in the vertical direction.
- the use of such scissors-shaped devices has disadvantages, in particular because of their high weight. In this construction, occur almost exclusively in the lifting movement, as well as the interception of horizontal shear forces bending forces, therefore, all parts of the scissors design must meet the requirement of high bending stability, which is achieved for correspondingly massive dimensioning of the bending beam. A pivoting of the load about a horizontal axis is impossible due to the scissors mechanism.
- Such a scissors-like mechanisms is for example in the EP 0 963 904 A1 disclosed. All the scissors rods are in a vertical plane and all the above-mentioned disadvantages and limitations arise.
- Another known from the prior art load hanger has vertically extending tension cables and two extending between the upper and lower platform non-driven telescopes. Via a cable mechanism, the two telescopes are connected to one another in such a way that during the lifting movement a common, mutually coordinated change in length of the telescopes takes place.
- the two telescopic tubes each extend in a direction aligned parallel to the longitudinal axis of the frame vertical plane and are rotatably mounted on the upper and lower platforms each about a horizontal axis. Transverse forces acting on the lower platform cause high bending moments in the telescopic tubes and in their articulation points on the platforms. This requires the use of massive and appropriately sized bending beams and thus significantly increases the weight of the hanger.
- such a load suspension has the disadvantage that the lower frame can not be pivoted about a horizontal axis.
- Such load suspensions are for example in the EP 0265 813 A1 and the US 4,273,242 A disclosed.
- the EP 1 157 960 A1 discloses a load hanger operable by means of vertical haul ropes, which additionally comprises a hanger-stiffening structure of bars extending between the upper and lower platforms.
- This structure includes a centrally arranged, in the longitudinal direction parallel to the vertical plane lying scissors structure, wherein when lifting and lowering of the load in each case a mecanicadosverschiebung a scissor arm on the upper and lower platform.
- oscillating rod means consisting of two acute triangles, which are connected in their tips at half height between the upper and lower platform via a joint and are mutually pivotable about a horizontal axis.
- the baseline of the lower triangle coincides with the axis of rotation to the the Triangle is pivotable relative to the lower platform, while the baseline of the upper, upside down triangle coincides with the axis of rotation with respect to the upper platform.
- the scissor structure and the two oscillating rods composed of two triangles are mechanically independent of each other. Apart from the fact that the plurality of rods and mechanisms is an excessive weight load, such stabilization is inadequate for many purposes. For example, forces that urge the lower platform to oscillate about a horizontal longitudinal axis can not be trapped, because each yielding one triangle, in which they collapse, while the other triangles unfold on the opposite side.
- the lower frame can not be pivoted about a horizontal axis.
- the US 3 241 686 A discloses a load lifting device with stabilizers made of bars which are synchronized with one another by means of intermeshing teeth at their ends.
- the stabilizers run in a vertical plane, all axes of rotation lie in a horizontal plane. Even by this measure, a pendulum of the load can not be suppressed sufficiently strong, because forces normal to the vertical plane of the stabilizers cause enormous stress on the pivot points.
- the load can not be pivoted about a horizontal axis.
- EP 1 426 275 A1 discloses a single hinged solid frame hinged to the lifting platform. Due to its weight and its inflexibility in terms of maneuvering the load, this lifting device is limited to a few applications.
- the object of the present invention is to solve the problems arising from the prior art and to provide a load lifting device that is insensitive to forces, shocks, vibrations and the like in the horizontal plane as well as undesirable pivoting about the vertical axis.
- the drives required to lift and lower the load should be kept to a minimum, but without affecting the previously mentioned specification.
- the weight of the entire load lifting device must be kept as low as possible.
- a load lifting device must be pivotable about a horizontal axis to allow access to different locations of the load.
- bracing means are provided between the upper platform and the lower platform and extend at least along a section between the upper and lower platforms, each aligned obliquely to both of two mutually perpendicular vertical planes and consist of elements that can transmit both pressure and tension, and that a mechanical synchronizer is provided which tunes the vertical distance between the two ends of the individual tensioning means to each other.
- the bracing itself have no own drive, but are changed exclusively by the lifting movement of the lower platform in their length. Since no drive for the Verspannstoff is needed, the weight of a load lifting device according to the invention can be reduced and the control, which now has to be done only on the traction means are simplified. At the same time, however, the stabilization effect of the tensioning means is considerably increased by the use of elements which can transmit tension and pressure. In order to prevent during the lifting process that caused by unequal length change of individual Verspannstoff pivoting or tilting of the load, the Verspannstoff, preferably in the region of the upper platform are mechanically synchronized.
- the synchronizer ensures that the tensioning means can not change their length independently or the vertical distances between the respective two ends of the individual tensioning means can not change independently of one another.
- the synchronizer must not be confused with the usual, indirect connection between individual Verspannstoffn on the lower or upper platform or the traction cables, because this indirect connection is just unable to effect a coordinated movement of all Verspannstoff.
- the synchronization according to the invention is in fact an additional device which connects the tensioning means directly to each other and their movements coordinated and even then causes a synchronization of their lengths or the distances between their ends, if synchronizer and Verspannstoff would be considered solved from the rest of the lifting device.
- a tensioning means consists of a variable-length rod connecting the upper and lower platforms.
- a bracing means consists of two mutually articulated rod structures, which are pivotable relative to each other about a horizontal axis.
- the vertical change in length is a direct consequence of a change in the angle between the two parts.
- the tensioning means are rods whose upper ends connected to the upper platform are horizontally movable, the rods undergoing a base-point displacement when lifting or lowering the load.
- the tensioning means engage in two points of engagement on the lower platform, preferably located on the longitudinal center axis of the lower platform.
- Fig. 1 shows a load lifting device according to the invention with an upper platform 1, an underlying lower platform 2 in the form of a frame which is held by vertically extending flexurally soft traction means, traction cables 3, on the upper platform 1 and vertically movable.
- the vertical traction cables 3 engage on the lower frame 2 at each of its corners arranged support rollers 18 and are deflected to rotatably mounted on the upper platform 1, driven by a motor 17 drums 16.
- At least 3 hoisting ropes are required to hold and lift the load, but it would also be conceivable to use more than 4 hoisting ropes depending on the loads to be lifted.
- the tensioning means running obliquely to the vertical, which are also referred to below as the tensioning means, provided that are variable in length.
- Each of these four bars runs continuously between the upper and lower platforms in a substantially straight line and connects the two together.
- two tensioning means run in the same obliquely to the vertical (in the coordinate system drawn for clarity) and parallel to the x-axis plane and form a pair of pointers whose origin is in the region of the point of application of the Verspannstoff on sub-frame (Sub Pointer pair are understood in this application, two straight lines, which lie substantially in one plane and emanate at least approximately from a single point).
- the other pair of pointers extends in a symmetrically inclined plane in the opposite direction.
- the individual bars cross each other, but in reality they do not touch each other. Dashed is in Fig. 1a to recognize the retracted position of the subframe.
- variable-length rods 4 take place solely by lifting or lowering the lower platform 2 relative to the upper platform.
- the variable-length rods therefore have no own drive. At least three of these continuous rods must be present to ensure stability, but it is advantageous to use more than three rods to effectively avoid pivoting about the vertical axis (z-axis in the coordinate system).
- variable-length rods 4 consist of a threaded spindle 6, which is screwed into a provided at the end of a hollow cylinder 5 counter thread, the nut 5a, while disappearing inside the hollow cylinder.
- other variable-length rods may also be used, for example cylinder-piston units, telescoping rods, racks, all types of spindles, combinations of threads and counter-threads, more generally parts that mirror each other.
- each rod 4 acts on its own point of attack, preferably in each case at the corners of the largest possible rectangle, two bars each run in a V-shape towards a common point of application 9a or 9b on the lower frame 2.
- the common points of attack 9a and 9b are on the Longitudinal axis 15 (parallel to the ⁇ axis of the imaginary coordinate system) of the lower platform. 2
- the task of the obliquely extending to the vertical bars 4 is to stabilize the lower platform 2 with respect to the upper platform 1 and in particular in the horizontal plane forces occurring on the sub-frame 2 act to catch.
