EP2911871A1

EP2911871A1 - Drive apparatus

Info

Publication number: EP2911871A1
Application number: EP13736530.0A
Authority: EP
Inventors: Joerg Rauschenberger
Original assignee: Modus One GmbH
Current assignee: Modus One GmbH
Priority date: 2012-10-25
Filing date: 2013-07-05
Publication date: 2015-09-02
Anticipated expiration: 2033-07-05
Also published as: EP2911871B1; JP2015533656A; JP6133429B2; WO2014063841A1

Abstract

The present invention relates to a drive apparatus (10), particularly for driving a forming device (12), with a drive unit (14) which provides a drive force (30) or a drive torque, a take-off unit (16) which has an input element (20) and a translationally movable output element (22), wherein the take-off unit (16) has a progressive force-travel characteristic between the input element (20) and the output element (22), and a transmission element (18) which is rotatably mounted on a point of rotation (26), wherein: the transmission element (18) is connected to the drive unit (14) in such a manner that a torque (38) can be transferred to the transmission element (18); the transmission element (18) has an output pivot point (28) to which a connecting element (34) is hinged, which connecting element forms together with the transmission element (18) an elbow lever (42); the connecting element (34) is connected to the input element (20) of the drive unit (16) in such a manner that a force can be transmitted onto the take-off unit (16); an angle (44) of the elbow lever (42) can be changed for a starting position of the output element (22) in order to adjust the force-travel characteristic of the output element (22).

Description

driving device

The present invention relates to a drive device, in particular for driving a forming device, with a drive unit which provides a drive force or a drive torque, an output unit having an input member and a translationally movable output member, wherein the output unit is a progressive force-displacement Course between the input member and the output member, and having a transmission element which is rotatably mounted at a pivot point, wherein the transmission element is connected to the drive unit such that a torque is transferable to the transmission element, and wherein the transmission element has an Ausgangsanlenkpunkt on in which a connecting element is articulated, which forms a toggle lever with the transmission element, wherein the connecting element is connected to the input member of the output unit in such a way that a force can be transmitted to the output unit. Such drive devices serve to provide the output member a defined force-displacement curve, for example, to drive or press a press or a punch.

For the machining of workpieces are for different processing steps such. Deep drawing, embossing or cutting / punching for the movement of the tool different force-displacement curves necessary. Pure drawing processes usually require a largely constant course of force over a long stroke, whereas embossing or calibration operations require a high force peak with an extremely progressive course. In contrast, cutting operations require high forces in a short stroke range with a rather degressive course.

For the different types of processing and the different requirements in relation to the forming technology, usually different drive concepts of the presses are used.

For drawing operations, hydraulic drives are preferably used, since they provide an approximately constant force curve for longer strokes. Different speed curves can be set well in hydraulic drives by controlling the flow rate and a switching point between rapid and working stroke can be chosen arbitrarily.

A disadvantage of the hydraulic actuators is the compressibility of the hydraulic oil, which is a compression in the higher single-digit percentage range at the necessary system pressures. This compressibility results in a high heat development, which has a negative effect on the energy balance of the hydraulic process. Further, the compressibility of the hydraulic oil affects the control of the force-displacement curve of the tool, and the force is applied with little rigidity. Therefore, for example, calibration processes are possible only with oversized forces, as a hard knocking is made difficult by the softness of the force. At the completion of a punching process is due to the compressibility highly stored spring energy suddenly released. The resulting cutting impact generates a high noise emission.

Mechanical drive systems in the form of eccentrics, cranks and knee joints usually have a low energy consumption and higher rigidity. However, the conventionally equipped with continuous electric motors drives allow only a limited variation possibility of the process flow, which can only be changed by elaborate additional equipment of the working stroke, the tool installation height and the tool speed to a small extent. In addition, a regulation during the power stroke is not possible. The mechanical drives have a progressive force-displacement curve, which is very pronounced in toggle drives. For this reason, such drives are only partially used, for example, for drawing operations with long strokes.

In the mechanical drive systems usually mechanical flywheels must be used for torque limiting of the motors and for smoothing the force peaks, whereby the technical complexity is further increased, for example by a switchable clutch. In general, the investment costs of conventional mechanical systems are high and offer little variation in the types of processing because they are limited to a progressive force-displacement curve.

Through the introduction of servo drives in the machining of workpieces, the forming processes both hydraulic and mechanical drives over a very wide range can be controlled. To avoid the disadvantages of the hydraulic drives, for example, controllable servomotors are connected to roller spindles, which are installed directly in the main power flow. In this case, however, the drive system is designed according to the highest peak force and limited the stroke speed to the maximum possible speed of the spindle, which is well below the travel speed of a hydraulic cylinder. Alternatively, the servo motor with extremely high torque without spindle or gear stage can be connected directly to a drive shaft of an eccentric or toggle lever. This results in extreme peaks in the course of the moment and thus peaks in the electrical power requirement of the drives, whereby complex energy storage are needed, which increase the technical complexity of the overall system in the form of capacitors or separate, electrically powered flywheels. Finally, the entire system must be designed according to the absolute torque or force peaks, so that the technical complexity is to be regarded as significantly higher than is actually technically necessary.

A drive for a press, in which the drive shaft without spindle o- the gear stage is driven, for example, is known from DE 10 2005 038 583 A1.

