CZ396799A3 - Transportation and/or positioning device, particularly for transfer of treated objects - Google Patents

Abstract

Traffic and / or positioning device (15), in particular for moving objects, contains among them drive motors (41, 46) and its output drive member (18) a lever mechanism (23) which provides a quick-acting mechanism. The linkage (23) takes over both the guide and the carrier drive means (18) which thus forms the output lever drive member the device. By converting to speed it is possible to achieve one high accelerations and delays on the carrier means (18) in which the mass inertia used is linear guides for storing levers and mass inertia significantly lower role of driven drives high positioning accuracy.

Description

Conveying and / or positioning devices, in particular for moving workpieces

Technical field

The invention relates to a conveying and / or positioning device, in particular for moving workpieces, in particular for conveying sheet metal workpieces in transfer presses.

BACKGROUND OF THE INVENTION

Processing devices with multiple processing stations arranged one after the other require the transport of the workpieces from one workstation to another. For this purpose, transfer devices are provided which pick up the workpiece, for example a sheet metal workpiece, at one processing station, move the workpiece to another processing station, where it is stored and released, while lying in a parked position away from it. processing station. Especially in large-panel presses, which process large-area parts for car bodies and, in individual cases, whole body parts, the parts are several meters wide. Correspondingly, the distance between the individual processing stations is relatively large. The sheets have a considerable weight. These components must be transported relatively quickly to allow a large number of strokes of the transfer press, ie to be accelerated and re-braked from workstation to workstation in one stroke, the shifting device having to produce the necessary driving power for the workpiece to achieve this. positioning accuracy.

In addition, shifting devices intended to transport the workpieces between the press stages are subject to relatively narrow design boundary conditions. For example, it is desirable that the space on the sides of the sliding tables of the press remain free so that the sliding tables of the transfer device can move undisturbed sideways from the transfer press.

SUMMARY OF THE INVENTION It is therefore an object of the present invention to provide a conveying and / or positioning device in such a way that it is possible to cover relatively long conveying paths in a short time and allow precise positioning of the conveyed parts (objects).

SUMMARY OF THE INVENTION

According to the invention, this object is achieved by a conveying and / or positioning device, in particular for moving workpieces, comprising a drive device comprising at least one lever device with an output driven member for driving and positioning the carrier means, the lever device comprising a pivot arm. the end forms an output driven member and is coupled to the support means, and is connected at two spaced apart locations to the receiving member and the drive, the distance between the bearing and the drive location being less than the distance between the output driven member, and place of storage.

Thus, the conveying and / or positioning device comprises a pivot arm with a pivot arm which carries at one end a carrier means which can be engaged with the workpiece or otherwise take over it. The pivot arm lies in a force transmission path arranged from the drive source to the support means. The swing arm takes over • ·· 0 0 · ·· 0 0 • • 0 0 0 0 0 0 0 ·· ·

000 00 0 0 0 0 0 • 0 0 0 0 0 0 0 ·· 00 0 0 0 000 0000

-3 Conversion to fast. It is guided or driven at two locations spaced from the carrier means, the distance between the two locations being less than the distance of the carrier means from the pivot axis of the lever. This results in a lever transmission. This results in the carrier means performing a faster and more extensive movement than the drive means engaging the pivot arm. They can be associated with guides, for example linear guides, slide runners and the like. Since these elements achieve a lower maximum speed and move along shorter paths than the carrier means, their weight does not play as important a role for the drive dynamics as the weight of the carrier means. They can be sized to provide accurate guidance. As a result, a high positioning accuracy can be achieved on the support means. Lever gear on the swivel arm makes it possible to quickly travel a long conveyor path with good accuracy.

According to a preferred embodiment, two drive devices are arranged in a mirror-symmetrically symmetrical manner, the pivoting arms of which are connected to one another by a transverse beam which forms the carrier means. The transverse beam may be provided with suction cups or other means to temporarily support the workpieces. The transverse beam is preferably guided by the two swinging arms along a loop path forming a displacement curve which is arranged, for example, in a vertical plane. This creates a biaxial displacement function in which the cross beam is moved vertically and horizontally. In this case, the path of the displacement curve is not fixed in advance, but is preferably selectable or adjustable by correspondingly controlling the drives belonging to the drive train. This control may advantageously consist of a prog-

-4ramable control. In addition, if the drive means acting at both ends of the crossbeam are differently actuated, the crossbeam may also perform pivotal movements about a vertical axis or along an axis longitudinally with respect to the conveying direction.