- the bars 4 are each aligned twice obliquely to the vertical, i. they arise as a line of intersection of two obliquely oriented to the vertical planes. By this measure forces can be collected from all horizontal directions as best as possible.
- variable-length rods 4 are not carried out for each individual rod independently of the others, but that they are synchronized with each other.
- the threaded spindles 6 are connected at their end facing the upper platform 1 with a synchronizing device 7.
- Fig. 2 shows such a synchronizing device 7, wherein for better clarity, the upper and lower platform and drive was omitted.
- the rotation of the spindle is - as shown in the detail drawing of Fig. 2a seen through a joint 20, such as a universal joint, converted into a rotational movement about a horizontal axis 21, whereby a plurality of one or more rotating belts 22 coupled to each other rollers 23 are set in motion.
- the bands stand with the Rolls 23 in positive engagement, for example via intermeshing ribs, which are provided in a corresponding manner on the inside of the bands and along the circumference of the rollers.
- the rotational movements of two combined by bands 22 threaded spindles 6 are synchronized with those of the attacking at the opposite end of the upper platform threaded spindles.
- Fig. 3 shows a variant of a synchronizer 7:
- the rotating threaded spindles 6 are about a provided at its upper end hinge 25, for example, a cardan, with a horizontally extending and about a horizontal axis of rotation 24 rotatable rod 26 (the storage of the rod to the upper platform not shown for reasons of clarity) connected.
- rotatable rod 26 the storage of the rod to the upper platform not shown for reasons of clarity
- Via bevel gear 27 and a torsion shaft 8 the transmission to the opposite pair of pointers takes place.
- the effect of the synchronizer is that the length of all tensioning means always changes uniformly. An irregular change in length of one or more bracing means would cause the lower platform to tilt about any pivot point and become unstable.
- Fig. 4 shows a second variant of the invention, in which the tensioning means do not extend over the entire distance between the platforms, but only over a portion.
- the four bracing means 30 are rods which, like the bracing means in the first example, are each oriented obliquely to both of two mutually perpendicular vertical planes.
- two of the bracing means 30 form a pair of pointers originating in the region of the subframe, thus each run in a V-shape towards a common point of application 9a or 9b of the subframe 2, and are combined to form a triangular planar framework 10.
- the other two bracing means are mirror images aligned and form the framework 10 '. Between the upper ends of the tensioning means 30 and the upper platform, a spatial truss 31 extends.
- the composite to a triangular framework 10 tensioning means 30, and the upper framework 31 are articulated in the area between the upper and lower platform to each other such that they against each other about a horizontal axis 32 (parallel to the x-direction) are pivotable.
- the upper framework 31 is also pivotable relative to the upper platform 1 about a horizontal axis 33 (also parallel to the x-direction).
- the system consisting of the truss 10 contained in the tensioning means 30, the upper truss 31 and upper platform (detached from the other parts of the lifting device) behaves such that pivoting of the individual parts against each other about two horizontal axes (fixed axis between the upper frame and upper framework and variable axis between upper framework and lower framework) are possible.
- the system behaves stiffly, whereby the tensioning means exerts a stabilizing function on the lower platform. If one looks at the overall system, ie together with the mirror-image parts, ie lower truss 10 'and upper truss 31' and the sub-frame, then it is also stiff compared to force components in ⁇ -direction.
- the change in length of the entire system is not carried out as in the previous example by a change in length of the individual rods, but by pivoting or folding of the two frame parts 10, 31 and 10 ', 31' against each other, thus by a change in angle.
- the tensioning means 30 are coupled to one another in the region of the upper platform 1 via a synchronizing range direction 7; in this case, the upper framework 31, 31 'merely establishes a connection between the synchronizing device and the tensioning means.
- each of the upper rod member 31 is pivoted relative to the upper platform. This rotational movement is transmitted respectively to gears 34, 34 '.
- gears 34, 34 ' By the meshing of the gears, the synchronization of the vertical distance of the two Verspannstoffenden done.
- the upper and lower frameworks 31, 10 need not necessarily be designed as frameworks. Other flat or spatial rigid structures, such as corrugated or ribbed plates, would also be possible, as long as the special arrangement does not require penetration of the parts. It is only important that the two parts 10, 31 are pivotable about an axis against each other, behave in the direction parallel to this axis as a rigid structure.
- the change in the distance between the two ends of the individual Verspannstoff done exclusively by the raising and lowering of the lower platform by means of tension cables. None of the Verspannstoff thus has its own drive.
- the points of application 9a and 9b, respectively, of the lower framework parts 30 are in the form of joints 14 which allow rotation of the subframe about a horizontal axis 15.
- the two frameworks 10 and 10 'containing the bracing means 30 penetrate each other, but do not touch each other in the area between the platforms.
- variable-length rods each extend in a plane that is aligned twice obliquely to the vertical. By this measure it is achieved that disturbances can be intercepted from both spatial directions and can lead to any vibration of the load hanger.
- Fig. 4 this is solved according to the same principle, but in a variant.
- the trusses are each constructed so that a pivoting about other than the two horizontal axes is not possible, whereby the load lifting device behaves like a rigid system with respect to all horizontally acting forces.
- Fig. 7 and 8th show a further variant of the invention.
- the bracing means 40 are again constructed of rods which are each aligned obliquely to two of two mutually perpendicular vertical planes.
- the bars extend continuously between upper and lower platform.
- Fig. 1 Run each two rods to a common point on the subframe with the formation of a horizontal axis of rotation 15.
- the upper ends of the rods keep in contrast to Fig. 1 not their position with respect to the upper platform, but are movable along the upper platform.
- the upper ends of two rods formed into a pair of pointers are connected to one another via a horizontal rod 41 to form a triangular planar framework.
- the two pointer pairs in turn act via a synchronizing device 7, which in Fig. 8 shown in detail together.
- the bracing means 40 are articulated to horizontally (in ⁇ -direction) displaceable racks 42 which are in opposite sense with a pinion 43 in engagement.
- the vertical distance between the upper and lower ends of a tensioning means ie the length resulting from a projection of the rods on the z-axis) can thus only change to the same extent with all tensioning means.
- Fig. 9 and 10 It can clearly be seen that the clamping means pass over at their lower end into a joint 14, which enable the rotation of the lower frame 2 with respect to the tensioning means about an axis 15 which is defined by the two opposing points of attack 9a, 9b on the lower frame.
- this is a universal joint.
- hinges, ball joints and the like are also conceivable.
- the individual rods of the Verspannstoff pressure sensors such as piezoelectric elements can be provided with which the train or pressurization can be determined within the bars.
- the voltage generated by the piezoelectric element can then be used as a controlled variable for an excitation voltage which is applied to a further piezoelectric element arranged in the rod in the form of a piezo pack or piezostack.
- the excitation voltage causes a change in length of the piezoelectric element and thus of the rod itself, which can be compensated from tensions resulting changes in length in the individual rods.
- the invention is not limited to the illustrated examples, so the synchronizer can take all conceivable forms, as long as a coordinated change in length of all Verspannstoff is guaranteed. Also, the formation of the bracing means is not limited to rod designs, other rigid full-surface or spatial structures are conceivable, but represent rods and frameworks due to weight considerations preferred variants.
- an arrangement of the synchronizing device in the region of the subframe is possible.
- the illustrated examples would only be upside down or reversed with the lower platform.
- the arrangement in the region of the upper platform is a preferred variant, as this makes it easier to achieve a horizontal Rotary axis of the subframe can be realized and the synchronizer itself does not have to be lifted.
- the synchronizing device could also take place in the middle in the region of the horizontal axes of rotation, for example with a similar combination of toothed racks and a pinion as in the example of FIG Fig. 7 ,
- the type and components of the synchronizer used are not essential to the invention. Thus, all possible combinations of spindles, nuts, racks, pinions, gears, hydraulic cylinders, telescopes, rotating ropes, belts, chains, etc., joints such as cardan joints, swivel joints, ball joints, etc. can be used.
- bracing means may vary, but at least three should be present in order to insure the load lifting device against all possible lateral forces.