A disadvantage of the well-known drive devices is that they are technically complex and / or are determined depending on the drive technology on a system-related force-displacement curve.

It is therefore the object of the present invention to provide a drive device, in particular for driving a forming device, which is more flexible for different processing operations and inexpensive, both in the production and in the operational use by low energy consumption.

This object is achieved in the aforementioned drive device according to a first aspect, characterized in that an angle of the toggle lever for an initial position of the output member is changeable to adjust the force-displacement curve of the output member.

This object is achieved in the aforementioned drive device according to a second aspect of the present invention in that a force-displacement curve of the transmission element in the same direction or in opposite directions to the force-displacement History of the output unit is selectable to adjust the force-displacement curve of the output member.

Furthermore, the above object is achieved according to a third aspect by a press module for a forming device with a translationally movable plunger and at least one drive device for driving the plunger according to the first or second aspect or according to an embodiment of the present invention.

The above object is finally achieved by a modular press system for machining workpieces with a plurality of press modules according to the third aspect of the present invention.

Characterized in that in the first aspect of the present invention, the angle of the toggle lever is adjustable, which is connected to the output member having a progressive force-displacement curve, the force-displacement curve of the transmission element is variably adjustable, so that at the output member different force-path profiles can be provided. This is achieved by different lever effects and thus different power transmissions of the toggle lever can be adjusted at different angles of the toggle lever. By combining the transmission element with the output unit, the force-displacement curves of the two elements are superimposed, whereby a virtually arbitrary force-displacement curve can be set on the output member.

Since in the second aspect of the present invention, the force-displacement curve of the transmission element in the same direction or opposite to the force-displacement curve of the output unit can be selected, can by adding the force-displacement profiles of the transmission element and the output unit can be set almost any force-displacement curve of the output member.

Overall, the drive device according to both aspects of the present invention is therefore used for different processing or forming steps. reversible, whereby the drive device can be used flexibly. Accordingly, the object of the invention is completely solved.

In a preferred embodiment, the Ausgangsanlenkpunkt of the connecting element is connected to the input member of the output and a length of the connecting element or a distance between the output steering point and the input member adjustable.

As a result, the angle of the toggle lever and thus a lever of the toggle lever over the working stroke can be adjusted with little effort, whereby the force-displacement curve of the transmission element with little effort is adjustable.

It is further preferred if the fulcrum of the transmission element is made displaceable relative to the output unit.

As a result, the angle of the toggle lever can be changed and thus adjust a lever of the transmission member on the power stroke, at the same time the transmission member and the connecting element can be made technically less expensive.

It is further preferred if an angular position of the starting articulation point is designed to be changeable for the starting position of the output member.

As a result, alternatively, the angle of the toggle lever can be adjusted, whereby different force-displacement curves of the transmission element can be adjusted.

It is further preferred if the Ausgangsanlenkpunkt is mounted on an eccentric hub on the transmission element to adjust the angle of the toggle lever. In this case, the eccentric hub is preferably fixed in different rotational positions on the transmission element. As a result, the angle can be adjusted with a high degree of freedom and with little effort.

It is further preferred if the Eingangsanlenkpunkt is mounted on an eccentric disc on the transmission element to adjust the second toggle lever. In this case, the eccentric hub is preferably fixable in different rotational positions on the transmission element to adjust the angle of the second toggle lever.

As a result, the angle of the second knee lever can be adjusted continuously, whereby the variation of the Kraftwegverlaufs the output member is more flexible and adjustable with little effort.

It is further preferred if the connecting element is mounted on the output unit by means of an eccentric hub to adjust the angle of the toggle lever. In this case, the eccentric hub is preferably fixable in different rotational positions on the output unit in order to realize the different storage positions.

As a result, the angle of the toggle lever can be adjusted with little effort, whereby the flexibility in the setting of the Kraftwegverlaufes the output member can be further increased.

In a particular embodiment, the Ausgangsanlenkpunkt of the transmission element, the Eingangsanlenkpunkt the transmission element and the connecting element is mounted on the output unit respectively by means of an eccentric hub, so that a versatile variable adjustment of the Kraftwegverlaufes the drive device can be provided in general.

It is further preferred if an input connection point is formed on the transmission element, to which an input connection element is articulated, which forms a second toggle lever with the transmission element. As a result, a large torque can be transmitted to the transmission element with little technical effort.

It is furthermore preferred if an angle between the input articulation point and the output articulation point is changeable or adjustable.

As a result, further force-displacement curves of the transmission member can be adjusted, whereby the overall variability of the force-displacement curve of the output member is increased.

It is further preferred if a linear adjustment device is formed on the transmission element, on which the input connection point is mounted. As a result, the lever of the second knee lever can be easily adjusted, whereby the force-displacement curve of the drive device can be further varied.

It is further preferred if a plurality of connection points is formed on the transmission element, which form different positions for the input coupling point and / or the Ausgangsanlenkpunkt.

As a result, the transmission member can be manufactured with little technical effort, since the angle of the first and the second toggle lever can be changed only by a displacement of the input connection element and / or the connecting element and thus can be dispensed with elaborate adjustment mechanisms.

