Drive device for output movement of a displacement element and a device for producing thread and profiles on blanks with said drive device

Abstract

The invention relates to a drive device (10) for an output movement of a displacement element, comprising a connecting rod (12) which is connected to the displacement element. The drive device (10) comprises a crank (22) and an eccentric unit (26). The eccentric unit (26) has a mechanical setting device (36), comprising a setting element (38) which acts on an eccentric element (40), wherein the setting element (36) is designed such that the setting element (38) can adopt different setting positions relative to the crank rotational axis, specifically position and / or orientation, wherein the setting element (38) can be locked in said setting position, and wherein an orbit of the eye-type bearing axis (ALA) about the crank rotational axis (KDA) is allocated to a setting position.

Description

[0001] DRIVE DEVICE FOR THE OUTPUT MOVEMENT OF A PROCESS ELEMENT AND A DEVICE FOR PRODUCING THREADS AND PROFILES ON BLANKS USING THIS DRIVE DEVICE

[0002] The invention relates to a drive device for the output movement of a travel element according to the type specified in the preamble of patent claim 1.

[0003] Drive devices for the output movement of a moving element are well known in the art. They are integrated, for example, in thread rolling machines to generate a linear back-and-forth movement of a movable rolling die relative to a parallel, stationary rolling die when producing a thread and / or profile on a blank located between two rolling dies. The rolled profile on one blank must precisely merge into the profile of the other rolling die after half a revolution. This makes it necessary to coordinate the respective longitudinal movement of the rolling dies. To produce reproducible, high-quality threads, the rolling dies must operate with high accuracy and be precisely aligned with one another.

[0004] For example, DE 2 413 035 A, US 3 308 642 A, and US 3 117 473 A each describe a drive device for a thread rolling machine that can move a moving element, e.g., a rolling die, back and forth. The drive device comprises a connecting rod connected to the moving element at one end and having a connecting rod eye at the other end, in which an eye bearing is arranged, which is connected to an eccentric device via an eye bearing axis. The eccentric device is connected to a rotatable crank of the drive device via an eccentric device bearing. The eccentricity of the eye bearing axis relative to the crank rotation axis is adjustable.

[0005] The adjustment of the travel element in the longitudinal direction, in particular the stroke position of a movable rolling die, which results from the starting position and the maximum stroke position, depends on the product parameters of the screw to be manufactured or the manufacturing tolerance of a pair of rolling dies. Such adjustment can only be achieved with great effort using the current state of the art.

[0006] The invention is based on the object of proposing a drive device for the output movement of a travel element, in which the stroke position of the travel element can be adjusted continuously and precisely with high reproducibility in a simple manner. In particular, the adjustment should be automatable.

[0007] This problem is solved by the characterizing features of patent claim 1 in conjunction with its preamble features.

[0008] The subclaims form advantageous further training.

[0009] In a known manner, a drive device that executes an output movement of a displacement element comprises a connecting rod having a connecting rod eye at a first end and a guide element at a second end that is connected to the movable displacement element. The displacement element can be, for example, a tool, a linkage of the tool, or the like.

[0010] The guide element is mounted in such a way that it essentially performs a translational movement in a guide direction. The guide element is preferably mounted so that it can rotate and / or pivot about a guide element axis.

[0011] The drive device comprises a crank, which is designed, for example, as a crank arm or a crank wheel and is mounted for rotation about a crank axis. The crank can, in particular, be mounted on a housing. The crank is a driven element of the drive device and can have drive structures, e.g., external teeth, via which it is driven. This allows the crank to cover a crank angle.

[0012] The drive device further comprises an eccentric device having an eye bearing and an eccentric device bearing. The eccentric device is connected to the connecting rod eye via the eye bearing, which has an eye bearing axis, in such a way that the connecting rod eye can rotate about the eye bearing axis. The eccentric device is connected to the crank via the eccentric device bearing. The eccentric device bearing defines an eccentric device bearing rotation axis that is arranged at a fixed distance from the crank rotation axis. As the crank rotates, a connecting line between the crank rotation axis and the eccentric device bearing rotation axis rotates about the crank rotation axis. The distance of the eccentric device bearing rotation axis from the crank rotation axis is greater than the distance of the eye bearing axis from the eccentric device bearing rotation axis. The eye bearing axis is eccentric to the crank rotation axis.

[0013] The guide element is assigned a first guide element position, in which the crank rotation axis, the eccentric bearing rotation axis, and the guide element axis lie in one plane. The first guide element position corresponds to a first crank position of the crank. The first guide element position or first crank position refers, for example, to a front dead center, at which the guide element axis exhibits the maximum deflection relative to the crank rotation axis. A second guide element position is assigned, for example, to a rear dead center, at which the guide element axis exhibits the smallest deflection relative to the crank rotation axis.

[0014] The eccentric device is designed such that, relative to one revolution of the crank, i.e., a crank angle of 360° starting from the first crank position, an orbit of the eye bearing axis around the crank rotation axis results. Depending on the orbit, the distance between the eye bearing axis and the crank rotation axis changes within one revolution of the crank. The eccentric device is designed such that the eccentricity of the eye bearing axis relative to the crank rotation axis is adjustable.

[0015] According to the invention, the eccentric device has a mechanical adjustment device which has an adjustment element which acts on an eccentric element, wherein the adjustment device is designed such that different adjustment positions relative to the crank rotation axis, namely position and / or orientation, can be assumed by the adjustment element and the adjustment element can be locked in this adjustment position, wherein a respective orbit of the eye bearing axis around the crank rotation axis is assigned to a adjustment position.

[0016] To adjust the eccentricity of the eye bearing axis relative to the crank rotation axis, the eccentric device has a mechanical adjustment mechanism. The mechanical adjustment mechanism can achieve the adjustment of the eccentricity of the eye bearing axis relative to the crank rotation axis by means of mechanical components, bodies, or parts that interact with forces. The adjustment mechanism comprises the adjustment element, which acts mechanically on the eccentric element to thereby effect a mechanically generated movement of the eye bearing axis relative to the crank rotation axis.

[0017] The adjustment element can assume different adjustment positions relative to the crank axis of rotation. The adjustment position is the position and / or orientation of the adjustment element relative to the crank axis of rotation. The position can be a distance, in particular a radial distance, of the adjustment element relative to the crank axis of rotation. The orientation can be an angular rotation of the adjustment element about the crank axis of rotation.

[0018] A respective setting position of the setting element is assigned an orbit of the eye bearing axis around the crank rotation axis. By changing the setting position, the alignment of the eye bearing axis relative to the eccentric device bearing axis of rotation, based on the first crank position, is changed, thereby changing the course of the orbit, i.e. the distance course of the eye bearing axis to the crank rotation axis. By changing the course, a change is brought about in the first guide element position or the second guide element position of the guide element. The eccentric device bearing is spaced a fixed distance from the crank rotation axis, so that when the course changes, the first guide element position and the second guide element position change, in particular by the same amount, whereby a stroke position of the travel element is adjusted without changing the stroke length.The adjustment position, and thus the guide element position, can be adjusted precisely and reproducibly due to the mechanical coupling.

[0019] Furthermore, according to the invention, the adjustment element can be locked in the desired setting position, particularly in a form-fitting manner, so that the setting position remains unchanged during rotation of the crank. This ensures that the first guide element position and the second guide element position, or the stroke position of the travel element, are maintained until the next change in the setting position.