- a variant of the invention is shown, wherein the pliable traction means 3 and the composite of rods 4 Verspannstoff are shown in a purely schematic manner.
- the tensioning means may, of course, be all variants already described.
- the upper platform is in Fig. 11 hidden.
- the common point of application 9a or 9b two Verspannstoff, in the present case two variable-length rods 4 is arranged centrally on the lower platform between the points of application of the traction means 3.
- the rotational axis 15 defined by the two points of application 9a and 9b of the tensioning means is not above the geometric center of gravity of the lower platform 2.
- traction means 3 are not arranged in the corner region of the loading platform, but each form together with the point of application 9a or 9b two Verspannstoff 4 a so-called. Triple point.
- a third traction means is laterally spaced from the axis of rotation 15 in the region of the outer side of the lower platform 2. This embodiment is preferred because only one laterally spaced traction means must be actuated for pivoting the load, which is for this purpose also has its own drive.
- the Fig. 12 the front view of the device according to the invention.
- connection of the tensioning and traction means can be done at the triple point shows Fig. 13 in detail. It is also a universal joint, wherein the traction means 3 is connected to the sub-frame 2 via an axle 44, which is identical to a. Axis of the universal joint is.
- the traction means spaced from the axis of rotation 15 must be actuated.
- the length of all other tension and tensioning means remains constant.
- 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.
- 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 9a or 9b of the clamping means is oriented parallel to the vehicle longitudinal axis. In principle, 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.
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Description
Die Erfindung bezieht sich auf eine Lasthebevorrichtung insbesondere für die Automobilindustrie, mit einer oberen Plattform und einer darunter angeordneten unteren Plattform, wobei die untere Plattform durch Zugmittel an der oberen Plattform gehalten und durch Antrieb der Zugmittel vertikal verfahrbar ist.The invention relates to a load lifting device, in particular for the automotive industry, with an upper platform and a lower platform arranged therebelow, wherein the lower platform is held on the upper platform by traction means and can be moved vertically by driving the traction means.
Eine Lasthebevorrichtung ist beispielsweise aus der
Die
Die
Die
Die
Die am Lastträger befestigten Tragrollen der Schrägseile sind entlang der Längserstreckung des Lastträgers versetzt und zueinander koaxial angeordnet, wodurch mit den gegenüberliegenden Rollen eine horizontale Drehachse gebildet ist. Da jedoch keine getrennten Antriebe für die jeweils zwei vertikal verlaufenden Hubseile vorgesehen sind (sie werden von derselben Tragrolle auf- bzw. abgewickelt), ist bei dieser Lasthebevorrichtung ein Verschwenken der Last um die Drehachse nicht möglich. Die angegebene Möglichkeit die Last in allen Richtungen zu kippen, beschränkt sich lediglich auf minimale List- und Trimmbewegungen.The support rollers of the stay cables fastened to the load carrier are offset along the longitudinal extent of the load carrier and arranged coaxially with each other, whereby a horizontal axis of rotation is formed with the opposite rollers. However, since no separate drives for each two vertically extending hoisting ropes are provided (they are from the same support roller up or unwound), a pivoting of the load about the axis of rotation is not possible in this load lifting device. The specified ability to tilt the load in all directions is limited to minimal list and trim movements.
Die
Der bewegliche Block hat zwei Aufgaben zu erfüllen: Wenn kein Verschwenken bzw. Kippen der Last gewünscht ist, dient die Relativbewegung des Blockes zum Gehänge dazu, unerwünscht induzierte Schwenk- bzw. Pendelbewegungen zu dämpfen. Zu diesem Zweck ist der bewegliche Block über Hydraulikzylinder mit dem Lastträger verbunden. Ein mit dem Hydraulikzylinder gekoppelter Hydraulikkreislauf bewirkt eine Dämpfung, wenn sich der bewegliche Block aufgrund von Stößen etc, zu bewegen beginnt. Dieser Mechanismus soll die durch schräge Verspannung erzielte Pendeldämpfung zusätzlich verstärken. Wenn jedoch ein Verschwenken der Last beabsichtigt ist, dann wird der (oder die) Hydraulikzylinder durch eine Pumpe betätigt und der Block wird relativ zum Lastträger verfahren. Durch das sich daraus ergebende Ungleichgewicht wird die Last entsprechend verschwenkt.The movable block has two purposes to accomplish: If no pivoting or tilting of the load is desired, the relative movement of the block to the hanger serves to damp undesirably induced swinging motions. For this purpose, the movable block is connected via hydraulic cylinders to the load carrier. A hydraulic circuit coupled to the hydraulic cylinder provides damping when the movable block begins to move due to impacts, etc. This mechanism is intended to additionally strengthen the pendulum damping achieved by oblique bracing. However, if pivoting of the load is intended, then the hydraulic cylinder (or cylinders) is actuated by a pump and the block is moved relative to the load carrier. Due to the resulting imbalance, the load is pivoted accordingly.
Die
Allen oben beschriebenen Lastgehängen ist gemeinsam, dass die Zug- und Verspannmittel ausschließlich auf Zug belastbar sind, nicht jedoch auf Druck.All load suspensions described above have in common that the tension and tensioning means are only loadable on train, but not on pressure.
Aus dem Stand der Technik ist weiters ein Lastgehänge bekannt, bei dem an der unteren Plattform jeweils an den Ecken angreifende, vertikal verlaufende Zugseile vorgesehen sind, mit denen die untere Plattform gehoben wird. Ein der Stabilisierung dienendes scherenartiges Gebilde verbindet die untere mit der oberen Plattform. Das jeweils freie Scherenarmende gleitet entlang von am Ober- bzw. Unterrahmen vorgesehenen Führungen, wodurch sich die Gesamtlänge der scherenartigen Konstruktion in vertikaler Richtung verändert. Die Verwendung derartiger scherenförmiger Vorrichtungen besitzt Nachteile insbesondere wegen ihres hohen Gewichtes. Bei dieser Konstruktion treten sowohl bei der Hubbewegung, als auch beim Abfangen horizontaler Querkräfte fast ausschließlich Biegekräfte auf, daher müssen sämtliche Teile der Scherenkonstruktion das Erfordernis einer hohen Biegestabilität erfüllen, was zur entsprechend massive Dimensionierung der Biegeträger erreicht wird. Ein Verschwenken der Last um eine horizontale Achse ist aufgrund des Scherenmechanismus unmöglich.From the prior art, a load suspension is further known, in which at the lower platform in each case at the corners attacking, vertically extending tension cables are provided with which the lower platform is lifted. A stabilizing scissor-like structure connects the lower and upper platforms. The respective free Scherenarmende slides along provided on the upper and lower frame guides, whereby the total length of the scissor-type construction changes in the vertical direction. The use of such scissors-shaped devices has disadvantages, in particular because of their high weight. In this construction, occur almost exclusively in the lifting movement, as well as the interception of horizontal shear forces bending forces, therefore, all parts of the scissors design must meet the requirement of high bending stability, which is achieved for correspondingly massive dimensioning of the bending beam. A pivoting of the load about a horizontal axis is impossible due to the scissors mechanism.