It is further preferred if the transmission element has two separate transmission members, which is rotatably mounted about the pivot point, wherein the Eingangsanlenkpunkt and the Ausgangsanlenkpunkt are each formed on one of the transmission members, wherein the transmission members are rotatably connected to each other in different angles of rotation. As a result, the angle of the second toggle lever can be adjusted with little effort, since the two transmission members are simply rotated relative to each other and can be connected to one another in different angles of rotation. As a result, the handling of the transmission element in general and the adjustment of the angle of the toggle lever is easier.

It is further preferred if the drive unit provides a drive torque, wherein the drive unit is connected directly or by means of a connecting rod with the transmission element.

As a result, the torque can be transmitted to the transmission element with little mechanical effort, which at the same time a particularly compact design is possible.

It is further preferred if the drive unit has an eccentric drive.

As a result, the drive device can be driven by means of a continuous electric motor.

It is alternatively preferred if the drive unit has a spindle drive.

As a result, a large force can be transmitted to the transmission element precisely.

[0049] It is further preferred if the drive unit is connected to the input articulation point by means of a connection unit which has at least one connecting rod. As a result, with little technical effort, the force can be transmitted from the drive unit to the transmission element, with the second toggle lever being able to be realized at the same time with technically little effort.

It is further preferred if the connection unit has a lever which is connected to the Eingangsanlenkpunkt.

This can be exercised with little technical effort a precise force on the transmission element.

It is further preferred if the lever arm of the lever is adjustable.

As a result, the maximum force provided by the output member can be adjusted with little technical effort.

It is further preferred if the lever is designed as a one-sided lever.

Thereby, the lever arm and thus the power transmission can be varied without changing the direction of movement of the Eingangsanlenkpunkts.

It is alternatively preferred if the lever is designed as a two-sided lever.

Thereby, the direction of movement of the Eingangsanlenkpunkts and thus the output member can be changed.

It is further preferred if the lever is designed as a triangular lever having two pivot points and a bearing point, which span a triangle. As a result, the ratio of the force of the drive to the introduction of force in the Eingangsanlenkpunkt during the stroke vary with technically simple means, whereby the force-displacement curve is additionally variably adjustable, in particular smoothed.

It is further preferred if the connection unit has a second rotatably mounted transmission element with two articulation points, wherein an angle between the articulation points is changeable.

As a result, the force-displacement curve of the output member can be set even more precisely.

It is further preferred if the output unit has a knee joint.

As a result, a precise and direct power transmission to the output member can be realized with technically little effort.

It is alternatively preferred if the output unit is formed by an eccentric.

As a result, the output unit can be realized with technically simple means in a compact design.

Overall, different force-displacement curves of the output member can be adjusted by the different variations of the drive device, whereby a total of the variability of the drive device for different steps, in particular for forming workpieces, can be used. Different large forces can be set constant or linearly increasing over the working stroke or progressively, ie with an exponential force curve over the working stroke. The force or torque to be provided by the drive unit remains constant over the entire stroke course, despite the different characteristics. Power peaks do not occur. The fact that the different force-displacement curves are adjustable only by mechanical adjustment of the drive device, the variants with relatively small and energy-efficient drive units can be realized, at the same time the advantages of mechanical drive and mechanical power transmission, with respect to a direct force with high Rigidity and economical use of energy can be used.

Thus, a drive device can be used for different processing methods, taking advantage of the different power transmissions.

It is understood that the features mentioned above and those yet to be explained not only in the particular combination given, but also in other combinations or alone, without departing from the scope of the present invention.

Embodiments of the invention are illustrated in the drawings and will be explained in more detail in the following description. Show it:

Fig. 1 is a schematic representation of a drive device for driving a forming device;

Fig. 2a to d

a schematic representation of an embodiment of the drive device in different positions and a corresponding progressive force-displacement curve;

Fig. 3a to d

the embodiment of the drive device of Figure 2a to d with alternative transmission element and an associated flat force-displacement characteristic. Fig. 4a to d

a further embodiment of the drive device with displaceable transmission element and various input connection points and associated force-displacement characteristics;

Fig. 5a to d

a further embodiment of the drive device with triangular lever and associated force-displacement characteristics;

Fig. 6a to d

a further embodiment of the variable input lever drive device and associated force-displacement characteristics;

Fig. 7a to d

an adjustment of the drive device of Figures 6a to c with a shortened stroke in favor of high force and an associated force-displacement curve.

8 shows a particular embodiment of the drive device with length-adjustable output connecting rod;

9 shows an embodiment of the drive device with two-sided input lever with variable lever arm and fixed abutment and two separate disk-shaped transmission members.

10 shows an embodiment of the drive device with two-sided input lever and variable abutment.

Fig. 1 1 shows an embodiment of the drive device with two-sided input lever with variable lever arm and fixed abutment.

12 shows an embodiment of the drive device with a triangular lever as input lever and upper bearing point. 13 shows an embodiment of the drive device with triangular lever and lower bearing point;

Fig. 14a, b

a detailed illustration of a constructive embodiment of the drive device with continuous adjustment in the setting of a progressive force-displacement curve;

Fig. 15a, b

a detailed illustration of the drive device of Fig. 14a, b; in the setting of a constant force-displacement curve;

Fig. 16a to g

Embodiments of the drive device with two rotatably mounted transmission elements or with a disc as input member of the output unit;

Fig. 17 shows an embodiment of the drive device with an eccentric as

Output unit;

18 shows an embodiment of the drive device with an eccentric drive unit;

19 shows an embodiment of the drive device with direct torque drive;

20 shows an embodiment of the drive device with a torque motor, which is connected via a connecting rod with the transmission unit.