In this case, the support means, i.e. the transverse beam, can be provided with a device intended to hold the displacement curve unrotated or to pivot it in a controlled manner. This is possible both by separate drives, supported by the swinging arms, and by means of force transmission, such as a parallelogram rod assembly or a drive system with rods, otherwise arranged drives.

The pivot arm is pivotable about an axis of rotation that is not stationary but is adjustable along a predetermined path. For example, the pivot axis can be adjusted by means of a suitable bearing on the slide which is supported on the guide. The sliding guide may be oriented vertically and, if necessary, horizontally or otherwise, and may be straight or curved. Alternatively, the bearing member adjusting the pivot arm of the pivot arm can also be guided differently, for example, via a rocker, a parallelogram, etc.

In a preferred embodiment, the pivot arm is vertically oriented in the central position and is pivoted for carrying out the conveying step on both sides. In the middle position, which can be considered a parking position, the sides of the sliding tables of the adjacent processing stations are free and thus also accessible. This is useful when changing tools. In addition, the drive train can be mounted above the tables. Space below and between

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Β Β Β · · · · · tak tak tak tak tak tak tak tak tak tak tak tak tak tak tak tak tak tak tak tak tak tak tak tak tak tak tak tak for waste manholes and scrap conveyors.

The drive train can be mounted on the press stands, which allows an extremely large footprint and space-saving design and eliminates the problems of the separation point between the press stands and the tables.

The linkage, to which the pivot arm belongs, can be designed differently. For example, it may comprise a rocker lever, articulated to the pivot arm, which is connected to the drive drive. If, for example, the drive drive is held on a sliding runner which itself is connected to a fixed drive device, the carrier means can be moved along the desired curve by means of controlled control of the sliding runner drive and the drive drive. In a preferred embodiment, the slider is mounted in a vertical guide. The rocker lever is connected to the pivot arm approximately in the middle, the end of the pivot arm facing away from the support means itself being rotatably supported on a slide carrier whose linear guide extends parallel to the above guide. In this embodiment, particularly clear operating and driving conditions arise when the length of the rocker lever corresponds to half the length of the rocker arm, determined by the distance of the axis of the support means from the pivot axis of the rocker arm, the rocker lever engaging in the center of the rocker arm. In this case, the control of the drive of the sliding carrier exclusively causes the height adjustment of the carrier means and the control of the swivel drive exclusively causes the linear adjustment of the carrier means in the transport direction.

Alternatively, the pivot arm may be driven by two

The reciprocating pivoting levers are arranged so as to be at an acute angle to one another and are fixed to the pivoting arm by means of a joint which defines a common articulation axis for the two pivoting levers. The rocker levers are preferably suspended at the other end on sliding runners of a linear guide which are provided with linear drives. The guides may be vertical on the press stands and define the vertical direction of the guides. This results in a densified constructional form in which the conveying movement of the support means is achieved without the need for the means for transmitting forces in the conveying direction. The linear strokes to be performed by the sliding runners are relatively short relative to the fast-moving transmission by the pivot arm, resulting in a compact, space-saving design.

The pivot levers and / or the swing arms can be configured as length-adjustable if necessary. As a result, additional degrees of freedom can be created in guiding the carrier means.

Preferably, the drive means is coupled to a force generating device which extends through the lever mechanism of the drive means a compensating force to the support means which at least approximately compensates for the gravity of the support means and the associated linkage. The force generating device can engage the sliding runner of the rotary-actuated lever. In addition, the swivel drive can be force compensated. For this purpose, it is possible to exert a more or less constant force on the rocking lever at a point between its axis of rotation and its articulated axis, which is oriented substantially vertically upwards or when acting on

9 · 99 · 99

9 9 9 9 · · · · ·

9 9 9 9 · · · · · 9

99 9 9999

-7the other side of the axis of rotation down. This can be achieved by means of pneumatic cylinders.

In an embodiment with two acute angle pivoting levers for actuating the pivoting arm, the gravity compensation can be performed via a third pivoting lever which acts on the pivoting arm with a substantially identical articulated axis and leads to a further vertical slider. The latter is connected via a rod assembly to a force generator, for example a pneumatic cylinder, which imposes a substantially constant and vertically upwardly directed force on the slider.

Further details of preferred embodiments will be apparent from the dependent claims, the drawings, and the following description.