[0020] Since the adjusting element of the adjusting device is located in a position that does not rotate relative to the crank, the orbit of the eye bearing axis around the crank rotation axis can advantageously be changed both when the drive device is at a standstill and during operation.

[0021] According to a preferred embodiment, the eccentric element is attached to the crank via the eccentric device bearing so that it can rotate about the eccentric device bearing's axis of rotation, wherein the eye bearing is connected to the eccentric element such that the eye bearing axis is arranged so that it can rotate about the eccentric device bearing's axis of rotation at a constant distance. The design with an eccentric element with offset axes of rotation allows the eye bearing axis to be easily adjusted on its orbit around the crank's axis of rotation by rotating the eccentric element about the eccentric device bearing's axis of rotation. By rotating the crank about the crank's axis of rotation, a relative rotation of the eccentric element to the crank can be caused. Thus, within one revolution of the crank, the eccentric element can move both about the crank's axis of rotation and about the eccentric device bearing's axis of rotation.A change in the orientation of the eccentric element by the adjusting element influences the course of the eccentricity of the eye bearing axis relative to the crank rotation axis.

[0022] The eccentric device preferably has an adjusting device that is operatively connected to the adjusting element such that actuation of the adjusting device changes the position of the eye bearing axis at an associated crank angle relative to the crank rotation axis. The adjusting device further comprises a locking device that locks the adjusting element in the adjusted position, in particular in a form-fitting manner. The change in the eye bearing axis relative to the crank rotation axis over a crank angle of 360° starting from the first crank position is the orbit. The change in the orbit is made possible by the changed position and / or orientation of the adjusting element relative to the crank rotation axis by means of the adjusting device.

[0023] The adjustment device preferably has a drive structure for accommodating a rotational movement. The adjustment device can be connected to a drive via the drive structure. The drive enables the rotational movement of the adjustment device, which can change the position and / or orientation of the adjustment element. Subsequently, the adjustment element acts mechanically on the eccentric element to adjust the eccentricity of the eye bearing axis relative to the crank rotation axis.

[0024] The adjustment device preferably comprises a motor, in particular an electric motor, connected to the drive structure. It is also conceivable for the drive device to be designed with a hydraulic motor. The adjustment of the position and / or orientation of the adjustment element can be easily automated.

[0025] According to a particularly preferred embodiment, the adjustment device comprises a control device that, in particular, controls the motor. This allows the adjustment position of the adjustment element to be adjusted automatically.

[0026] In a further development, the control device has a memory unit in which a parameter set of operating parameters, for example, of a rolling process, is stored, so that, depending on the parameter set, an associated setting position of the adjustment element can be set via a motor control. This allows the adjustment of the adjustment element to be carried out quickly and easily, for example, depending on product parameters. Due to the stored setting positions of the adjustment element, the adjustment of the adjustment element can advantageously be carried out sensorlessly and reproducibly using the motor control method.

[0027] The adjustment device preferably comprises an adjustment gear configured as a self-locking gear. This allows the adjustment and locking of the adjustment element to be performed using the same gear. The adjustment position can be achieved by driving the gear. When the gear is unloaded, the adjustment element's return is prevented, so that it is locked in the set position. The adjustment gear is resistant to loosening, e.g., slipping or twisting, and forms the locking device that locks the adjustment element in the set position.

[0028] According to a preferred embodiment, the adjusting gear comprises a threaded screw element which acts between the drive structure and the adjusting element, wherein the thread is designed to be self-locking. The threaded screw element and the adjusting element can be part of a gear and are in particular in direct engagement with one another. Adjusting the screw element changes a setting position, i.e. position and / or orientation of the adjusting element relative to the crank rotation axis. Such a configuration can reliably prevent resetting, e.g. due to slipping or twisting of the adjusting element, since a positive connection is created between the gear teeth, whereby the adjusting element is also held in its setting position with a positive fit. The adjusting device can be used to adjust the position and / or orientation of the adjusting element and to fix the position and / or orientation.Thus, adjustment and locking are advantageously achieved by the same device.

[0029] According to a preferred embodiment, the eccentric element is designed as a gear and the adjusting element as a central gear, wherein the central gear is arranged coaxially to and via the adjusting gear rotatable about the crank rotation axis and can be locked via the adjusting gear, wherein in the locked state it interacts with the gear such that the gear executes a relative rotation to the crank when the crank rotates, wherein the eye bearing axis is moved about the eccentric device bearing axis.

[0030] By angularly rotating the central gear about its axis of rotation, which is coaxial with the crank axis of rotation, the alignment of the central gear relative to the crank axis of rotation is adjusted. The central gear mechanically acts on the gear to also rotate the gear, which is coaxial with the eccentric bearing axis of rotation and firmly connected to the eye bearing. This adjusts the eye bearing. This is accompanied by a change in the position of the eye bearing axis relative to the eccentric bearing axis of rotation. Thus, the eccentricity of the eye bearing axis relative to the crank axis of rotation is adjusted and the orbit of the eye bearing axis around the crank axis of rotation is changed. As a result, the first guide element position and the second guide element position are changed in the guide direction and an adjustment of the stroke position of the travel element can be effected.

[0031] The central gear is mounted in such a way that the crank can rotate and the central gear remains stationary. The central gear can be locked in the adjusted position via the adjustment mechanism. The locked central gear interacts with the gear in such a way that the gear rotates relative to the crank when the crank rotates. Preferably, the gear rolls directly against the central gear during one rotation of the crank.

[0032] According to a further embodiment of the invention, the adjusting gear can be designed as a worm gear comprising a worm wheel that is rotationally fixedly connected to the central gear, wherein the threaded screw element comprises a worm shaft that meshes with the worm wheel. The thread of the worm shaft engages the tooth gaps of the worm wheel. Such a worm gear has a high load capacity. The worm gear provides great resistance to slipping or twisting of the adjacent worm shaft and worm wheel. This locks the central gear that meshes with the worm wheel in its adjusted position.

[0033] By adjusting the adjustment element or the central gear, the worm gear can be easily adjusted equally in both directions of rotation. Rotating the central gear around the crank axis of rotation rotates the gear, which in turn adjusts the eye bearing and subsequently the first and second guide element positions. In this way, by continuously rotating the stationary central gear, a continuous adjustment of the eye bearing axis relative to the crank axis of rotation can be achieved, enabling precise adjustment of the first position of the guide element or the movable travel element with high precision.

[0034] Preferably, the central gear and the gear are configured with the same number of teeth. Thus, after one rotation of the eccentric bearing around the crank rotation axis, the eye bearing axis returns to its starting point. As a result, the stroke length of the guide element or the guide element axis remains unchanged.

[0035] According to a preferred embodiment, the eccentric element is a lever that can be pivoted about the eccentric bearing axis of rotation by a pivot angle. The eye bearing axis is arranged on the lever eccentrically to the eccentric bearing axis of rotation. Depending on the lever's pivot angle, the position of the eye bearing axis relative to the crank axis of rotation changes, with the pivoting movement of the lever being realized by a cam control. The cam control includes the adjustment element. The cam control allows a curved path to be implemented based on the rotation of the crank, depending on the position of the adjustment element.

[0036] According to an advantageous development, the link control is implemented such that the adjusting element is a sliding block that can be rotated relative to the crank about a rotational axis parallel to the crank's rotational axis. The link is formed along the lever, in particular in the form of an elongated hole. This results in the lever's pivot angle changing over one revolution, depending on the radial distance, in particular, of the sliding block from the crank's rotational axis.