Fig. 21 force-displacement curves of different settings of the drive device; Fig. 22 is a detailed illustration of the adjustable transmission element of Figs. 16f and g; and

Figure 23 shows an embodiment of the drive device with eccentrically rotatably mounted articulation points.

In Fig. 1, a drive device is shown schematically and generally designated 10. The drive device 10 serves to drive a forming device 12. Together, the drive device 10 and the forming device 12 form a module, in particular a press module.

The drive device 10 has a drive unit 14 and an output unit 16. The drive unit 14 is connected via a transmission element 18 to the output unit 16. The output unit 16 is formed in this embodiment as a toggle lever, which is generally mechanically connected via an input member 20 to the transmission element 18. The output unit 16 further generally has an output member 22 which is linearly or translatorily movable and is connected in the application schematically shown here with a plunger 24 which carries a lower part of a tool 24 in the forming device 12.

The transmission element 18 is rotatably mounted about a pivot point 26. The transmission element 18 has a first connection point 28, which forms an output connection point 28 of the transmission element 18. The transmission element 18 also has a second articulation point 30, which forms an input articulation point 30 of the transmission element 18. The input linkage 30 is connected to the drive unit 14 via an input link 32. The Ausgangsanlenkpunkt 28 is connected via an output connecting element 34 to the output unit 16 and to the input member 20 of the output unit 16.

The drive unit 14 is formed as a spindle drive 14 and transmits via the input link 32, which is formed in this particular embodiment as a connecting rod, a force on the Eingangsanlenkpunkt 30, wherein the force in Fig. 1 is shown schematically by an arrow 36. Alternatively, the input coupling point 30 can also be connected directly to the spindle of the spindle drive 14. As a result, a torque is transmitted to the rotatably mounted transmission element 18, wherein the torque is schematically represented by an arrow 38. The torque 38 is transmitted to the input member 20 via the output connector 34 so that a corresponding force is transmitted to the output member 22 to move the plunger 24, as schematically indicated by an arrow 40. The output unit 16 is formed in this embodiment as a toggle lever and has a progressive force-displacement curve between the input member 20 and the output member 22. In other words, the force exerted on the plunger 24 increases with increasing stroke. This is due to the particular leverage of the bell crank 16. Alternatively, the drive unit 14 may also be a servo-controlled hydraulic cylinder.

The output connection element 34, which is articulated at the output connection point 28, together with the transmission element 18 rotatably mounted at the pivot point 26, forms an output knee lever 42, which has a characteristic force-displacement profile. The force-displacement curve is adjustable via an angle 44 of the toggle lever 42 of the Ausgangsanlenkpunkts 28. The angle 44 is adjustable or exchangeable for a specific starting position of the output member 22 or for a predefined position of the output member 22, so that a working stroke of the drive apparatus 10 begins at different settings with different values of the angle 44. As a result, force-displacement characteristics of the transmission element 18 can be adjusted, which run in the same direction or in opposite directions to the force-displacement curve of the output unit 16, so that as a result different force-displacement characteristics of the output member 22 can be adjusted.

The input link 32, which is hinged to the input link 30, forms an input link 46 together with the transfer element 18. The input link 46 has an angle 48 formed between the input link 32 and the pivot point 26 at the input link 30. If the angle 44 is set to a small value in an initial position of the output member 22, the working stroke of the connecting member 34 starts with a large force (reverse toggle), which drops over the power stroke and at an angle 44 of about 90 ° ends with a low value. Through this degressive force-displacement curve, a force-displacement curve of the output member 22, which is trough-shaped, concave, develops in the sum with the progressive course of the toggle lever 16, with higher forces at the beginning and at the end and a low point in the middle region , By appropriate adjustment of the angle 48 in the force input region of the transmission element 18, namely 90 ° at about half a stroke, acts on the transmission element, a maximum moment in the central region, whereas it reaches a minimum at the beginning and at the end of the stroke. Due to the superimposition of this convex moment profile with the above-described concave profile of the following combined elements, the force-displacement curve of the output member 22 is greatly smoothed and comes relatively close to a constant course over a wide stroke range. Exceptions are the extreme positions, especially the end of the stroke, since in the extended position the force of the toggle lever goes to infinity. If necessary, the stroke should therefore be stopped beforehand. If, however, the angle 44 is set to a value of about 90 ° in an initial position of the output member 22, the working stroke of the connecting element 34 begins with a small force which increases over the working stroke and ends at an angle 44 of near 180 ° with a maximum , This progressive course reinforces the likewise progressive course of the output member 22. As a result, a highly progressive, at the end of the working stroke extremely increasing force-path curve of the output member 22, as explained in more detail below. This course can be additionally influenced by a variation of the angle 48, namely again amplified or attenuated.