BRIEF DESCRIPTION OF THE DRAWINGS

BRIEF DESCRIPTION OF THE DRAWINGS The invention is explained in more detail below with reference to the accompanying drawings, in which: FIG. 1 is a perspective partial view of a plurality of successive workstations of a progressive molding line interconnected by transfer units; FIG. Fig. 3 is a diagram of the kinematics of the transfer unit of Fig. 2; Fig. 4 is a perspective diagram of a modified embodiment of a transfer unit connecting two workstations; 4, 6 shows the kinematics diagram of the transfer unit according to the principle shown in FIG. 2, with the rotary drive of FIG. 2, FIG.

and a diagram of the kinematics of the modified transfer unit.

DETAILED DESCRIPTION OF THE INVENTION

FIG. 1 shows a transfer press 1 at their work stations 2, 3, 4, 5, 6 for processing the workpieces. Each workstation 2-6 includes a corresponding sliding table 7, 8, 9, 10, 11 for receiving a tool (not shown). On both sides of the row, formed by the sliding tables 7, 8, 9, 10, 11, there are press stands 12, 14 mounted at the level of the spacing between the sliding tables 7, 8, 9, 10, 11.

In order to allow the workpieces to be conveyed from one workstation to another, there are shifting units 15, which are identical to one another and are therefore provided with each other between two successive workstations as well as at the beginning and at the end of the row formed from the workstations 7-11. with the same reference numerals. The transfer unit 15, which is disposed between the work stations 2 and 3 and thus between the sliding tables 7, 8, is shown separately in FIG. 2 and is further described as representative for all further transfer units 15 of the transfer press line 1.

The transfer unit 15 comprises two drive devices 16, 17 which are arranged mirror-symmetrically with respect to each other relative to the vertical plane and which hold a transverse beam 18 therebetween serving as a support means for the workpieces. For picking up or gripping and holding workpieces, for example large sheet metal parts, if the transfer press 1 is a body press,

-9 • 99 99 9 99 ·· · 9 9 · 9 9 9 · · · 99 · 9 9 9 999

999 99 9 · · ·

9,999,999

Suction cups 19, 20, each containing a plurality of suction cups 21 spaced apart from one another, are mounted on the crossbeams 18, 999 99 99 99 9 9 9 99. As a result of the mirror symmetry between the drives 16, 17, the description of the drive 16 applies accordingly to the drive 17, with the same reference numerals being used for reference.

The drive means 16 includes a lever arm 23 with a pivot arm 24, which at the end comprises a support 25 for the crossbeam 18. The support 25 forms an output drive member of the lever 23 and the crossbeam 18 is rotatably supported thereon about an axis arranged transversely to the direction traffic, the so-called axis of rotation.

The pivot arm 24 is supported by a slide 27 defining the pivot axis 28 on the slider 29. The pivot axis K and the pivot axis K formed by the center axis of the guide 25 or the crossbeam 18 define the length of the pivot arm 24 referred to in FIG. L. The slider 29 may be replaced by a powered or passive lever guide, which instead of a linear guide is an arched guide.

The slider 29 is mounted vertically adjustable on a linear guide 31. The slider 29 runs freely, i.e. it is not connected to any drive and is freely movable in the vertical direction. The pivot arm 24 is freely pivotable on the slider 29. Thus, there are no drive mechanisms at or below the height of the sliding tables 7, 8. If necessary, a swivel motor can be used to swivel the crossbeam.

The swing arm 24 is driven via the rocker lever.

9 9 9

9 99

The rocker lever 32 is pivotally connected to the rocker arm at the hinge 33, whose axis 34 lies midway between the pivot axis K and the pivot axis 28.

At its other end, remote from the pivot arm 24, the rocker 32 is connected to a short cantilevered shaft 36, which is the output member of the pivoting drive 38 mounted on a linearly sliding slider 37. The slider 37 is guided in a vertical direction by a guide 39. The sliding runner 39 is supported parallel to the slider guide 31 and is mounted on the stand 12 or 14 as the latter. The swivel drive 38, supported by the slider 37, consists of an adjusting motor 41 and a low speed transmission whose output is a short cantilevered shaft 36 .

The slider 37 is connected to a stroke drive 45, which includes an adjusting motor 46 and a spindle lifting gear 47 shown below. Both motors 41, 46 are subject to control by a central control device.