Ein derartiger scherenartiger Mechanismen ist beispielsweise in der
In der noch unveröffentlichten internationalen Anmeldung
Ein weiteres aus dem Stand der Technik bekanntes Lastgehänge weist vertikal verlaufende Zugseile auf und zwei sich zwischen oberer und unterer Plattform erstreckende nicht angetriebene Teleskope. Über einen Seilmechanismus sind die beiden Teleskope derart miteinander verbunden, dass bei der Hubbewegung eine gemeinsame, aufeinander abgestimmte Längenänderung der Teleskope erfolgt. Die beiden Teleskoprohre verlaufen jeweils in einer parallel zur Längsachse des Rahmens ausgerichteten Vertikalebene und sind an der oberen und unteren Plattform jeweils um eine horizontale Achse drehbar gelagert. Auf die untere Plattform wirkende Querkräfte verursachen in den Teleskoprohren und in deren Anlenkpunkten an den Plattformen hohe Biegemomente. Dies erfordert den Einsatz von massiven und entsprechend dimensionierten Biegeträgern und erhöht damit das Gewicht des Gehänges erheblich. Außerdem haftet einem derartigen Lastgehänge der Nachteil an, dass der untere Rahmen nicht um eine horizontale Achse geschwenkt werden kann.Another known from the prior art load hanger has vertically extending tension cables and two extending between the upper and lower platform non-driven telescopes. Via a cable mechanism, the two telescopes are connected to one another in such a way that during the lifting movement a common, mutually coordinated change in length of the telescopes takes place. The two telescopic tubes each extend in a direction aligned parallel to the longitudinal axis of the frame vertical plane and are rotatably mounted on the upper and lower platforms each about a horizontal axis. Transverse forces acting on the lower platform cause high bending moments in the telescopic tubes and in their articulation points on the platforms. This requires the use of massive and appropriately sized bending beams and thus significantly increases the weight of the hanger. In addition, such a load suspension has the disadvantage that the lower frame can not be pivoted about a horizontal axis.
Derartige Lastgehänge werden beispielsweise in der
Die
Die
Die vom Gebiet der Anmeldung weiter abliegende
Lasthebevorrichtungen müssen eine Menge Erfordernisse erfüllen, um einerseits effizient zu sein und andererseits den gesetzlich vorgeschriebenen Sicherheitsvorkehrungen Rechnung tragen zu können. Darüber hinaus soll die Herstellung von derartigen Lasthebevorrichtungen kostengünstig und ohne viel Aufwand verbunden sein. Folgende Eigenschaften müssen dabei erfüllt sein:
- eine hohe Stabilität des Unterrahmens samt dem darauf befestigten Gehänge für die Aufnahme von Fahrzeugkarossen, gegen darauf wirkende Kräfte, beispielsweise verursacht durch Beschleunigung bzw. Verzögerung beim Verfahren zum nächsten Arbeitsschritt, menschliche Muskelkraft, Kräfte und Vibrationen durch Werkzeuge oder andere Anlagenteile (Manipulatoren),
- eine geringe Bauhöhe im eingefahrenen Zustand bei gleichzeitig großer Hubhöhe,
- eine hohe Sicherheit gegen das Abstürzen der Last, da in den meisten Arbeitsschritten Menschen neben oder unter der Lasthebevorrichtung bzw. der von ihr gehaltenen Last arbeiten,
- ein möglichst kleines Eigengewicht bei großen bewegten Massen und dabei hoher Bauteilsteifigkeit,
- günstige Fertigungs-, Montage- und Wartungskosten der Lasthebevorrichtung,
- eine möglichst lineare Hubgeschwindigkeit, wodurch auch geringere Leistung aufweisende und daher kostengünstigere Motoren eingesetzt werden können,
- eine Hubbewegung möglichst in vertikaler Richtung,
- Zusatzvorteile für den Anwender, z.B. Möglichkeit einer Drehbewegung des unteren Aufnahmegestells um eine der beiden horizontalen Raumachsen.
- a high stability of the subframe together with the hanger fastened thereon for receiving vehicle bodies, against forces acting on them, for example caused by acceleration or deceleration in the process to the next work step, human muscle power, forces and vibrations by tools or other equipment parts (manipulators),
- a low overall height in the retracted state with simultaneous high lift height,
- a high degree of safety against the falling of the load, since in most work steps people are working next to or under the load lifting device or the load it holds,
- the smallest possible weight for large moving masses and thereby high component rigidity,
- favorable manufacturing, assembly and maintenance costs of the lifting device,
- as linear as possible a stroke speed, which can also be used lower-power and therefore cheaper engines,
- a lifting movement in the vertical direction, if possible,
- Additional benefits for the user, eg possibility of a rotary movement of the lower support frame around one of the two horizontal spatial axes.
Es besteht der Bedarf an einem Schwerlastgehänge insbesondere für die Automobilendmontage, welches durch seine geringe Bauhöhe in eingefahrenem Zustand, sein geringes Eigengewicht und seinen günstigen Preis einen Marktvorteil gegenüber bereits bekannten Hubgehängen bieten. Dieser Vorteil soll dadurch noch gesteigert werden, dass bei Bedarf ein Schwenken des Unterrahmens um eine horizontale Achse, z.B. die Längsachse eines Automobils, (mindestens bis um einen Winkel von 45°) möglich ist. Dabei ist in der Fahrzeugendmontage meistens ein Schwenken um die Fahrzeuglängsachse und in der Fahrzeuglackierung ein Schwenken quer zur Fahrzeuglängsachse von Bedeutung.There is a need for a Schwerlastgehänge especially for the final automotive assembly, which offer a market advantage over already known Hubgehängen by its low height in retracted state, its low weight and its low price. This advantage is to be further enhanced by, if necessary, pivoting the subframe about a horizontal axis, e.g. the longitudinal axis of an automobile, (at least up to an angle of 45 °) is possible. In the vehicle final assembly, pivoting about the longitudinal axis of the vehicle and pivoting across the vehicle longitudinal axis are most often important in the vehicle finish.
Zusammenfassend lässt sich festhalten, dass es im Stand der Technik zwar Hubeinrichtungen gibt, welche eine vertikale Hubbewegung bei einer Stabilisierung der Last gegen Längs-, Querkräfte und Momente um die Hochachse ermöglichen, wobei der Hubmotor bei konstanter Hubgeschwindigkeit konstante Antriebsdrehzahl besitzt. Die Stabilisierungseinrichtungen sind aber entweder Varianten von angetriebenen Scheren oder scherenartigen Gebilden oder Klapp- oder Teleskoprohren. Die Geräte aus dem Stand der Technik können Schwenkbewegungen nur durch erhöhten Aufwand z.B. seriellen Zwischenebenen ermöglichen. Alle diese Vorrichtungen tragen die Kräfte immer oder zumindest größtenteils mittels Biegeträgern ab und sind deshalb sehr schwer. Eigengewichte von 3.000 kg - 5.000 kg bei einer Nutzlast von 2.000 kg sind durchaus üblich.In summary, it can be stated that while there are lifting devices in the prior art, which allow a vertical lifting movement with a stabilization of the load against longitudinal, lateral forces and moments about the vertical axis, wherein the lifting motor has constant driving speed at a constant lifting speed. The stabilizers are either variants of driven scissors or scissors-like structures or Hinged or telescopic tubes. The devices of the prior art can allow pivotal movements only by increased effort eg serial intermediate levels. All these devices wear the forces always or at least for the most part by means of bending beams and are therefore very heavy. Dead weights of 3,000 kg - 5,000 kg with a payload of 2,000 kg are quite common.
Allen Vorrichtungen, die Seile als Verspannmittel benutzen, ist der Nachteil gemein, dass die Steifigkeit des Verspannmittels begrenzt ist. Dies deshalb, da die Durchmesser der Wickeltrommeln nicht zu groß werden dürfen, können die Zugmittel nur einen dem Trommeldurchmesser proportionalen Wert annehmen (ansonsten würden die Spannungen im Zugmittel durch den Wickelprozess zu groß werden). Des weiteren ist diesen Hubgeräten gemeinsam, dass zum Spannen des Zugmittels immer ein Antrieb (mit allen Steuerkomponenten) oder zumindest eine Energiespeichereinheit zur Verfügung stehen muss. Versionen die alle Zugmittel von einem gemeinsamen Antrieb verteilen, weisen den Nachteil auf, dass die Hubgeschwindigkeit hoch nichtlinear ist.All devices which use ropes as bracing means have the common disadvantage that the rigidity of the bracing means is limited. This is because the diameters of the winding drums may not be too large, the traction means can only accept a value proportional to the diameter of the drum (otherwise the stresses in the traction means would be too great due to the winding process). Furthermore, these lifting devices have in common that for tensioning the traction means always a drive (with all control components) or at least one energy storage unit must be available. Versions that distribute all traction means from a common drive, have the disadvantage that the lifting speed is highly non-linear.