As a result, therefore, the force-displacement characteristic of the output member 22 can be set differently depending on the angle 44 for an initial position of the output member 22, whereby the drive apparatus 10 can be used for different operations. By combination with the variably adjustable additional angle 48 of the force-displacement curve of the output member 22 is almost arbitrarily adjustable. In Fig. 2a to c, an embodiment of the drive device 10 for different positions of the power stroke S is shown schematically and wherein in Fig. 2d, the resulting force-displacement curve of this embodiment is shown. In the embodiment of Fig. 2a to c, the transmission element 18 is designed as a rigid, one-piece triangle lever, wherein the angle 44 in an initial position of the output member 22 has approximately 90 °. The angle 48 of the input lever 46 is about 45 ° in the home position. The input linkage point 30, the output linkage point 28 and the pivot point 26 span an angle of about 100 °.

The three different positions of the power stroke S are shown in FIGS. 2a to c and the different positions of FIGS. 2a to c are marked S1, S2 and S3 in the diagram in FIG. 2d.

Due to the particular leverage of the Eingangsanlenkpunkts 30 and the Ausgangsanlenkpunkts 28 in the three positions of the power stroke S of Fig. 2a to c, there is a highly progressive or increasing force-displacement curve of the output member 22, the in Fig. 2d is shown. In Fig. 2d, the individual positions of the working stroke, which are shown in Figures 2a to c, respectively marked S1, S2 and S3. It follows that the force that is transmitted through output member 22, for the working stroke S1 and S2 of Figures 2a and b only slightly different, since the leverage in the two rotational positions of the transmission element 18 changes only slightly, whereas the Force for the working stroke S3, which corresponds to the position of Fig. 2c, is significantly larger, since here the lever of the Eingangsskniehebels 46 is particularly favorable and the lever of the Ausgangskniehebels 42 is stretched particularly flat.

Figures 3a to c show the drive device 10 in three different positions of the power stroke S and Fig. 3d shows an associated force-displacement curve for the three positions of the power stroke S. The drive device 10 corresponds to the drive device of Figures 2a to c wherein the transmission element 18 is formed with changed angles 44, 48 of the output knee lever 42 and the input knee lever 46. The same elements are designated by the same reference numerals, in which case only the special features are explained. In this embodiment, the transmission element 18 is designed as a one-piece, rigid element, in which the input connection point 30, the output connection point 28 and the pivot point 26 form an angle of approximately 190 °. In the illustrated in Fig. 3a starting position of the power stroke, which is denoted by S1, the angle 44 of the Ausgangskniehebels 42 is very small and the angle 48 of the Eingangskniehebel 46 about 90 °. As a result, a large force is transmitted from the transmission element 18 in this position of the power stroke S1. In the position of the power stroke, which is shown in Fig. 3b and is denoted by S2, the angle 44 and the angle 48 in the intermediate region, so that from the transmission element 18 an average force is transmitted and in the position of the working stroke, which in Fig. 3c is shown and designated S3, the angle 44 at 90 ° and the angle 48 is very large, whereby the resulting lever arm of the drive 14 to the pivot point 26 is so very small, so that a small force transmitted from the transmission element 18 becomes. This force-displacement curve of the transmission element 18 shown in FIGS. 3 a to c is formed approximately counter to the progressive force-displacement curve of the output unit 16, so that in the sum over a long distance an approximately linear force-displacement History of the output member 22 results. This force-displacement curve is shown for the three positions of the working stroke S1, S2, S3 in FIG. 3d.

The transmission elements 18 shown in Figures 2a to c and 3a to c are formed as a rigid one-piece elements with a fixed angle between the Eingangsanlenkpunkt 30 and the Ausgangsanlenkpunkt 28 so that a change of the angle 44 of the Ausgangsskniehebels 42 only by replacing the Transmission element 18 can take place.

In Fig. 4a to c an alternative embodiment of the transmission element 18 in different installation positions and in different positions of the power stroke S is shown. The same elements are designated by the same reference numerals, in which case only the special features are explained.

The transmission element 18 is formed as a rigid element and in this embodiment has a semicircular disk shape. The transmission element 18 has four connection positions, which are formed as round recesses are. The terminal positions serve to connect the input connector 32 in different positions to the transmission member 18 and to articulate at the different positions, respectively, to realize different angles of the output knee lever 42 or the input knee lever 46. One of the terminal positions serves to rotatably support the transmission element 18 at different positions and to form the pivot point 26 accordingly.

In the figures 4a to c are each two different Anschlußbzw. Storage options of the transmission element 18 shown, wherein a first connection variant is shown by solid lines and a second connection variant is shown with dashed lines.

In the first connection variant, the input coupling point 30 and the output coupling point 28 are arranged at an angle of approximately 190 ° relative to the pivot point 26, so that in the starting position of the power stroke S1 illustrated in FIG. 4a the angle 44 of the output knee lever 42 is approximately 90 ° and the angle 48 of the input lever 46 has an obtuse angle of about 120 °.

In the second connection variant (shown in dashed lines), the transmission element 18 is rotatably mounted to the right at the output unit 16 at the pivot point 26 ', wherein the Eingangsanlenkpunkt 30' relative to the first connection variant is offset by about 90 °, so that in the starting position of the working stroke S1 shown in Fig. 4a of the angle 44 'of the output knee lever 42' is an acute angle of about 30 ° and the angle 48 'of the input buckle lever 46 about 90 °.