[0037] The adjustment device is designed so that the sliding block can be locked at an adjustable distance from the crank axis. This allows for good repeatability of the adjustment and provides good torque support.

[0038] By changing the position of the sliding block relative to the crank rotation axis, the pivoting angle range of the lever changes relative to the eccentric device bearing, thereby shifting the eccentricity of the eye bearing axis relative to the crank rotation axis. This shifts the deflection of the connecting rod as well as the first guide element position and the second guide element position in the guide direction and thus also the stroke position of the travel element. The adjusting gear is preferably a spindle gear connected to the sliding block. The spindle gear comprises a self-locking screw element connected to the sliding block in such a way that the distance, in particular the radial distance, of the sliding block from the crank rotation axis can be changed upon actuation of the spindle drive. The sliding block is positionally adjustable along a displacement axis of the spindle gear.The position of the sliding block can be set at a distance from the crank rotation axis using the self-locking screw element.

[0039] According to a preferred embodiment, the spindle drive has a spindle axis that is orthogonal to the crank rotation axis. A change in the position of the sliding block changes the distance between the sliding block and the crank rotation axis.

[0040] In a preferred embodiment, the adjustment device comprises a locking device that secures the adjustment element in a setting position. The locking device can, for example, guide the adjustment element during adjustment of the setting position and then lock the adjustment element when the setting position is reached.

[0041] According to a further aspect of the invention, a device for producing threads and profiles on blanks comprises a rolling die arrangement having a stationary rolling die and a movable rolling die which are guided parallel to one another in a guide direction, wherein the movable rolling die is connected to a drive device which generates a translational movement of the movable rolling die relative to the stationary rolling die, and wherein the drive device has an adjustable eccentric device for aligning the movable rolling die relative to the stationary rolling die.

[0042] The movable rolling die and the stationary rolling die each have a rolling profile. The drive device generates a linear back-and-forth movement of the movable rolling die relative to the parallel, stationary rolling die. The drive device features an adjustable eccentric device for precise alignment of the two rolling dies.

[0043] According to the invention, the drive device is designed as described above. The drive device comprises a connecting rod having a connecting rod eye at a first end and a guide element at a second end. The guide element has a guide element axis and on which the movable rolling die is mounted directly or indirectly such that the guide element axis, and thus the movable rolling die, executes a linear movement in the guide direction.

[0044] The drive device further comprises a crank, which is designed in particular as a crank arm or a crank wheel and is rotatably mounted about a crank rotation axis.

[0045] The eccentric device of the drive device is connected via an eye bearing, which has an eye bearing axis, to a connecting rod eye of a connecting rod which can rotate about the eye bearing axis.

[0046] Furthermore, the eccentric device has an eccentric device bearing that defines an eccentric device bearing rotation axis. The eccentric device is mounted on the crank via the eccentric device bearing.

[0047] The eccentric bearing axis of rotation is at a fixed distance from the crank axis of rotation. Rotation of the eccentric device about the eccentric bearing axis of rotation results in an orbit of the eye bearing axis around the crank axis of rotation, according to which the distance of the eye bearing axis to the crank axis of rotation changes within one revolution of the crank. The eccentricity of the eye bearing axis relative to the crank axis of rotation can be adjusted via the eccentric device.

[0048] For this purpose, the eccentric device has a mechanical adjustment device comprising an adjustment element that acts mechanically on an eccentric element. The adjustment element can assume different adjustment positions relative to the crank rotation axis, namely position and / or orientation, wherein the adjustment position of the adjustment element can be locked in a form-fitting manner. A respective adjustment position is assigned to an orbit of the eye bearing axis around the crank rotation axis, so that changing the course of the orbit causes a change in the position of the guide element. This makes it possible to adjust the stroke position of the movable rolling die. Thus, in the guide direction, an initial position which the movable rolling die holds before it is moved over a stroke relative to the stationary rolling die can be changed without changing the stroke length.By means of the drive device according to the invention, the alignment of the movable rolling jaw relative to the stationary rolling jaw can be adjusted with great precision and easily regulated, so that high-quality threads can be produced reproducibly.

[0049] The adjustment element can be positively locked in the desired setting position, ensuring that the setting position remains unchanged during rotation of the crank. This ensures that the stroke position of the movable rolling die is maintained until the next change in the setting position.

[0050] The adjustment element is located in a position that does not rotate relative to the crank. This advantageously allows the orbit of the eye bearing axis around the crank rotation axis to be changed both when the device is stationary and during operation.

[0051] The further developments described in the description of the drive device according to the invention can also apply to the device for producing threads and profiles.

[0052] Further advantages, features and possible applications of the present invention will become apparent from the following description in conjunction with the embodiments shown in the drawings.

[0053] In the drawing:

[0054] Fig. 1 is a perspective view of a first embodiment of a drive device according to the invention;

[0055] Fig. 2 is a side view of a first embodiment of a drive device according to the invention;

[0056] Fig. 3 is a representation of a first embodiment of a drive device in different working positions;

[0057] Fig. 4 is a representation of a first embodiment of a drive device with an adjusted adjustment element and in different working positions;

[0058] Fig. 5 is a representation of a first embodiment of a drive device with an adjusted adjustment element and in different working positions;

[0059] Fig. 6 is a sectional view of the drive device according to Fig. 2;

[0060] Fig. 7 is a side view of a second embodiment of a drive device according to the invention;

[0061] Fig. 8 is an exploded view of the drive device according to Fig. 7;

[0062] Fig. 9 is a representation of a second embodiment of a drive device in different working positions;

[0063] Fig. 10 is a representation of a second embodiment of a drive device with an adjusted adjustment element and in different working positions; and

[0064] Fig. 11 is a representation of a second embodiment of a drive device with an adjusted adjustment element and in different working positions.

[0065] Fig. 1 to Fig. 11 show in a schematic representation a drive device according to the invention, designated overall by the reference number 10, for the output movement of a travel element.

[0066] Fig. 1 shows a perspective view of a first embodiment of a drive device 10 according to the invention. The drive device 10 comprises a connecting rod 12 having a connecting rod eye 16 at a first end 14 and a guide element 20 at a second end 18, which is connected directly or indirectly, for example, by a rod linkage or the like, to a movable displacement element (not shown here). The displacement element can, in particular, be a movable rolling die of a thread rolling machine.

[0067] The guide element 20 is mounted, in particular, rotatably and / or pivotably about a guide element axis FA. The guide element 20 is mounted such that it essentially executes a translational movement in a guide direction FR that is orthogonal to the guide element axis FA.

[0068] The drive device 10 comprises a crank 22, which in this case is designed as a crank wheel. The crank 22 is mounted on a housing (not shown), for example, of a thread rolling machine, via a bearing axis 24. The crank 22 is rotatably mounted about a crank rotation axis KDA and has a crank axis KA orthogonal to the crank rotation axis KDA. The crank axis KA can rotate about the crank rotation axis KDA and, in doing so, covers a crank angle α. The crank 22 has drive structures 25 in the form of external teeth, via which the crank 22 can be driven.

[0069] The drive device 10 further comprises an eccentric device 26, which is connected to the connecting rod eye 16 via a connecting rod eye 32 having a connecting rod eye axis ALA. The connecting rod eye 16 is arranged to be rotatable about the connecting rod eye axis ALA.