For balancing the weight 18 acting on the crossbeam 18 as well as the weight of the lever assembly consisting of the pivot arm 24 and the rocking lever 32, a force generating device is used, for example comprising two pneumatic cylinders 51, 52 having internal pressure either is substantially constant and / or is optionally controlled from the control device. Pneumatic cylinders 51, 52 are connected via sliders 53, 54 to slider 37.

The transfer unit 15 described above operates with reference to the schematic representation of FIG. 3. The control unit causes the adjusting motors 41, 46 to raise or lower the slider 37 and to rotate the rocker 32 such that the hinge axis 34 passes along the displacement curve θ. The hinge 33 forms the drive for the swing arm 24. Its lower end is supported by the slider 29, which thus forms the bearing for the swing arm 24. The lever transmission from the drive at the hinge 33 to the bearing 25 results on the bearing 25 and hence on the carrier 18, the desired curve-shaped shift curve K. The shift curve K has a length in the shift direction X that is twice as long as the length of the curve křivθ in the shift direction. In terms of height, the two curves essentially match.

The swivel arm 24 thus provides a gear to rapid, i.e., the carrier means 18 moves considerably faster and is more rapidly accelerated and braked more heavily than the hinge 22. The inertia masses of these elements therefore influence the acceleration and braking of the carrier means 18 with reduced values. In this way, good drive dynamics can be achieved, and the above drive means 16 also permits good positioning accuracy. At the ratios shown in Fig. 3 (L = 2 x 1), the vertical direction and the transport direction X are disconnected from each other, ie the movement of the motor 41 is converted solely to the movement in the X direction and the movement of the motor 46 is driven exclusively into the net direction. direction Y.

In the rest position and at the beginning of the working cycle of the transfer unit 15, the rocker arm 24 is pivoted by the rocker lever 32 to a vertical position. The axis of rotation K is located in the first

-12 * 9 9 9 9 9 9 9 9 9 9 9 9 9 9 99 99 9 9

9 9 9 9 9

9 99 99 999 99 99 point A of the shift curve K. While the tool opens in processing stage 2 upstream in the conveying direction X, the pivoting drive 38 is actuated, the motor 41 being actuated such that the rocker lever 32 in FIG. rotates to the left, ie against the X direction of traffic. At the same time, the slider 37 performs a lifting and lowering movement by actuating the motor 46, so that the carrier 18 with its rotational axis K undergoes a movement along the curve section AB at the end of the travel point A and reaches the picking point B at its end.

Here, the workpiece is taken over by operating the suction cups 21 and the motor 46 for lifting the workpiece is first actuated. Once the stroke has begun, the motor 41 is actuated against its original direction, as a result of which the support means 18 is strongly accelerated in the transport direction X and passes along the curve section BC to the storage point C. Shortly before reaching the storage point C the swivel drive 38 inhibits the forward movement. When the workpiece at the point C of the path is stored in the tool of the next processing stage, the swivel drive 38 and the lift drive 45 are actuated such that the carrier means 18 returns along the path curve CA to the starting point A. grade 2, 3. ·

By way of derogation from the embodiment described above, the rocker lever 32 can also be mounted on a stationary pivoting actuator. The height adjustment is achieved, for example, by the telescopic drive of the rocker lever 32, which is then adjustable in length. Alternatively, both the slider 37 and the hinged version can be swingable.

• * »44

4 4 4 4 4

4 4 4 4

445 44 4

4 4 4

444 44 44 The pivoting actuator is mounted on the hinge 33 on the stationary pivot axis. However, the pivoting arm is then subjected to greater movements and accelerations.

If necessary, the swivel drive can also be mounted on the slider 29 and act directly on the swing arm 24. This applies both when the rocker 32 is non-adjustable in length and is mounted on the slider 37 and when the rocker 32 is formed as a telescope and its articulation point is defined by a pivot axis fixed in space. Irrespective of how the swivel drive of the swivel arm 24 is shown in detail, the swivel arm 24 can also be designed as a telescope,

The telescopically extendable location may lie both above and below the hinge 33 and may be provided with a telescopic drive. Here, the lower slider 29 can be omitted. This construction can lead to a reduced construction height, which can also bring advantages.

Another modified embodiment of the drive train 16 is based on the kinematics shown in FIG. Instead of the pivoting drive 38 carried by the slider 37, the rocker 32 is provided with a lever arm 61 which is rigidly connected thereto and which is connected to the slider 63 via a connecting rod 62. This is guided in a linear guide, which is preferably arranged parallel to the linear guide of the slider 37. The slider drive 63 causes the pivoting lever 32 to pivot unless the lever is actuated synchronously with the slider 37 drive.