In Fig. 4d, two force-displacement curves for the two installation variants of the transmission element 18 are shown in accordance with a solid and a dashed line. Due to the particular adjustment of the angles 44, 48 via the working stroke positions S1, S2, S3 shown in FIGS. 4a to c, the transmission element 18 in the first installation variant has a progressive force-displacement curve, so that as a result of the total force -Weg course of the output member 22, which is shown in Fig. 4d, has a progressive course. In contrast, in the second installation variant, the transmission element 18 on a force-displacement curve, which is in opposite directions to the progressive force-displacement curve of the output unit 16 or in other words in the position S1, a large power transmission in the position S2, an average power transmission, in the Position S3 allows a low power transmission, so that as a result, the total force-displacement curve of the output member 22 over the working stroke between S1 and S3 is substantially constant, as shown in Fig. 4d.

By the particular embodiment of the transmission element 18 shown in Figures 4a to c with the different connection positions for the pivot point 30 and the pivot point 26, the transmission element 18 can be installed or connected so that different force-displacement paths of Output member 22 are adjustable.

A variant of the drive device 10 from FIGS. 4a to c with an additional intermediate lever, which is connected between the drive unit 14 and the input linkage point 30, is shown schematically in FIGS. 5a to c. The same elements are designated by the same reference numerals, in which case only the special features are explained.

FIGS. 5 a to c show a first variant with solid lines, in which the drive unit 14 is connected to a one-sided triangular lever 50 in order to transmit the introduced force 36 to the input coupling point 30. The triangular lever 50 is designed as a one-sided lever and has a bearing point 52 and two articulation points 54, 56 for a connecting rod of the drive unit 14 and for an output connecting rod for connecting to the transmission element 18.

FIGS. 5a to c show a second connection variant without the triangular lever 50 with dashed lines, which substantially corresponds to the second connection variant from FIGS. 4a to c. By the triangular lever 50, the input force 36 in its effect on the Eingangsanlenkpunkt 30 in addition to the variation of the force acting angle 48 is still changed by the relative to the fulcrum 52 different ratio of the resulting lever arms of the force direction 36 and the Verbindungspleuels between the articulation points 56 and 30. In the working stroke position S1, the lever arm of the driving force 36 with respect to the fulcrum 52 is larger than the resultant lever arm of the connecting rod. As a result, the input force 36 is amplified in its effect on the input connection point 30. In the working stroke position S3, the ratio is reversed, the input force 36 is thus reduced in their effect. In the working stroke position S2, the ratio is balanced. As a result, in the total summation, the force in the output unit 16 is increased in the first half of the power stroke, reduced in the second half compared to the embodiment without the triangular lever 50. Thus, over a large area of the power stroke results in a constant force-displacement curve it is shown in Fig. 5d with a solid line. In comparison, the connection variant without the triangular lever 50 has a force-displacement curve which increases linearly over the same working stroke, as is likewise shown (as a dashed line) in FIG. 5d.

A further variant of the drive device 10 is shown schematically in FIGS. 6a to c. The drive unit 14 is connected via a variable one-sided lever 60 with the Eingangsanlenkpunkt 30 of the transmission element 18. The same elements are designated by the same reference numerals, in which case only the special features are explained.

Two connection variants of the one-sided lever 60 are shown in FIGS. 6a to c, wherein a variant with a small lever is shown with solid lines and a second connection variant with a large lever is shown with dashed lines.

The one-sided lever 60 is mounted at one bearing point 62 on one side and has an Ausgangsanlenkpunkt 64, which forms a fixed lever path to the bearing point 62 and further includes an Eingangsanlenkpunkt 66 which is connected to the drive unit 14, wherein the Eingangsanlenkpunkt 66 variable or displaceable is formed so that the lever of the Eingangsanlenkpunkts 66 can be varied relative to the bearing point 62.

In Fig. 6d two force-displacement curves of the two connection variants of the figures 6a to c for the different working stroke positions S1, S2, S3 are shown, wherein the variant with a small lever of the one-sided lever 60 with a solid line and the second variant with a large lever of the one-sided lever 60 is shown as a dashed line. By varying the lever or the lever action of the one-sided lever 60, the maximum force transmitted by the drive device 10 can be varied, wherein, as shown in FIG. 6d, the force-displacement curve is only shifted in parallel. This results in a further possibility of variation for the use of the drive device 10.

FIGS. 7a to c show another setting variant of the drive device 10 with the one-sided lever 60. In this case, the transmission element 18 is compared to the variants of Fig. 6a to c even closer to the output unit 16 towards offset rotatably supported. The same elements are designated by the same reference numerals, in which case only the special features are explained.

By the displacement of the transmission element 18 of the working stroke S of the output member 22 is shortened. The starting position of the output member 22 is in a range in which the output unit 16 already develops a high initial force because of its progressive course. Due to the small value of the angle 44 (reverse toggle lever), the transmission element 18 transmits a high force at the start via the Ausgangsanlenkpunkt 28 on the output unit 16, which decreases degressively in the course of the power stroke. In conjunction with the already described in Fig. 1 influence of the angle 48 in the force introduction region of the transmission element 18 results in a nearly constant force-displacement curve, as already described with reference to Figure 3 ad, but at a higher level of force, at the expense of a shorter working stroke , By the one-sided lever 60, the basic ratio of the introduction of force in the Eingangsanlenkpunkt 30 in the transmission element 18, as already described with reference to FIG. 6 ad, varied and the total force thus be reinforced again. In the result can be set by a high power over a shortened stroke S, as shown in Fig. 7d.