[0070] The eccentric device 26 is connected to the crank 22 via an eccentric device bearing 34. The eccentric device bearing 34 has an eccentric device bearing rotation axis ELA about which it can rotate. The eccentric device bearing rotation axis ELA is arranged at a fixed distance D from the crank rotation axis KDA. The distance D is greater than a distance d between the eye bearing axis ALA and the eccentric device bearing rotation axis ELA. The eye bearing axis ALA has an eccentricity EZ relative to the crank rotation axis KDA.

[0071] During one revolution of the crank 22, a connecting line VL, which connects the crank rotation axis KDA with the eccentric device bearing rotation axis ELA and is orthogonal to the crank rotation axis and the eccentric device bearing rotation axis ELA, pivots around the crank rotation axis KDA.

[0072] In the present case, the drive device 10 is shown in a working position A, which denotes a front dead center of the crank 22, in which the crank rotation axis KDA, the eye bearing axis ALA, and the guide element axis FA lie in one plane, and the guide element axis FA exhibits the greatest deflection Smax relative to the crank rotation axis KDA. Along with the front dead center, a first guide element position 27 is assigned to the guide element 20, and a first crank position 28 of the crank 22 is assigned to the crank 22.

[0073] When the crank 22, starting from the first crank position 28, covers a crank angle of 180°, the crank 22 is assigned a second crank position 30, which corresponds to a rear dead center of the crank 22, as described in Fig. 3 to Fig. 5. The guide element 20 is assigned a second guide element position 29, corresponding to the second crank position 30, in which the guide element axis FA has the smallest deflection Smin relative to the crank rotation axis KDA and the drive device 10 has the working position B. An extension between the first guide element position 27 and the second guide element position 29 corresponds to a stroke length H of the travel element connected to the guide element 20.

[0074] The eccentric device 26 is designed such that, based on one revolution of the crank 22, starting, for example, from the first crank position 28, an orbit of the eye bearing axis ALA around the crank rotation axis KDA results. According to the orbit, the eccentricity EZ of the eye bearing axis ALA relative to the crank rotation axis KDA changes within one revolution of the crank 22.

[0075] The eccentricity EZ of the eye bearing axis ALA relative to the crank rotation axis KDA is adjustable. For this purpose, the eccentric device 26 has a mechanical adjustment mechanism 36, which has an adjustment element 38 that acts with mechanical forces on an eccentric element 40. In the present embodiment of the drive device 10, the adjustment element 38 is designed as a sliding block 39, and the eccentric element 40 is designed as a lever 41.

[0076] The lever 41 is pivotable about the eccentric bearing rotation axis ELA by a pivot angle β and pivots the eye bearing axis ALA about the eccentric bearing rotation axis ELA. The pivoting movement of the lever 41 is realized by a link control that includes the link block 39. The link block 39 is rotatable relative to the crank 22 about a rotation axis DA that is coaxial with the crank rotation axis KDA, wherein the link block 39 is received in a link 42 that is formed as an elongated hole along the lever 41. By changing the position of the link block 39 relative to the crank rotation axis KDA, a pivot angle range of the lever 41 changes, see Fig. 4.

[0077] Due to the rotation of the crank 22, the link control results in an orbit of the eye bearing axis ALA around the crank rotation axis KDA, which can change depending on the pivoting angle range of the lever 41, wherein the pivoting angle range can in turn be adjusted by changing the position of the link block 39 relative to the crank rotation axis KDA.

[0078] This means that the orbit of the eye bearing axis ALA around the crank rotation axis KDA can be varied depending, in particular, on the radial distance of the sliding block 39 from the crank rotation axis KDA. Each adjustment position of the sliding block 39 is assigned an orbit of the eye bearing axis ALA around the crank rotation axis KDA.

[0079] To adjust the position of the sliding block 39, the eccentric device 26 has an adjusting device 44, not shown here, which is described in more detail in Fig. 2.

[0080] Fig. 2 shows a side view of the first embodiment of the drive device 10 according to the invention. The eccentric device 26 has the adjusting device 44, which is operatively connected to the sliding block 39 and via which a position of the sliding block 39 relative to the crank rotation axis KDA can be adjusted.

[0081] In the present case, the adjusting device 44 comprises a spindle gear 46, which includes a spindle 48 and a self-locking screw element 50. The spindle 48 has a spindle axis SA, which is orthogonal to the crank rotation axis KDA.

[0082] The screw element 50 is connected to the sliding block 39, which is rotatably mounted about a rotational axis DA, which in this case is coaxial with the crank rotational axis KDA. When the crank axis KA covers a crank angle α, the sliding block 39 rotates about its rotational axis DA, and the lever 41 pivots about the rotational axis DA, with the lever 41 covering a pivot angle β starting from the connecting line VL, which connects the crank rotational axis KDA and the eccentric bearing rotational axis ELA. The guide element axis FA performs a linear movement in the guide direction FR.

[0083] By actuating the spindle gear 46 of the adjusting device 44, the setting position of the sliding block 39 can be changed. The adjusting device 44 has a drive structure for absorbing a rotary movement, which is connected to a motor 52, in particular an electric motor. The motor 52 sets the spindle 48 in a rotary movement, whereby a position of the screw element 50 along the spindle axis SA of the spindle 48 can be adjusted in both directions. The screw element 50 is fixed in the setting position by a locking device 74, wherein the locking device 74 is designed in this case for linear guidance of the screw element 50.

[0084] The adjustment device 44 can therefore change the setting position of the sliding block 39 by adjusting, in particular, the radial distance of the sliding block 39, which is rotatably connected to the screw element 50, from the crank rotation axis KDA, see also Fig. 4. This changes the pivot angle ß relative to the connecting line VL and thus the pivot angle range of the lever 41, which changes the orbit of the eye bearing axis ALA around the crank rotation axis KDA. Consequently, the first guide element position 27 and the second guide element position 29, as well as the stroke of the travel element, are changed.

[0085] The screw element 50 is particularly designed to be self-locking, so that the position of the sliding block 39 can be positively locked at a distance from the crank rotation axis KDA, and the adjustment position remains unchanged during the rotation of the crank 22. This ensures that the first guide element position 27 and the second guide element position 29 are maintained until the next change in the adjustment position.

[0086] The adjustment device 44 can further comprise a control device, which in particular controls the motor 52. This allows the setting position of the sliding block 39 to be adjusted automatically. The control device can, for example, access a memory unit in which a parameter set of operating parameters, e.g., of a rolling process, is stored. Depending on the parameter set, an assigned setting position of the sliding block 39 can be set by controlling the motor 52. The stored setting positions of the sliding block 39 allow the adjustment of the sliding block 39 to be quickly and easily repeated and reproduced using a control method for the motor 52. The adjustment can advantageously be carried out sensorless.

[0087] Fig. 3 shows a side view of the drive device 10 according to the invention shown in Fig. 1 in different working positions A, B, corresponding respectively to the front dead center and the rear dead center of the crank 22. The respective crank rotation axes KDA are arranged in alignment in this case. In both working positions A, B, the sliding block 39 maintains a neutral position relative to the crank rotation axis KDA, in which its rotation axis DA is coaxial with the crank rotation axis KDA. In the neutral position, the sliding block 39 rotates in the link 42 of the lever 41 about the crank rotation axis KDA.