Das Ziel der vorliegenden Erfindung besteht darin, die sich aus dem Stand der Technik ergebenden Probleme zu lösen und eine Lasthebevorrichtung anzugeben, die unempfindlich ist gegenüber Kräften, Stößen, Schwingungen und dergleichen in der horizontalen Ebene sowie unerwünschte Verschwenkungen um die Hochachse. Die für das Heben und Senken der Last erforderlichen Antriebe sollen auf ein Minimum begrenzt werden, ohne jedoch die zuvor angeführte Vorgabe zu beeinträchtigen. Des weiteren muss das Gewicht der gesamten Lasthebevorrichtung möglichst gering gehalten werden. Besonders wichtig ist die Tatsache, dass eine Lasthebevorrichtung um eine horizontale Achse verschwenkbar sein muss, um die Zugänglichkeit zu verschiedenen Stellen der Last zu ermöglichen.The object of the present invention is to solve the problems arising from the prior art and to provide a load lifting device that is insensitive to forces, shocks, vibrations and the like in the horizontal plane as well as undesirable pivoting about the vertical axis. The drives required to lift and lower the load should be kept to a minimum, but without affecting the previously mentioned specification. Furthermore, the weight of the entire load lifting device must be kept as low as possible. Of particular importance is the fact that a load lifting device must be pivotable about a horizontal axis to allow access to different locations of the load.
Erfindungsgemäß werden diese Ziele mit einer eingangs erwähnten Lasthebevorrichtung dadurch gelöst, dass zwischen der oberen Plattform und der unteren Plattform Verspannmittel vorgesehen sind, die zumindest entlang eines Abschnittes zwischen oberer und unterer Plattform verlaufen, jeweils schräg zu beiden von zwei aufeinander normal stehenden Vertikalebenen ausgerichtet sind und aus Elementen bestehen, die sowohl Druck, als auch Zug übertragen können, und dass eine mechanische Synchronisiereinrichtung vorgesehen ist, die den vertikalen Abstand zwischen den beiden Enden der einzelnen Verspannmittel aufeinander abstimmt.According to the invention, these objects are achieved with a load lifting device mentioned in the introduction in that bracing means are provided between the upper platform and the lower platform and extend at least along a section between the upper and lower platforms, each aligned obliquely to both of two mutually perpendicular vertical planes and consist of elements that can transmit both pressure and tension, and that a mechanical synchronizer is provided which tunes the vertical distance between the two ends of the individual tensioning means to each other.
Die Verspannmittel selbst weisen keinen eigenen Antrieb auf, sondern werden ausschließlich durch die Hubbewegung der unteren Plattform in ihrer Länge verändert. Da kein Antrieb für die Verspannmittel benötigt wird, kann das Gewicht einer erfindungsgemäßen Lasthebevorrichtung reduziert und die Ansteuerung, die nunmehr lediglich auf die Zugmittel zu erfolgen hat, vereinfacht werden. Gleichzeitig wird aber durch den Einsatz von Elementen, die Zug und Druck übertragen können, die Stabilisierungswirkung der Verspannmittel erheblich erhöht. Um während des Hubvorganges zu verhindern, dass infolge ungleicher Längenänderung einzelner Verspannmittel Verschwenkungen oder Verkippungen der Last verursacht werden, sind die Verspannmittel, vorzugsweise im Bereich der oberen Plattform mechanisch synchronisiert.The bracing itself have no own drive, but are changed exclusively by the lifting movement of the lower platform in their length. Since no drive for the Verspannmittel is needed, the weight of a load lifting device according to the invention can be reduced and the control, which now has to be done only on the traction means are simplified. At the same time, however, the stabilization effect of the tensioning means is considerably increased by the use of elements which can transmit tension and pressure. In order to prevent during the lifting process that caused by unequal length change of individual Verspannmittel pivoting or tilting of the load, the Verspannmittel, preferably in the region of the upper platform are mechanically synchronized.
Im Gegensatz zum Stand der Technik werden bei den erfindungsgemäßen Verspannmittel ausschließlich Zug und Druckkräfte übertragen. Die Belastung ist über den gesamten Querschnitt im wesentlichen konstant verteilt. Da keine biegestabilen Elemente wie im Stand der Technik für punktuelle Spitzenbelastungen benötigt werden, kann der Aufbau der Stabkinematik in Leichtbauweise erfolgen.In contrast to the prior art, exclusively tensile and compressive forces are transmitted in the tensioning means according to the invention. The load is distributed over the entire cross section substantially constant. Since no bending-stable elements as in the prior art for punctual peak loads are needed, the structure of the rod kinematics can be made in lightweight construction.
Die Synchronisiereinrichtung gewährleistet, dass die Verspannmittel ihre Länge nicht unabhängig voneinander ändern können bzw. sich die vertikalen Abstände zwischen den jeweils beiden Enden der einzelnen Verspannmittel nicht unabhängig voneinander ändern können. Die Synchronisiereinrichtung darf nicht mit der üblichen, mittelbaren Verbindung zwischen einzelnen Verspannmitteln über die untere oder obere Plattform bzw. die Zugseile verwechselt werden, denn diese mittelbare Verbindung ist eben nicht imstande eine aufeinander abgestimmte Bewegung aller Verspannmittel zu bewirken. Die erfindungsgemäße Synchronisierung ist tatsächlich eine zusätzliche Einrichtung, die die Verspannmittel unmittelbar miteinander verbindet und deren Bewegungen aufeinander abstimmt und die auch dann eine Synchronisation ihrer Längen bzw. der Abstände ihrer Enden bewirkt, wenn Synchronisiereinrichtung und Verspannmittel lösgelöst vom Rest der Lasthebevorrichtung betrachtet würden.The synchronizer ensures that the tensioning means can not change their length independently or the vertical distances between the respective two ends of the individual tensioning means can not change independently of one another. The synchronizer must not be confused with the usual, indirect connection between individual Verspannmitteln on the lower or upper platform or the traction cables, because this indirect connection is just unable to effect a coordinated movement of all Verspannmittel. The synchronization according to the invention is in fact an additional device which connects the tensioning means directly to each other and their movements coordinated and even then causes a synchronization of their lengths or the distances between their ends, if synchronizer and Verspannmittel would be considered solved from the rest of the lifting device.
Durch die erfindungsgemäße Maßnahme können folgende Vorteile erreicht werden:
- konstante Hubgeschwindigkeit durch konstante Antriebsdrehzahl, da lediglich die vertikalen Zugseile angetrieben werden müssen.
- bei der Verwendung längenveränderlicher Stäbe können Piezoelemente als Druckmesser zur Messung der auftretenden mechanischen Spannungen herangezogen werden. Die Messgröße selbst kann als Regelgröße zur Einstellung einer elektrischen Spannung verwendet werden, die an ein weiteres Piezoelement im Querschnitt des Stabes angelegt die aufgetretenen mechanischen Verschiebungen bestmöglich kompensiert.
- die Stabilität und die Wirkabstände der Zug-, Druckelemente ist frei wählbar und somit die Steifigkeit wie das Gewicht der Lasthebevorrichtung positiv beeinflussbar (nach dem Stand der Technik wiegt ein mechanisches Hubgehänge 4-5 t und hat eine Steifigkeit gegen Querkräfte von ca. 50 N/mm - 100 N/mm, ein vergleichbares Gehänge der erfindungsgemäßen Bauart hat bei ca. 1,2 t Eigengewicht eine Steifigkeit von 300 N/mm).
- es werden keine Antriebe, Motoren, Spanneinrichtungen und dergleichen benötigt, um die Verspannmittel betreiben zu können.
- Durch entsprechende Anbindung der Verspannmittel an der unteren Plattform kann diese ohne serielle Zusatzplattformen um eine horizontale Achse gekippt werden.
- Durch die optimale Anordnung und durch die Tatsache, dass keine zusätzlichen Motoren für die Verspannmittel benötigt werden, und das günstige Eigengewicht halbieren sich die Herstellungskosten im Vergleich zum Stand der Technik.
- Constant stroke speed due to constant input speed, as only the vertical pull ropes have to be driven.