Fig. 8 shows a further embodiment of the drive device 10 with a length-adjustable output connecting element 34. Thus, the same effect is achieved as with the displacement of the pivot point 26 of the transmission element 18, namely the variation of the angle 44. The pivot point 26 can therefore at this Embodiment remain fixed. A first variant with a short connecting element is shown in FIG. 8 with solid lines, whereas a second variant with an extended connecting element is shown with dashed lines. The same elements are designated by the same reference numerals, in which case only the special features are explained.

The transmission element 18 is formed as a rigid one-piece disc which is rotatably mounted at the pivot point 26. The transmission element 18 has three connection points at which the input connection element 32 can be steered at two different positions in order to adjust the angle 48 of the input knee lever 46, and the output connection element 34 is articulated at the output connection point 28. Further, the output connector 34 has a length adjustment member 68 to vary a length of the output connector 34 and thereby adjust the angle 44 of the output knee lever 42.

In the first connection variant shown in Fig. 8, the input linkage point 30 is formed in the outer terminal position, wherein the length adjustment member 68 is shortened such that the angle 44 in the illustrated in Fig. 8 Ausgangsarbeitshubposition is about 90 ° and through the choice of the connection position of the Anlenkpunkts 30 of the angle 48 of the Eingangsskniehebels 46 has about 120 °. This results in simple means a progressive force-displacement curve of the output member 22, which corresponds to the representation in Fig. 2d.

In the second connection variant illustrated in FIG. 8, the input connection point 30 'is articulated on the interior of the connection points, so that an angle of approximately 30 ° is formed between the two points 28, 30'. The length adjustment The guiding element 68 is extended in such a way that, in the starting position of the working stroke position shown in FIG. 8, the angle 44 'of the output knee lever 42 is pointed and has less than 45 °. In contrast, the angle 48 'of the input knee lever 46 in this Arbeitshubposition is about 90 °. From this setting results in an approximately linear force-displacement curve of the output member 22, which corresponds to the representation in Fig. 3d. By the choice of the articulation positions on the transmission element 18 and the choice of the length of the output connection element 34 by means of the length adjustment element 68, different force-displacement characteristics of the output element 22 can also be set between the extreme situations. In a further embodiment, the output linkage point 28 can also be displaced in different connection variants in order to vary the angle 44.

In Fig. 9, an alternative embodiment of the drive device 10 is shown schematically, wherein the transmission element 18 is formed of two rotatable discs. The transmission element 18 has an input member 70 and an output member 72, wherein the Eingangsanlenkpunkt 30 is formed on the input member 70 and the Ausgangsanlenkpunkt 28 on the output member 72. The input member 70 and the output member 72 are rotatably mounted at the pivot point 26. The input member 70 and the output member 72 are rotatable relative to each other and are rotatably connected to each other in different angles of rotation connectable (not shown) to transmit the torque 38 to the output unit 16. The input member 70 and the output member 72 are rotatably connected to each other in different angular positions connected to different angular positions of the input linkage point 30 and the Ausgangsanlenkpunktes 28 can be adjusted relative to each other. Further, the output connector 34 has the length adjustment member 68 to adjust the angle 44 of the output knee lever 42 accordingly.

In this embodiment, the drive unit 14 is connected via a two-sided lever 74 to the Eingangsanlenkpunkt 30, wherein a pivot point 76 of the drive unit 14 is slidably mounted on the two-sided lever 74 and the two-sided lever 74 is mounted at a pivot point 78 with a fixed abutment , In this embodiment, it is particularly advantageous that the relative rotation of the articulation points 28, 30 can be adjusted by the variable transmission element 18 with simple means and a few simple steps and wherein the length adjustment element 68, the angle 44 of the Ausgangsskniehebels 42 are set by simple means can. Furthermore, the force of the drive unit 14 can be deflected via the two-sided lever and the size of the transferable force can also be adjusted.

FIG. 10 schematically shows a variant of the drive device 10 from FIG. 9. The same elements are designated by the same reference numerals, in which case only the special features are explained. The drive unit 14 is connected via the two-sided lever 74 to the Eingangsanlenkpunkt 30, in this embodiment, the abutment of the pivot point 78 is slidably and variably and the drive unit 14 is articulated by means of a fixed Anlenkpunkts 80 on the two-sided lever 74. As a result of the particular embodiment of the two-sided lever 74, it is likewise possible, as in the embodiment according to FIG. 9, to set different forces on the output member 22.

In Fig. 1 1, a further variant of the drive device 10 of FIG. 9 is shown schematically. The same elements are designated by the same reference numerals, in which case only the special features are executed.

In the variant shown in FIG. 11, the drive unit 14 is arranged laterally next to the transmission element 18 and connected to the two-sided lever 74 via the displaceable articulation point 76. As a result, the force 36 exerted by the drive unit 14 is transmitted in the same direction to the transmission element 18. By this embodiment, a particularly compact design of the drive device 10 is generally possible.

In Fig. 12, a further variant of the drive device 10 is shown schematically. The same elements are designated by the same reference numerals, in which case only the special features are explained. The drive unit 14 is connected in this embodiment via a triangular lever 82 with the Eingangsanlenkpunkt 30. The triangular lever 82 has an input pivot point 84 and an output pivot point 86 and is rotatably supported at a pivot point 88. In this embodiment, the triangular lever 82 is rotatably mounted about the pivot point 88, which is mounted above the triangle lever 82. As a result, the force 36 is transmitted in the same direction from the drive unit 14 to the input connection point 30.