[0088] At the front dead center of the working position A, the guide element axis FA exhibits the greatest deflection Smax relative to the crank rotation axis KDA. The guide element 20, which is guided in a guide 21 in this case, is assigned the first guide element position 27, and the crank 22 is assigned the first crank position 28.

[0089] When the crank 22 rotates from the first crank position 28, the sliding block 39 rotates about its axis of rotation DA, which in this case is coaxial with the crank axis of rotation KDA. The connecting line VL, which connects the crank axis of rotation KDA with the eccentric bearing axis of rotation ELA and is orthogonal to the crank axis of rotation KDA and the eccentric bearing axis of rotation ELA, pivots about the crank axis of rotation KDA. The sliding block control results in an orbit of the eye bearing axis ALA around the crank axis of rotation KDA, which corresponds to the eccentricity EZ of the eye bearing axis ALA with respect to the crank axis of rotation KDA. At the front dead center, the eccentricity is designated EZ-1 and at the rear dead center, it is designated EZ-2. At a crank angle α of 180° starting from the first crank position 28, the working position B is reached, which corresponds to the rear dead center and the associated second crank position 30 of the crank 22.The guide element 20 is brought in the guide direction FR over a stroke length H from the first guide element position 27 into the second guide element position 29, which has the smallest deflection Smin of the guide element axis FA relative to the crank rotation axis KDA.

[0090] In the current neutral adjustment position of the sliding block 39, the eye bearing axis ALA has the same distance from the crank rotation axis KDA at the front dead center and at the rear dead center. In this orbit, which is associated with the neutral adjustment position, the eccentricities EZ-1 and EZ-2 have the same value.

[0091] The orbit of the eye bearing axis ALA around the crank rotation axis KDA, or the eccentricity EZ of the eye bearing axis ALA relative to the crank rotation axis KDA, can be adjusted by changing the pivot angle range of the lever 41. The pivot angle range can be adjusted by changing the position of the sliding block 39 relative to the crank rotation axis KDA. This is achieved using the adjustment device 44 described in Fig. 2. The spindle 48 of the adjustment device 44 can be rotated in both directions. This allows a change in the position of the sliding block 39 relative to the crank rotation axis KDA in the axial direction of the spindle 48. The position of the sliding block 39 can be adjusted such that its rotation axis DA can be moved parallel to the crank rotation axis KDA in one direction (see Fig. 4) and in the other direction along the spindle 48 (see Fig. 5).

[0092] In Fig. 4, the drive device 10 is shown with a modified setting position of the sliding block 39 relative to the neutral setting position shown in Fig. 3. Along with the front dead center and the rear dead center, the crank 22 is shown in the respective working positions A, B, with the respective crank rotation axes KDA arranged in alignment.

[0093] By linearly adjusting the screw element 50 along the spindle axis SA, in this case in particular in an upward direction, the position of the sliding block 39 connected to the screw element 50 is adjusted relative to the neutral setting position (see Fig. 3). As a result, the rotational axis DA of the sliding block 39 is spaced from the crank rotational axis KDA by a particularly radial distance R. The changed setting position of the sliding block 39 relative to the neutral setting position changes the sliding block control. As a result, the lever 41, which is pivotable about the eccentric bearing rotational axis ELA, is rotated counterclockwise by a pivot angle ß starting from the connecting line VL (see Fig. 3 with Fig. 4).

[0094] Depending on the change in the pivot angle ß, the connecting rod eye 16 rotates around the eye bearing 32, and the eye bearing axis ALA, which is arranged eccentrically to the eccentric device bearing rotation axis ELA on the lever 41, shifts relative to the crank rotation axis KDA. This changes the eccentricity EZ of the eye bearing axis ALA relative to the crank rotation axis KDA, and thus the orbit of the eye bearing axis ALA around the crank rotation axis KDA. In this case, the orbit is changed such that the eccentricity EZ-1 at the front dead center is greater than that of the neutral setting position; compare working position A in Fig. 3 and Fig. 4, respectively.

[0095] As a result, the first guide element position 27 assigned to the neutral setting position of the sliding block 39 changes relative to the crank rotation axis KDA. The maximum deflection Smax of the guide element axis FA shifts by the amount M in the guide direction FR. This means that the stroke position of the travel element (not shown here) is shifted by a amount M in the guide direction FR.

[0096] Starting from the first crank position 28 at a crank angle a of 180°, the crank 22 reaches the working position B, which corresponds to the rear dead center. The change in the orbit of the eye bearing axis ALA around the crank rotation axis KDA results in the eccentricity EZ-2 at the rear dead center being less than the eccentricity EZ-1 at the front dead center; compare working position A with working position B.

[0097] In the working position B, the guide element axis FA has the smallest deflection Smin relative to the crank rotation axis KDA. Since the distance between the eccentric device bearing rotation axis ELA and the rotation axis DA of the sliding block 39 remains constant during the rotation of the crank 22, the stroke length H over which the guide element 20 can be moved is also constant. As a result, the smallest deflection Smin of the guide element axis FA relative to the crank rotation axis KDA is changed by the same amount M in the guide direction FR relative to the second guide element position 29 of the neutral setting position (compare the working position B in Fig. 3 and Fig. 4). This results in an adjustment of the stroke position of the travel element without an adjustment of the stroke length.

[0098] In Fig. 5, the sliding block 39 of the drive device 10 is adjusted by the same distance R relative to the crank rotation axis KDA in the other direction along the spindle axis SA, in particular downwards, compare Fig. 3 and Fig. 5. The rotation axis DA of the sliding block 39 is arranged parallel and spaced from the crank rotation axis KDA, and the lever 41 is adjusted at the front dead center starting from the connecting line VL counterclockwise over the pivot angle ß about the eccentric device bearing rotation axis ELA.

[0099] Along with the change in the position of the sliding block 39, the alignment of the eye bearing axis ALA relative to the eccentric device bearing axis ELA and thus the eccentricity EZ relative to the crank rotation axis KDA is changed. The orbit of the eye bearing axis ALA around the crank rotation axis KDA is changed in such a way that the eccentricity EZ-1 at the front dead center is now less than the eccentricity EZ-2 at the rear dead center, compare working position A and working position B. Accordingly, the respective deflections Smax and Smin of the guide element axis FA relative to the crank rotation axis KDA in the respective working positions A, B in the guide direction FR are reduced by the same amount M, each compared to the first guide element position 27 and second guide element position 29, which are assigned to the neutral setting position of the sliding block 39. This results in an overall adjustment of the stroke position of the travel element without changing the stroke length.

[0100] A respective stroke position of a travel element connected to the guide element 20 is thus assigned to each setting position of the sliding block 39. The adjustment of the stroke position of the travel element by the dimension M, in particular between 0 and 10 mm, can be carried out continuously and precisely with high reproducibility by mechanically adjusting the setting position of the sliding block 39 relative to the crank rotation axis KDA.

[0101] Fig. 6 shows a section VI-VI of the drive device 10 according to Fig. 2. The drive device 10 comprises the crank 22, which is connected to a housing (not shown here) via the bearing axis 24 and has drive structures 25 by which it can be driven. The crank 22 rotates about the crank rotation axis KDA.

[0102] Furthermore, the drive device 10 has the eccentric device 26, which comprises the eye bearing 32 and the eccentric device bearing 34.