- When variable-length rods are used, piezo elements can be used as pressure gauges for measuring the occurring mechanical stresses. The measured variable itself can be used as a controlled variable for setting an electrical voltage, which optimally compensates for the mechanical displacements that have occurred on a further piezoelectric element in the cross-section of the rod.
- the stability and the effective distances of the tension and compression elements are freely selectable and thus the stiffness as well as the weight of the load lifting device can be positively influenced (according to the state of the art, a mechanical lifting suspension weighs 4-5 t and has a stiffness against transverse forces of approx. mm - 100 N / mm, a comparable hanger of the type according to the invention has a stiffness of 300 N / mm at about 1.2 t own weight).
- There are no drives, motors, clamping devices and the like needed to operate the Verspannmittel can.
- By appropriate connection of the tensioning means on the lower platform, it can be tilted about a horizontal axis without additional serial platforms.
- Due to the optimal arrangement and the fact that no additional motors are required for the Verspannmittel, and the favorable net weight to halve the manufacturing cost compared to the prior art.
In einer bevorzugten Ausführungsform besteht ein Verspannmittel aus einem längenveränderlichen Stab, der die obere mit der unteren Plattform verbindet.In a preferred embodiment, a tensioning means consists of a variable-length rod connecting the upper and lower platforms.
In einer Variante besteht ein Verspannmittel aus zwei miteinander gelenkig verbundenen Stabwerken, die gegeneinander um eine horizontale Achse verschwenkbar sind. Die vertikale Längenänderung ist unmittelbare Folge einer Änderung des Winkels zwischen den beiden Teilen.In one variant, a bracing means consists of two mutually articulated rod structures, which are pivotable relative to each other about a horizontal axis. The vertical change in length is a direct consequence of a change in the angle between the two parts.
In einer weiteren Ausführungsform sind die Verspannmittel Stäbe, deren obere, mit der oberen Plattform verbundene Enden horizontal verfahrbar sind, wobei die Stäbe beim Heben bzw. Senken der Last eine Fußpunktverschiebung erfahren.In a further embodiment, the tensioning means are rods whose upper ends connected to the upper platform are horizontally movable, the rods undergoing a base-point displacement when lifting or lowering the load.
In einer bevorzugten Ausführungsform greifen die Verspannmittel in zwei Angriffspunkten an der unteren Plattform, vorzugsweise an der Längsmittelachse der unteren Plattform gelegen, an.In a preferred embodiment, the tensioning means engage in two points of engagement on the lower platform, preferably located on the longitudinal center axis of the lower platform.
Im folgenden wird die Erfindung anhand der Zeichnung näher erläutert. Dabei zeigt
-
Fig. 1 eine Ausführungsform der erfindungsgemäßen Lasthebevorrichtung mit längenveränderlichen Stäben, -
Fig. 1a eine Seitenansicht der Lasthebevorrichtung vonFig. 1 , -
Fig. 2 das Verspannsystem mit einer Synchronisiereinrichtung, -
Fig. 2a die Synchronisiereinrichtung im Detail, -
Fig. 3 eine Variante einer Synchronisiereinrichtung -
Fig. 4 eine Ausführungsform der erfindungsgemäßen Lasthebevorrichtung mit gegeneinander verschwenkbaren Stabwerken, -
Fig. 5 eine Seitenansicht der Lasthebevorrichtung vonFig. 4 , -
Fig. 6 eine Seitenansicht der Lasthebevorrichtung vonFig. 4 in eingefahrenem Zustand, -
Fig. 7 eine Ausführungsform der erfindungsgemäßen Lasthebevorrichtung mit Fußpunktverschiebung, -
Fig. 8 eine Seitenansicht der Lasthebevorrichtung vonFig. 7 mit der Synchronisiereinrichtung und eines Verbindungsgelenk im Detail, -
Fig. 9 eine Detailansicht eines Gelenks, -
Fig. 10 Schnitt durch ein Gelenk, und -
Fig. 11 ,12 und13 eine weitere Ausgestaltung mit der Ausbildung eines Trippelpunktes.
-
Fig. 1 An embodiment of the load lifting device according to the invention with variable-length rods, -
Fig. 1a a side view of the lifting device ofFig. 1 . -
Fig. 2 the bracing system with a synchronizer, -
Fig. 2a the synchronizer in detail, -
Fig. 3 a variant of a synchronizer -
Fig. 4 An embodiment of the load lifting device according to the invention with mutually pivotable frameworks, -
Fig. 5 a side view of the lifting device ofFig. 4 . -
Fig. 6 a side view of the lifting device ofFig. 4 in retracted state, -
Fig. 7 an embodiment of the load lifting device according to the invention with Fußpunktverschiebung, -
Fig. 8 a side view of the lifting device ofFig. 7 with the synchronizer and a connecting joint in detail, -
Fig. 9 a detailed view of a joint, -
Fig. 10 Cut through a joint, and -
Fig. 11 .12 and13 a further embodiment with the formation of a triple point.
Innerhalb des von den Zugseilen 3 definierten Quaders sind vier, schräg zur Vertikalen verlaufende Stäbe 4, die im folgenden auch als Verspannmittel bezeichnet werden, vorgesehen, die in ihrer Länge veränderlich sind. Jeder einzelne dieser vier Stäbe verläuft durchgehend zwischen oberer und unterer Plattform im wesentlichen geradlinig und verbindet die beiden miteinander. Im dargestellten Beispiel verlaufen jeweils zwei Verspannmittel in derselben schräg zur Vertikalen (im zur besseren Verständlichkeit eingezeichneten Koordinatensystem die z-Achse) und parallel zur x-Achse ausgerichteten Ebene und bilden ein Zeigerpaar, dessen Ursprung im Bereich des Angriffspunktes der Verspannmittel am Unterrahmen liegt (Unter Zeigerpaar werden in dieser Anmeldung zwei Geraden verstanden, die im wesentlichen in einer Ebene liegen und zumindest annähernd von einem einzigen Punkt ausgehen). Das andere Zeigerpaar verläuft in einer symmetrisch dazu in entgegengesetzter Richtung geneigten Ebene. In der Projektion der Verspannmittel in x-Richtung - wie aus der Ansicht von
Die Längenänderung der Stäbe 4 erfolgt allein durch Heben bzw. Senken der unteren Plattform 2 relativ zur oberen Plattform. Die längenveränderlichen Stäbe besitzen also keinen eigenen Antrieb. Zumindest drei dieser durchgehenden Stäbe müssen, um Stabilität zu gewährleisten vorhanden sein, jedoch ist es zur effizienten Vermeidung von Verschwenkungen um die Hochachse (z-Achse im Koordinatensystem) von Vorteil mehr als drei Stäbe einzusetzen.The change in length of the
In der dargestellten Ausführungsform bestehen die längenveränderlichen Stäbe 4 aus einer Gewindespindel 6, die in einem am Ende eines Hohlzylinders 5 vorgesehenen Gegengewinde, der Mutter 5a, verschraubbar ist und dabei im Inneren des Hohlzylinders verschwindet. Es können selbstverständlich auch andere längenveränderlichen Stäbe eingesetzt werden, beispielsweise Zylinder-Kolben Einheiten, teleskopierbare Stäbe, Zahnstangen, alle Arten von Spindeln, Kombinationen von Gewinden und Gegengewinden, ganz allgemein Teile, die sich spiegelbildlich zueinander verhalten.In the illustrated embodiment, the variable-
Während an der oberen Plattform jeder Stab 4 an einem eigenen Angriffspunkt, vorzugsweise jeweils an den Ecken eines größtmöglichen Rechtecks, angreift, laufen jeweils zwei Stäbe V-förmig auf einen gemeinsamen Angriffspunkt 9a bzw. 9b am Unterrahmen 2 zu. Vorzugsweise befinden sich die gemeinsamen Angriffspunkte 9a und 9b auf der Längsmittelachse 15 (parallel zur γ-Achse des gedachten Koordinatensystems) der unteren Plattform 2.While on the upper platform each
Das Heben und Senken der Last erfolgt ausschließlich durch Betätigen der Zugseile 3. Die Aufgabe der schräg zur Vertikalen verlaufenden Stäbe 4 besteht darin, die untere Plattform 2 in Bezug auf die obere Plattform 1 zu stabilisieren und insbesondere in der horizontalen Ebene auftretende Kräfte, die auf den Unterrahmen 2 wirken, aufzufangen. In der dargestellten bevorzugten Ausführungsform sind die Stäbe 4 jeweils doppelt schräg zur Vertikalen ausgerichtet, d.h. sie ergeben sich als Schnittlinie zweier schräg zur Vertikalen orientierten Ebenen. Durch diese Maßnahme können Kräfte aus allen horizontalen Richtungen bestmöglich aufgefangen werden.The task of the obliquely extending to the
An jener Stelle, an der zwei Stäbe 4 in einen gemeinsamen Angriffspunkt 9a bzw. 9b am Unterrahmen 2 münden, ist jeweils ein Gelenk 14 vorgesehen, welches eine Verschenkung des Unterrahmens 2 um die horizontale Drehachse 15 ermöglicht. Zum Zwecke des Verschwenken müssen für die Zugseile zwei voneinander unabhängige Motoren vorgesehen werden. Bei der Lasthebevorrichtung von
Ein wesentlicher Bestandteil der Erfindung besteht darin, dass die Längenänderung der längenveränderlichen Stäbe 4 nicht für jeden einzelnen Stab unabhängig von den anderen erfolgt, sondern dass sie miteinander synchronisiert sind. Zu diesem Zweck sind die Gewindespindeln 6 an ihrem der oberen Plattform 1 zugewandten Ende mit einer Synchronisiereinrichtung 7 verbunden.An essential part of the invention is that the change in length of the variable-
Die Wirkung der Synchronisiereinrichtung besteht darin, dass sich die Länge aller Verspannmittel immer gleichmäßig ändert. Unregelmäßige Längenänderung eines oder mehrerer Verspannmittel hätte nämlich zur Folge, dass die untere Plattform um irgendeinen Drehpunkt verkippt und in eine instabile Lage gerät.The effect of the synchronizer is that the length of all tensioning means always changes uniformly. An irregular change in length of one or more bracing means would cause the lower platform to tilt about any pivot point and become unstable.