FIG. 8 shows an embodiment of a drive train 16; FIG.

Wherein the length ratios between the pivot arm 24 and the rocker 32 are different than the ratios previously described. The length L of the swing arm 24 exceeds the length 1 (small 1) of the swing arm 32 by more than twice. This implies a larger transfer. The lines and drives can be designed and arranged according to all the variants and embodiments described above. In addition, in all embodiments, it is possible to arrange the drive device 16 as being essentially hinged, i.e. head-down in FIG. This can be of significance when all drives and guides are to be mounted as far as possible above the sliding tables 7, 8. In the case of suspension, the sliding runner drives independently of the runner 37 being driven and the sliding runner 29 freely late is the sliding runner 29 driven. sliding runner freely movable, mounted above the lever mechanism. In addition, sliding runners 37, 29 can be dispensed with if the pivot arm 24 is a telescope and the distance between the hinge axis 34 and the pivot axis 28 is variable.

the bearings can be sliding or not

A further embodiment of the conveying and positioning unit 16 is shown in FIGS. 4 and 5. The design and mounting of the pivot arm 24 and the crossbeam 18 carried by it is identical to that of FIG. The displacement unit 15 of FIG. 4 differs from the above by positioning the pivot axis 34 in space. For this purpose, two rocker levers 32a, 32b, which are connected in a joint 33 to the pivot arm 24. Both rocker levers 32a, 32b comprise the same pivot axis 34.

The rocker levers 32a, 32b are disposed at an acute angle from the pivot arm 24 toward the slider 37a, 37b, which are supported on, for example, parallel linear guides 12 (14). On sliders ··· · • ·

-1537a, 37b, for example, the pivoting levers 32a, 32b, which are of the same length relative to one another, are freely pivotable. The sliders 37a, 37b are connected to the corresponding stroke drives 45a, 45b. These include displacement motors 46a, 46b which act via linear gears, for example spindle stroke gears 47a, 47b, to the corresponding slider 37a, 37b.

A third rocker lever 32c, which is also attached at or near the articulated joint 33, leads to a third slider 37c which, for example, is subjected to a substantially constant vertical upward force and is supported on a vertical guide. A pneumatic cylinder 51, equipped as a force generator, is coupled to the sliding slide 37c via a tension rod 53 for exerting force.

In the transfer unit 15 is located in the axis of the joint 34 formed along the transfer motion curve K _Q interaction of the stroke movement of the slider 37a, 37b. As in the embodiments described above, the pivot arm 24 converts the movement of the hinge axis 34 into a displacement curve K.

In all the described embodiments, it is possible both to guide the crossbeam without tilting, and to provide the possibility of pivoting or tilting it in a controlled manner. 7 shows a kinematics in which a parallelogram guide extends from the slider 37 to the crossbeam 18. A pivoting lever 32 'is mounted parallel to the rocker 32 and is pivotally mounted on the slider 37. A short guide lever 71 is articulated on the rocker arm 24 pivotably about the pivot axis 34, which is arranged parallel to an imaginary connection of opposing pivot axes. of the rocking levers 32, 32 '. Swivel lever 32 ', the length of which is

16 coincides with the length of the rocker 32, is pivotally connected to the guide lever 71 at its axis 72. The rocker 32, 32 'forms a parallelogram. This also applies to the pivot arm 24 extending from the hinge axis 34 to the tilting axis K, and to the further pivot lever 23 ', which extends from the guide lever 71 to the lever 73 connected to the crossbeam 18. The lever 73 is exactly the same length , as a guide lever 71.

In this embodiment, the firing position of the crossbeam 78 is determined by arranging a lever 73 that corresponds to the orientation of the link between the upper end of the rocker levers 32, 32 'in each pivoting position. The corresponding adjusting drive can be performed by the slider 37. In addition, it is possible to provide a rocker lever 32 'and / or a rocker lever 24' adjustable in length.

The conveying and positioning device 15, in particular for moving the workpieces, comprises, between their drive motors 41, 46 and its drive-driven output member 18, a lever device 23 which performs a gear-to-fast operation. The lever assembly 23 takes over both the guide and the drive means of the carrier 18, which thus forms the output member of the lever assembly. By converting to fast, high accelerations and delays can be achieved on the support means 18, in which the mass inertia of the linear guides used in the bearing arrangement plays a role, and the mass inertia of the drives moving together play a distinctly reduced role. In addition, high positioning accuracy can be achieved.