[0103] The eccentric device 26 is mounted on a bearing journal 76 of the crank 22 via the eccentric device bearing 34. The eccentric device bearing 34 defines the eccentric device bearing rotation axis ELA, which is arranged at a fixed distance D from the crank rotation axis KDA, see Fig. 2. During one revolution of the crank 22, the eccentric device bearing rotation axis ELA rotates about the crank rotation axis KDA.

[0104] The eccentric device 26 is connected to the connecting rod eye 16 of the connecting rod 12 via the eye bearing 32, which defines the eye bearing axis ALA. The connecting rod eye 16 is rotatable about the eye bearing axis ALA. In this case, the eye bearing 32 comprises an eccentric disc 78, which is non-rotatably connected to the lever 41. The eye bearing axis ALA is fixedly mounted on the lever 41 and spaced apart by a distance d from the eccentric device bearing rotation axis ELA, wherein the lever 41 is pivotable about the eccentric device bearing rotation axis ELA.

[0105] By changing the pivot angle ß of the lever 41 about the eccentric device bearing rotation axis ELA, the lever 41 rotates the eccentric disc 78 attached to it, whereby the position of the eye bearing axis ALA relative to the eccentric device bearing rotation axis ELA as well as the eccentricity EZ relative to the crank rotation axis KDA change.

[0106] Fig. 7 shows a side view of a second embodiment of the drive device 10 according to the invention. It comprises a connecting rod 12 having a connecting rod eye 16 at a first end 14 and a guide element 20 at a second end 18, which is mounted, in particular, rotatably and / or pivotably about a guide element axis FA and is connected to a movable movement element (not shown here), in particular a movable rolling jaw.

[0107] The drive device 10 comprises a crank 22, which is mounted for rotation about a crank axis KDA. The crank 22 can be driven via external drive structures 25, in particular teeth. The crank 22 has a crank axis KA, which is orthogonal to the crank axis KDA and can rotate about the crank axis KDA. The crank axis KA covers a crank angle α, and the guide element axis FA executes a substantially linear movement in the guide direction FR.

[0108] In the present case, the crank 22 is shown in a working position B, which corresponds to a rear dead center of the crank 22 and in which the guide element axis FA has the smallest deflection Smin relative to the crank rotation axis KDA. The crank 22 is assigned a first crank position 28 and a second crank position 30, respectively, corresponding to the front dead center and the rear dead center, in which the crank rotation axis KDA, the eccentric bearing rotation axis ELA, and the guide element axis FA lie in one plane.

[0109] The drive device 10 has an eccentric device 26, which is connected to the crank 22 via an eccentric device bearing 34. The eccentric device bearing 34 has an eccentric device bearing rotation axis ELA about which it is rotatably mounted. The eccentric device bearing rotation axis ELA is spaced apart from the crank rotation axis KDA by a fixed distance D.

[0110] The eccentric device 26 is connected to the connecting rod eye 16 via an eye bearing 32, which has an eye bearing axis ALA. The eye bearing axis ALA is arranged to rotate about the eye bearing axis ALA. The eye bearing axis ALA is arranged to rotate about the crank rotation axis KDA and the eccentric device bearing rotation axis ELA. The eye bearing axis ALA is spaced apart from the eccentric device bearing rotation axis ELA by a distance d and is eccentric to the crank rotation axis KDA.

[0111] The eccentric device 26 has a mechanical adjusting device 36 which comprises an adjusting element 38 designed as a central gear 54, which is operatively connected to an eccentric element 40 designed as a gear 54 via intermeshing external teeth 58.

[0112] The central gear 54 is arranged rotatably around and coaxially with the crank rotation axis KDA. The central gear 54 is mounted in such a way that the crank 22 can rotate and the central gear 54 is stationary. When the crank 22 rotates, the gear 56 rotates relative to the crank 22 and rolls directly on the central gear 54. This results in an orbit of the eye bearing axis ALA around the crank rotation axis KDA, for example, starting from the first crank position 28.

[0113] To adjust the eye bearing axis ALA relative to the crank rotation axis KDA, the setting position of the central gear 54 relative to the crank rotation axis KDA is changed. This is achieved by an angular rotation of the central gear 54 about the crank rotation axis KDA. For this purpose, the eccentric device 26 has an adjusting device 44, which in the present second embodiment of the drive device 10 is designed as a worm gear 60. The worm gear 60 comprises a worm gear 62, which is rotationally fixedly connected to the central gear 54, and a worm shaft 64, which engages tooth gaps of the worm gear 62 via a thread 66. An axial adjustment of the worm shaft 64 can be effected by a motor 52. This results in an angular rotation of the worm gear 62 and thus of the central gear 54.By changing the setting position of the central gear 54, the gear 56, which is firmly connected to the eye bearing 32, is adjusted.

[0114] The rotation of the gear 56 is accompanied by a rotation of the eye bearing axis ALA about the eccentric device bearing rotation axis ELA. This changes the eccentricity EZ of the eye bearing axis ALA relative to the crank rotation axis KDA, so that the orbit of the eye bearing axis ALA about the crank rotation axis KDA changes. Due to the change in the eye bearing axis ALA, a deflection Smin of the connecting rod 12 shifts relative to the crank rotation axis KDA, causing an adjustment of the guide element axis FA in the guide direction FR.

[0115] The central gear 54 is locked in its setting position, in particular by the worm gear 60, so that during the rotation of the crank 22 the setting position of the central gear 54 remains unchanged and is maintained until the next change in the setting position.

[0116] Fig. 8 shows an exploded view of the second embodiment of the drive device 10. The eccentric device 26 of the drive device 10 is connected via the eccentric device bearing 34 to the crank 22, which is mounted on a housing (not shown) via a shaft 24 for rotation about its crank axis of rotation KDA. The eccentric device 26 is rotatable about the eccentric device bearing axis of rotation ELA.

[0117] Furthermore, the eccentric device 26 is connected via the eye bearing 32 to the connecting rod eye 16, which is rotatable about the eye bearing rotation axis ALA.

[0118] The guide element axis FA of the guide element 20 is pivotally mounted about the eye bearing rotation axis ALA via the connecting rod 12, in whose connecting rod eye 16 the eye bearing 32 is received. The eye bearing axis ALA is spaced apart from the eccentric device bearing rotation axis ELA by a distance d, with the fixed distance D of the eccentric device bearing rotation axis ELA from the crank rotation axis KDA being greater than the distance d from the eye bearing axis ALA. Thus, the eye bearing axis ALA has an eccentricity EZ relative to the crank rotation axis KDA.

[0119] During one revolution of the crank 22, a connecting line VL, which is orthogonal to the crank rotation axis KDA and the eccentric bearing rotation axis ELA and connects the crank rotation axis KDA with the eccentric bearing rotation axis ELA, pivots about the crank rotation axis KDA. When the guide element axis FA has the greatest deflection Smax relative to the crank rotation axis KDA, the guide element 20 is assigned the first guide element position 27, which corresponds to the first crank position 28 of the crank 22, and the guide element axis FA lies in the same plane as the connecting line VL.

[0120] At a crank angle of 180° starting from the first crank position 28, the crank 22 is assigned a second crank position 30, which corresponds to a rear dead center. The guide element 20 is assigned a second guide element position 29, corresponding to the second crank position 30, in which the guide element axis FA has the smallest deflection Smin relative to the crank rotation axis KDA, wherein the guide element axis FA lies in the same plane as the connecting line VL. The distance between the first guide element position 27 and the second guide element position 29 corresponds to a stroke length H of the crank drive.