Im folgenden wird der Aufbau und die Funktionsweise anhand eines in der
In der Projektion in x-Richtung ergibt sich ein zur z-Achse im wesentlichen symmetrischer Verlauf der Verspannmittel, wie aus der
Die Längenänderung der gesamten Systems erfolgt nicht wie im vorangegangenen Beispiel durch eine Längenänderung der einzelnen Stäbe, sondern durch eine Verschwenkung bzw. Einklappen der beiden Stabwerksteile 10, 31 und 10' , 31' gegeneinander, somit durch eine Winkeländerung. Die Verspannmittel 30 sind jedoch wie im ersten Ausführungsbeispiel im Bereich der oberen Plattform 1 über eine Synchronisiereichrichtung 7 miteinander gekoppelt, dabei stellt das obere Stabwerk 31, 31' lediglich eine Verbindung zwischen der Synchronisiereinrichtung und den Verspannmitteln her. Bei der Änderung des vertikalen Abstandes zwischen den beiden Enden der einzelnen Verspannmittel 30 wird jeweils der obere Stabwerksteil 31 bezüglich der oberen Plattform verschwenkt. Diese Drehbewegung wird jeweils auf Zahnräder 34, 34' übertragen. Durch das Ineinandergreifen der Zahnräder erfolgt die Synchronisierung des vertikalen Abstandes der beiden Verspannmittelenden. Denkbar wäre selbstverständlich auch eine Synchronisierung mittels Bändern, Zahnriemen, Zahnstangen etc.The change in length of the entire system is not carried out as in the previous example by a change in length of the individual rods, but by pivoting or folding of the two
Die oberen und unteren Stabwerke 31, 10 müssen nicht unbedingt als Stabwerke ausgebildet sein. Andere flächige oder räumliche starre Gebilde, wie z.B. gewellte oder gerippte Platten, wären gleichfalls denkbar, solange die spezielle Anordnung nicht ein Durchdringen der Teile erfordert. Wichtig ist lediglich, dass die beiden Teile 10, 31 um eine Achse gegeneinander verschwenkbar sind, in Richtung parallel zu dieser Achse sich als starres Gebilde verhalten.The upper and
Wie im Ausführungsbeispiel von
Die beiden, die Verspannmittel 30 enthaltenden Stabwerke 10 und 10' durchdringen einander, berühren sich aber im Bereich zwischen den Plattformen nicht.The two
Im Fall der
Die beiden Zeigerpaare wirken wiederum über eine Synchronisiereinrichtung 7, die in
Aus
In den einzelnen Stäben der Verspannmittel können auch Drucksensoren wie Piezoelemente vorgesehen sein, mit denen die Zug- bzw. Druckbeaufschlagung innerhalb der Stäben bestimmt werden kann. Die vom Piezoelement generierte Spannung kann dann als Regelgröße für eine Anregungsspannung verwendet werden, die an ein weiteres im Stab angeordnetes Piezoelement in Form eines Piezopacks bzw. Piezostacks angelegt wird. Die Anregungsspannung bewirkt eine Längenänderung des Piezoelements und damit des Stabes selbst, wodurch sich aus Spannungen ergebende Längenänderungen in den einzelnen Stäben ausgeglichen werden können.In the individual rods of the Verspannmittel pressure sensors such as piezoelectric elements can be provided with which the train or pressurization can be determined within the bars. The voltage generated by the piezoelectric element can then be used as a controlled variable for an excitation voltage which is applied to a further piezoelectric element arranged in the rod in the form of a piezo pack or piezostack. The excitation voltage causes a change in length of the piezoelectric element and thus of the rod itself, which can be compensated from tensions resulting changes in length in the individual rods.
Die Erfindung ist nicht auf die dargestellten Beispiele beschränkt, so kann die Synchronisiereinrichtung alle denkbaren Formen annehmen, solange eine aufeinander abgestimmte Längenänderung aller Verspannmittel gewährleistet ist. Auch ist die Ausbildung der Verspannmittel nicht auf Stabkonstruktionen beschränkt, andere starre vollflächige oder räumliche Gebilde sind denkbar, jedoch stellen Stäbe und Stabwerke aufgrund von Gewichtsüberlegungen bevorzugte Varianten dar.The invention is not limited to the illustrated examples, so the synchronizer can take all conceivable forms, as long as a coordinated change in length of all Verspannmittel is guaranteed. Also, the formation of the bracing means is not limited to rod designs, other rigid full-surface or spatial structures are conceivable, but represent rods and frameworks due to weight considerations preferred variants.
Prinzipiell ist auch eine Anordnung der Synchronisiereinrichtung im Bereich des Unterrahmens möglich. Die dargestellten Beispiele wären lediglich auf den Kopf zu stellen bzw. obere mit unterer Plattform zu vertauschen. Jedoch stellt die Anordnung im Bereich der oberen Plattform eine bevorzugte Variante dar, da dadurch leichter eine horizontale Drehachse des Unterrahmens realisiert werden kann und die Synchronisiereinrichtung selbst nicht gehoben werden muß.In principle, an arrangement of the synchronizing device in the region of the subframe is possible. The illustrated examples would only be upside down or reversed with the lower platform. However, the arrangement in the region of the upper platform is a preferred variant, as this makes it easier to achieve a horizontal Rotary axis of the subframe can be realized and the synchronizer itself does not have to be lifted.
Im Beispiel von
Auch die Art und die verwendeten Bauteile der Synchronisiereinrichtung sind nicht erfindungswesentlich. So können alle mögliche Kombinationen von Spindeln, Muttern, Zahnstangen, Ritzel, Zahnrädern, hydraulischen Zylindern, Teleskopen, umlaufenden Seile, Bänder, Ketten, etc., Gelenke wie Kardangelenke, Drehgelenke, Kugelgelenke usw. verwendet werden.The type and components of the synchronizer used are not essential to the invention. Thus, all possible combinations of spindles, nuts, racks, pinions, gears, hydraulic cylinders, telescopes, rotating ropes, belts, chains, etc., joints such as cardan joints, swivel joints, ball joints, etc. can be used.