Claims (22)

PATENT CLAIMS A conveying and / or positioning device (15), in particular for moving workpieces, comprising a drive device (16) comprising at least one lever device (23) with an output driven member (25) for driving and positioning the carrier means (18) wherein the lever assembly (23) comprises a pivot arm (24), one end of which forms an output driven member (25) and is connected to the support means (18), and is connected at two connection points (28, 34) lying in a distance between the bearing member (27) and the drive (32, 33), the distance between the bearing location (28) and the drive location (34) being less than the distance between the output driven member (25) and the bearing location (28) . Device according to claim 1, characterized in that the pivot arm (24) is guided so that the output driven member (25) extends along a loop path (K) which is longer than the path along which the location (28) is guided. ) a bearing or drive location (34). Device according to claim 2, characterized in that the track (K) is arranged in a vertical plane. A device according to claim 1, the arm (24) being in the bearing member of the horizontal axis (28). 1, characterized in that the pivoting (27) is pivoted about Apparatus according to claim 1, the pivot arm (24) preferably of a linear path. 1, characterized in that the bearing is guided in a predetermined manner; 9 -186. Device according to claim 1, characterized in that the connection point where the drive (32) of the pivot arm (24) is connected to the pivot arm (24) lies between the bearing member (27) and the output driven member (25). Device according to claim 1, characterized in that the drive (32) is designed and guided so that the spatial position of the connection point (34) of the drive (32) to the pivot arm (24) is determined by the drive (32). Device according to claim 1, characterized in that the actuator (32) comprises at least one rocker lever (32) via which the pivot arm (24) is connected to a guide device (37), preferably a linear guide device. Device according to claim 8, characterized in that the guide device (37) is connected to the drive unit (45). Apparatus according to claim 8, characterized in that the guide device (37) is a slider guide on which the slider (37) of the rocker levers (32) is pivotably mounted. Apparatus according to claim 10, characterized in that the rocker (32) is connected to a pivoting actuator (38) by which it is possible to adjust the pivot lever (32). Device according to claim 11, characterized in that the swivel drive (38) is carried by the slider (37). 13. cutting drive Apparatus according to claim 11, characterized in that (38) lies outside (63) of the slider (37). that natá-19- Device according to claim 1, characterized in that the connection point (34) between the rocker (32) and the pivot arm (24) is arranged centrally between the bearing member (27) and the output driven member (25). Apparatus according to claim 13, characterized in that the swivel drive is connected to the rocker (32) at a location (62a) spaced from the pivot axis of the rocker (32), the swivel drive preferably comprising a guide device (63) whose guide direction is arranged parallel to the guide device (37) of the rocker lever (32), and wherein the rocker lever (32) is preferably formed as a two-arm lever, one end of which guides the rocker arm (24) and the other end of which is a rotary drive (62, 63). Apparatus according to claim. 1, characterized in that the actuator has at least two rocker levers (32a, 32b) through which the rocker arm (24) is connected to guide means, preferably with linear guide means, the two rocker levers (32a, 32b) being mutually mutual they form an acute angle and are pivotally connected to the pivot arm (24) about a common pivot axis (34) at the point of attachment. Apparatus according to claim 16, characterized in that the two guide devices are connected to a corresponding drive unit (45a, 45b), the guide device being formed by sliding runner guides, the corresponding sliding runners (37a, 37b) being freely rotatably mounted to be pivoted levers (32a, 32b). Device according to claim 17, characterized in that it guides the water. The measuring devices are parallel to each other. Device according to claim 1 or 8, characterized in that the rocker arm (24) and / or the rocker lever (32) is telescopically designed and provided with a telescopic drive. Device according to claim 1, characterized in that the pivot arm (24) is provided with a device (24 ', 32', 71, 73) for tilting the carrier means (18). Apparatus according to claim 1, characterized in that the pivot arm (24) comprises a stationary pulley connected by a toothed belt to a pulley of the same size fixedly connected to the support means (18) and preventing the support means from tilting about a horizontal axis transversely to direction of transport. Device according to claim 21, characterized in that the pulley is mounted on the pivot arm (24) at the connection point (28). Device according to claim 21 or 22, characterized in that the pulley on the pivot arm (24) is no longer firmly connected to the pivot arm (24), but is driven by a motor for controlled tilting of the carrier means.