[0121] In relation to one revolution of the crank 22, the orbit of the eye bearing axis ALA around the crank rotation axis KDA results, whereby a distance EZ of the eye bearing axis ALA to the crank rotation axis KDA changes within one revolution of the crank 22.

[0122] The eccentricity EZ of the eye bearing axis ALA relative to the crank rotation axis KDA is adjustable in this case by the mechanical action of the central gear 54 on the gear 56. The central gear 54 is arranged coaxially to the crank rotation axis KDA. The angular orientation of the central gear 54 about the crank rotation axis KDA can be adjusted via the adjusting device 44. For this purpose, the worm shaft 64 of the worm gear 60 is axially adjusted, thereby rotating the worm gear 62 and the central gear 54, which is non-rotatably connected to the worm gear 62.

[0123] The central gear 54 is operatively connected to the gear 56 via respective external toothings 58, so that the gear 56, which is coaxially connected to the eccentric device bearing rotation axis ELA and fixedly connected to the eye bearing 32, also rotates when the central gear 54 is adjusted. This is accompanied by an adjustment of the eye bearing 32. This changes the position of the eye bearing axis ALA relative to the eccentric device bearing rotation axis ELA as well as the eccentricity EZ of the eye bearing axis ALA relative to the crank rotation axis KDA. This changes the orbit of the eye bearing axis ALA around the crank rotation axis KDA. This results in an angular position of the connecting rod 12 and thus the position of the guide element axis FA in the guide direction FR or the first guide element position 27 and the second guide element position 29 changing. This adjusts the stroke position of the travel element connected to the guide element 20.

[0124] The central gear 56 can be locked in the set position via gear teeth of the worm gear 60. The set position remains unchanged during the rotation of the crank 22. This ensures that the first guide element position 27 or the second guide element position 29 is maintained until the next change in the set position.

[0125] The central gear 54 can be fixed by a locking device 74.

[0126] Fig. 9 shows the second embodiment of the drive device 10 in different working positions A, B, each corresponding to the front dead center and the rear dead center of the crank 22. In the respective working positions A, B, the crank rotation axis KDA, the eccentric bearing rotation axis ELA, and the guide element axis FA lie in one plane. The respective crank rotation axes KDA are aligned.

[0127] In this case, the central gear 54 maintains a neutral setting position relative to the crank rotation axis KDA. In each setting position, the central gear 54 is fixed in a rotationally fixed manner relative to the crank rotation axis KDA. In this case, a fixed position 70 of a first tooth 72 of the central gear 54 is marked with an arrow.

[0128] In the working position A, the first crank position 28 is assigned to the crank 22 and the first guide element position 27 is assigned to the guide element axis FA. The guide element axis FA has a maximum deflection Smax relative to the crank rotation axis KDA.

[0129] At a crank angle a of 180° starting from the first working position A or the first guide element position 27, the gear 56 rolls on the central gear 54 and the guide element axis FA moves in the guide direction FR over a stroke length H into the second guide element position 29, which coincides with the second working position B and the rear dead center of the crank 22. In the working position B, the guide element axis FA has the smallest deflection Smin relative to the crank rotation axis KDA.

[0130] The neutral setting position of the central gear 54 is assigned an orbit of the eye bearing axis ALA around the crank rotation axis KDA. According to the orbit, the eccentricity EZ of the eye bearing axis ALA relative to the crank rotation axis KDA changes within one revolution of the crank 22, with the eccentricity being designated EZ-1 at the front dead center and EZ-2 at the rear dead center. In the neutral setting position, the eccentricity EZ-1 at the front dead center and the eccentricity EZ-2 at the rear dead center are equal; compare working position A with working position B.

[0131] The orbit of the eye bearing axis ALA around the crank rotation axis KDA is accompanied by a reciprocating movement of the connecting rod 12 and a substantially linear movement of the guide element axis FA in the guide direction FR or of a travel element connected to the guide element 20. Thus, the orbit of the eye bearing axis ALA around the crank rotation axis KDA is associated with a respective stroke position of the guide element axis FA, which corresponds to the first guide element position 27 and the second guide element position 29.

[0132] By rotating the central gear 54, the gear 56 is rotated, and the eye bearing axis ALA is rotated about the eccentric bearing rotation axis ELA. As a result, the orbit of the eye bearing axis ALA is adjusted about the crank rotation axis KDA, causing the connecting rod 12 to be displaced and, consequently, the first guide element position 27 and the second guide element position 29 to be displaced.

[0133] Starting from the neutral setting position, the setting position of the central gear 54 is adjustable about its rotational axis DA, which is coaxial with the crank rotational axis KDA, in one direction of rotation (see Fig. 10) and in the other direction of rotation (see Fig. 11) by the worm gear 62. This allows the stroke position to be changed.

[0134] In Fig. 10, the setting position of the central gear 54 is adjusted by means of worm gear 60 by a maximum angle of rotation relative to the neutral setting position of the central gear 54 in a rotational direction, particularly clockwise. As a result, the position 70 of tooth 72 is realigned relative to the neutral setting position. The gear 56 operatively connected to the central gear 54 is also rotated. As a result, the orientation of the eye bearing axis ALA relative to the eccentric bearing rotation axis ELA and the crank rotation axis KDA is changed; compare Fig. 10 with Fig. 9.

[0135] By changing, in particular maximizing, the eccentricity EZ of the eye bearing axis ALA relative to the crank rotation axis KDA, the orbit of the eye bearing axis ALA around the crank rotation axis KDA is changed relative to the neutral setting position. In this case, the eccentricity EZ-1 at the front dead center is increased compared to the neutral setting position, and the eccentricity EZ-2 at the rear dead center is decreased, so that EZ-1 > EZ-2.

[0136] As a result, the deflection of the connecting rod 12 in the guide direction FR is shifted, in particular, the deflection is increased. In this case, the guide element axis FA is adjusted by the dimension M in the guide direction FR relative to the first guide element position 27, which corresponds to the neutral setting position.

[0137] At a crank angle a of 180°, starting from the first working position A, the guide element axis FA moves over a stroke length H into the second guide element position 29, which corresponds to the second working position B, the rear dead center, and the smallest deflection Smin of the guide element axis FA relative to the crank rotation axis KDA. Due to the changed eccentricity of the eye bearing axis ALA relative to the crank rotation axis KDA, the orbit of the eye bearing axis ALA around the crank rotation axis KDA is changed, with the distance D between the eccentric device bearing rotation axis ELA and the crank rotation axis remaining constant. As a result, the second guide element position 29 assigned to the neutral setting position is shifted relative to the crank rotation axis KDA by the same amount M in the guide direction FR.

[0138] Due to the change in the eccentricity EZ of the eye bearing rotation axis ALA relative to the crank rotation axis KDA, the deflection Smax and the deflection Smin between the guide element axis FA and the crank rotation axis KDA are increased by the same amount M in the guide direction FR. This results in an adjustment of the stroke position of the travel element by the amount M without changing the stroke length.