Auch die Anzahl der Verspannmittel kann variieren, jedoch sollten mindestens drei davon vorhanden sein, um die Lasthebevorrichtung gegenüber allen möglichen Querkräften unempfindlich zu machen.Also, the number of bracing means may vary, but at least three should be present in order to insure the load lifting device against all possible lateral forces.
In den
Wie die Anknüpfung der Verspann- und Zugmittel am Tripelpunkt erfolgen kann zeigt
Um in den geschwenkten Zustand zu gelangen muss bei dieser bevorzugten Ausführungsform lediglich das von der Drehachse 15 beabstandete Zugmittel betätigt werden. Die Länge aller anderen Zug- und Verspannmittel bleibt konstant. Wie aus den Detailansichten hervorgeht, ist das Gelenk im Tripelpunkt derart an den Unterrahmen angebunden, dass der Unterrahmen in Bezug auf das Gelenk um die Drehachse 15 verdrehbar ist. Um auch eine einfache Verschwenkung in der anderen Richtung durchzuführen zu können, kann auch ein viertes Zugmittel vorgesehen sein, welches an der gegenüberliegenden Seite des Unterrahmens angreift.In order to reach the pivoted state, in this preferred embodiment only the traction means spaced from the axis of
Es ist nicht unbedingt notwendig, dass die durch die Angriffspunkte 9a bzw. 9b der Verspannmittel definierte Drehachse 15 parallel zur Fahrzeugslängsachse orientiert ist. Prinzipiell ist jede Orientierung möglich, jedoch ist insbesondere bei der Fahrzeugendmontage ein Schwenken einzig um die Fahrzeugslängsachse und in der Fahrzeugtauchlackierung ein Schwenken quer zur Fahrzeugslängsachse von Bedeutung.It is not absolutely necessary that the axis of
Eine ähnliche Lasthebevorrichtung, bei der zwei Trippelpunkte ausgebildet sind, ist in der noch unveröffentlichten internationalen Patentanmeldung mit der Anmeldenummer
Claims (15)
- Load-lifting apparatus, in particular for the automobile industry, having a superior platform and an inferior platform arranged thereunder, wherein the inferior platform is connected to the superior platform by a traction mechanism and can be moved vertically by operating the traction mechanism, and having bracing mechanisms provided between the superior platform and the inferior platform, comprising elements which can transfer pressure and traction, and having a mechanical synchronisation device which adjusts the vertical gap between both ends of the individual bracing mechanisms, wherein the bracing mechanisms (4, 30, 40) are each arranged at an angle to both the two vertical, normally upright planes and at least run along a section between the superior platform (1) and the inferior platform (2).
- Load-lifting apparatus according to Claim 1, characterised in that the bracing mechanisms (4, 30, 40) are rods with changeable lengths.
- Load-lifting apparatus according to Claim 2, characterised in that the rods with changeable lengths are each composed of a spindle (6) and a nut (5a).
- Load-lifting apparatus according to Claim 3, characterised in that the synchronisation device (7) adjusts the rotation caused by the changing of lengths.
- Load-lifting apparatus according to Claim 1, characterised in that the individual ends of the bracing mechanisms (40) are arranged moveably on the superior platform (1) and the synchronisation device (7) adjusts the shifting of their base point to the superior platform (1).
- Load-lifting apparatus according to one of Claims 1 to 5, characterised in that the bracing mechanisms (30) only run via a section between the superior platform (1) and the inferior platform (2) and are linked to the synchronisation device (7) via coupling devices (31).
- Load-lifting apparatus according to one of Claims 1 to 6, characterised in that at least four bracing mechanisms (4, 30, 40) are provided, wherein every two bracing mechanisms (4, 30, 40) at least come into contact approximately with the inferior platform (2) at a mutual point (9a, 9b).
- Load-lifting apparatus according to one of Claims 1 to 7, characterised in that the ends of every two bracing mechanisms (4, 30, 40) pass into a joint (14) linked to the inferior platform, which enables the inferior platform (2) to rotate around a rotational axle (15) relative to the bracing mechanisms (4, 30, 40), which is created by both contact points (9a, 9b).
- Load-lifting apparatus according to one of Claims 1 to 8, characterised in that the synchronisation device (7) comprises rollers (23) which are linked to each other by at least one rotating belt (22) which works positively in conjunction with the rollers (23).
- Load-lifting apparatus according to one of Claims 1 to 8, characterised in that the synchronisation device (7) comprises gear rods (42) which intermesh in an opposing way with a gear (43).
- Load-lifting apparatus according to one of Claims 1 to 8, characterised in that the synchronisation device (7) comprises two gear wheels (34, 34') which intermesh with each other.
- Load-lifting apparatus according to one of Claims 1 to 8, characterised in that the synchronisation device (7) comprises hydraulic cylinders.
- Load-lifting apparatus according to one of Claims 1 to 8, characterised in that two bracing mechanisms (30, 40) each make up a bar frame (10).
- Load-lifting apparatus according to Claim 2, characterised in that the rods with changeable lengths (4) each comprise a cylinder-piston unit.
- Load-lifting apparatus according to one of Claims 1 to 14, characterised in that every two bracing mechanisms (4, 30, 40) at least come into contact approximately with the inferior platform (2) at a mutual point (9a, 9b) and in that each traction mechanism (3) at least comes into contact approximately with both contact points (9a, 9b), creating a triple contact with the two bracing mechanisms (4, 30, 40) for each contact point.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/AT2005/000429 WO2006047798A1 (en) | 2004-11-02 | 2005-10-28 | Hoist device |
AT0058106A AT502741B1 (en) | 2005-10-28 | 2006-04-05 | Gravity-inertia motor structure used in ships, has looped and cross-looped chains to transfer multi-directional momentum of mass to toothed wheels fixed on drive shafts, to impart uni-directional propulsive rotation to drive shafts |
PCT/AT2006/000413 WO2007048152A1 (en) | 2005-10-28 | 2006-10-10 | Load-lifting apparatus |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1948549A1 EP1948549A1 (en) | 2008-07-30 |
EP1948549B1 true EP1948549B1 (en) | 2012-11-21 |
Family
ID=37592427
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06804341A Not-in-force EP1948549B1 (en) | 2005-10-28 | 2006-10-10 | Load-lifting apparatus |
Country Status (2)
Country | Link |
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EP (1) | EP1948549B1 (en) |
WO (1) | WO2007048152A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105600666A (en) * | 2015-12-18 | 2016-05-25 | 哈尔滨锅炉厂有限责任公司 | Manhole cover disassembly and assembly device for heat exchanger |
PL3461782T3 (en) * | 2017-09-28 | 2020-11-16 | Mohr Lizenz Verwaltungs Gmbh | Lifting device for lifting and lowering heavy objects |
DE102018101609B4 (en) | 2018-01-24 | 2020-04-16 | Eb-Invent Gmbh | Hangers, especially for an EMS (electric monorail) |
PL4091970T3 (en) * | 2021-05-21 | 2024-04-22 | Siemens Aktiengesellschaft | Device for lifting loads |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3396858A (en) * | 1965-10-23 | 1968-08-13 | Royal Industries | Load handling apparatus having retractable stabilizing arm |
DE3636459A1 (en) * | 1986-10-25 | 1988-04-28 | Tepora Transportsysteme Entwic | DEVICE FOR GUIDING A LOAD ON A CONVEYOR |
DE4219370A1 (en) * | 1992-06-13 | 1993-12-16 | Krupp Industrietech | Lifting device for loads |
DE19643347A1 (en) * | 1996-10-21 | 1998-04-23 | Andreas Zentner | Attachment device for crane for lifting and lowering objects |
-
2006
- 2006-10-10 WO PCT/AT2006/000413 patent/WO2007048152A1/en active Application Filing
- 2006-10-10 EP EP06804341A patent/EP1948549B1/en not_active Not-in-force
Also Published As
Publication number | Publication date |
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WO2007048152A1 (en) | 2007-05-03 |
EP1948549A1 (en) | 2008-07-30 |
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