[0139] In Fig. 11, the adjustment position of the central gear 54 is in the other direction of rotation, counterclockwise relative to the neutral adjustment position. At the present maximum angle of rotation of the central gear 54 relative to the crank rotation axis KDA, the position 70 of the first gear 72 is adjusted counterclockwise relative to the neutral adjustment position, compare Fig. 9. Accordingly, the gear 56 is also rotated, and the eye bearing axis ALA is adjusted relative to the eccentric device bearing rotation axis ELA and the crank rotation axis KDA. As a result, the eccentricity EZ of the eye bearing axis ALA is shifted relative to the crank rotation axis KDA relative to the neutral adjustment position, whereby the orbit of the eye bearing axis ALA around the crank rotation axis KDA changes. In this case, the eccentricity EZ-1 at the front dead center is reduced compared to the neutral adjustment position, and the eccentricity EZ-2 of the rear dead center is increased. Therefore, EZ-1 < EZ-2.

[0140] By adjusting the eye bearing axis ALA, the deflection of the connecting rod 12 is shifted, in particular reduced. The maximum deflection Smax and minimum deflection Smin between the guide element axis FA and the crank rotation axis KDA are reduced by the same amount M in the guide direction FR, so that the overall stroke position of the travel element is shifted by the amount M.

[0141] A respective setting position of the central gear 54 is accompanied by a respective stroke position of the travel element connected to the guide element 20, wherein the stroke position can be continuously adjusted by the dimension M, in particular between 0 and 10 mm.

Claims

Patent claims 1 . Drive device (10) for the output movement of a displacement element, comprising a connecting rod (12) which has a connecting rod eye (16) at a first end (14) and a guide element (20) at a second end (18) which is connected to the displacement element, wherein the guide element (20) is mounted in such a way that it essentially executes a translational movement in a guide direction (FR), wherein the drive device (10) comprises a crank (22) which has a crank arm or a crank wheel and is mounted rotatably about a crank rotation axis (KDA), wherein the drive device (10) further comprises an eccentric device (26) which has an eye bearing (32) and an eccentric device bearing (34), wherein the eccentric device (26) is connected to the connecting rod eye (16) via the eye bearing (32), which has an eye bearing axis (ALA), in such a way that the connecting rod eye (16) can rotate about the eye bearing axis (ALA) is rotatable,wherein the eccentric device (26) is mounted on the crank arm or crank wheel via the eccentric device bearing (34), wherein the eccentric device bearing (34) defines an eccentric device bearing rotation axis (ELA) which is arranged at a fixed distance (D) from the crank rotation axis (KDA), wherein the guide element (20) is assigned a first guide element position (27), in which the crank rotation axis (KDA), the eccentric device bearing rotation axis (ELA), and the guide element axis (FA) lie in one plane, and wherein the eccentric device (26) is designed such that, due to the rotation of the eccentric device (26) about the eccentric device bearing rotation axis (ELA), an orbit of the eye bearing axis (ALA) around the crank rotation axis (KDA) results, according to which the distance (EZ) of the eye bearing axis (ALA) to the crank rotation axis (KDA) changes within one revolution of the crank (22), characterized,that the eccentric device (26) has a mechanical adjusting device (36) comprising an adjusting element (38) which acts on an eccentric element (40), wherein the adjusting device (36) is designed such that different adjusting positions relative to the crank rotation axis, (KDA), namely position and / or orientation, wherein the adjusting element (38) can be locked in this adjusting position, and wherein an orbit of the eye bearing axis (ALA) around the crank rotation axis (KDA) is assigned to an adjusting position.

2. Drive device according to claim 1, characterized in that the eccentric element (40) is fastened to the crank (22) via the eccentric device bearing (34) so ​​as to be rotatable about the eccentric device bearing axis of rotation (ELA), and the eye bearing (32) is connected to the eccentric element (40) such that the eye bearing axis (ALA) is arranged so as to be rotatable about the eccentric device bearing axis of rotation (ELA) at a constant distance (d).

3. Drive device according to claim 1 or 2, characterized in that the eccentric device (26) has an adjusting device (44) which is operatively connected to the adjusting element (38) in such a way that actuation of the adjusting device (44) changes the position of the eye bearing axis (ALA), at an associated crank angle (α), relative to the crank rotation axis (KDA), wherein the adjusting device (44) further comprises a locking device which locks the adjusting element (38) in the setting position, in particular in a form-fitting manner.

4. Drive device according to claim 3, characterized in that the adjusting device (44) has a drive structure for receiving a rotary movement.

5. Drive device according to claim 4, characterized in that the adjusting device (44) comprises a motor (52), in particular an electric motor, which is connected to the drive structure.

6. Drive device according to claim 5, characterized in that the adjusting device (44) has a control device which in particular controls the motor (52).

7. Drive device according to claim 6, characterized in that the control device has a memory unit in which a parameter set of operating parameters is stored, so that depending on the parameter set an associated setting position of the setting element (38) is set via the controlled motor (52).

8. Drive device according to one of the preceding claims 3 to 7, characterized characterized in that the adjusting device (44) comprises an adjusting gear which is designed as a self-locking gear.

9. Drive device according to claim 8, characterized in that the adjusting gear comprises a screw element (50) with a thread which acts between the drive structure and the adjusting element (38), the thread being designed to be self-locking.

10. Drive device according to one of claims 2 to 9, characterized in that the eccentric element (40) is a gear (56) and the adjusting element (38) is a central gear (54) which is arranged coaxially to and rotatable about the crank rotation axis (KDA) via the adjusting gear, wherein the central gear (54) can be locked via the adjusting gear and in the locked state interacts with the gear (56) in such a way that the gear (56) executes a relative rotation to the crank (22) when the crank (22) rotates.

11. Drive device according to claim 10, characterized in that the adjusting gear is designed as a worm gear (60) having a worm wheel (62) which is connected in a rotationally fixed manner to the central gear (54), wherein the thread-bearing screw element (50) comprises a worm shaft (64) which is in engagement with the worm wheel (62).

12. Drive device according to one of claims 10 or 11, characterized in that the gear (56) and the central gear (54) are formed with an equal number of teeth.

13. Drive device according to one of claims 2 to 9, characterized in that the eccentric element (40) is a lever (41) which is pivotable about the eccentric device bearing axis of rotation (ELA) by a pivot angle (ß), wherein the position of the eye bearing axis (ALA) relative to the crank axis of rotation (KDA) is changed depending on the pivot angle (ß) of the lever (41), wherein the pivoting movement of the lever (41) is realized by a link control comprising the adjusting element (38).

14. Drive device according to claim 13, characterized in that the adjusting element (38) is designed as a sliding block (39) of the sliding block control, wherein the sliding block (39) mounted on a rotational axis (DA) parallel to the crank rotational axis (KDA) and the lever (41) has a link (42), in particular in the form of an elongated hole along the lever (41), so that the pivot angle of the lever (41) changes over one revolution depending on a distance of the link block (39) from the crank rotation axis (KDA).

15. Drive device according to claim 14, characterized in that the adjusting gear is a spindle gear (46) which is connected to the sliding block (39).

16. Drive device according to claim 15, characterized in that the spindle gear (46) has a spindle axis (SA) which is orthogonal to the crank rotation axis (KDA).

17. Drive device according to one of claims 3 to 16, characterized in that the adjusting device (44) comprises a locking device (74) which fixes the adjusting element (38) in an adjusting position.

18. Device for producing threads and profiles on blanks, comprising a rolling die arrangement which has a stationary rolling die and a movable rolling die which are guided parallel to one another in a guide direction (FR), wherein the movable rolling die is connected to a drive device (10) for generating a translational movement relative to the stationary rolling die, which drive device has an adjustable eccentric device (26) for aligning the rolling dies with one another, characterized in that the drive device (10) is designed according to one of claims 1 to 17.

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