FIG. 13 schematically shows a variant of the drive device 10 from FIG. 12. The same elements are designated by the same reference numerals, in which case only the special features are explained.

In the embodiment of FIG. 13, the triangular lever 82 is rotatably mounted about the pivot point 88, which is mounted below the triangular lever 82.

Thereby, the force 36, which is exerted by the drive unit 14, transmitted in the opposite direction to the articulation point 30. In other words, a thrust force becomes a tensile force and vice versa.

FIGS. 14 a and b schematically illustrate a detailed embodiment of the drive device 10 with a variable one-sided lever 60 and a variable transmission element 18 in different working stroke positions. The same elements are designated by the same reference numerals, in which case only the special features are explained.

The variable lever 60 is rotatably supported about the fulcrum 62. The output link 64 is connected to the input link 30 of the transfer element 18 via the input link 32. The input connection point 66 is connected via a connecting rod to the drive unit 14, which is designed as a spindle drive 14 in this embodiment. The Eingangsanlenkpunkt 66 is adjustable by means of an adjusting screw 90 in the axial direction of the one-sided lever 60, so that the lever travel, which acts between the Eingangsanlenkpunkt 66 and the Ausgangsanlenkpunkt 64 and the pivot point 62, via the adjusting screw 90 is adjustable. The adjusting screw 90 is connected to a corresponding rotary control element 92 in order to simplify or automate the handling.

The transmission element 18 has the input member 70 and the output member 72, which are rotatably connected to each other in different angles of rotation and are rotatably mounted about the pivot point 26. The input member 70 and the output member 72 each have a tooth portion 94 which are adjustable by means of a gear 96 relative to each other to adjust the angular position. As a result, the relative position of the Eingangsanlenkpunkts 30 to the Ausgangsanlenkpunkt 28 by simple means and preferably set automatically.

The pivot point 26 is displaceably mounted and designed displaceable relative to the output unit 16 by means of an adjusting screw 98. The adjusting screw 98 is connected to a control element 100, preferably to adjust the corresponding position of the pivot point 26 by motor.

In Fig. 14a an initial position of the working stroke is shown, in which the angle 44 is about 90 ° and in Fig. 14b, an end position of the power stroke is schematically shown, in which the angle 44 of the Ausgangskniehebels is about 130 °. This results in a progressive force-displacement curve.

In Figures 15a and b, the detailed embodiment of Figures 14a and b is shown in an alternative setting with respect to the relative angular position of the input linkage point 30 and the output linkage point 28 and the pivot point 26. The same elements are designated by the same reference numerals, in which case only the special features are explained.

In the adjustment illustrated in Figures 15a and b, the input member 70 and the output member 72 of the transmission member 18 are set at a different angular position to each other so that a larger angle of about 270 ° between the input linkage point 30 and the output linkage point 28 relative to the pivot point 26 is realized. Further, the pivot point 26 is relative to the setting of the Figures 14a, b offset to the output unit 16, so that a smaller angle 44 of the output Ziehhebels 42 is set in the starting position of Fig. 15a. This results in an approximately constant force-displacement curve of the output member 22. FIG. 15b shows an end position of the working stroke for the adjustment from FIG. 15a.

In general, can be adjusted by the three adjustment options from the embodiment of FIGS. 14 and 15 and by the three degrees of freedom of the drive device 10 of Figures 14 and 15, a plurality of different force-displacement paths of the output member 22, whereby In general, the possibility of variation of the drive device 10 is improved and automated.

In Fig. 16a, another embodiment of the drive device 10 is shown schematically. The same elements are designated by the same reference numerals, in which case only the special features are explained.

The transmission element 18 is formed by the input member 70 and the output member 72, which are rotatable relative to each other and rotatably connected to each other. The output connector 34 has the length adjustment member 68 to adjust the angle 44 accordingly. The drive unit 14 is connected via the two-sided lever 74 to a second transmission element 102, which is connected to the first transmission element 18 in order to transmit the force transmitted by the drive unit 14 as the torque 38 to the transmission element 18. The transmission element 102 has an input member 104 and an output member 106 which are rotatably mounted at a pivot point 108 and which are rotatable with each other and rotatably connected to each other. An input connection point 110 is formed on the input element 104, and an output connection point 12 is formed on the output element 106. The input member 104 and the output member 106 are rotatable to each other and rotatably connected to each other to adjust different angular positions of the Eingangsanlenkpunkts 1 10 and the Ausgangsanlenkpunkts 1 12 relative to each other. The Eingangsanlenkpunkt 1 10 is connected to the two-sided lever 74 and connected to transmit the power from the drive unit 14 to the transmission element 102. The Ausgangsanlenkpunkt 1 12 is connected by means of a connecting rod with the articulation point 30 of the transmission element 18 to a Force from the transmission element 102 to the transmission element 18 to transmit. By this embodiment with the two rotatably mounted and adjustable transmission elements 18, 102 and the two-sided lever 74, the force-displacement curve of the output member 22 is very precisely adjustable.

FIG. 16b shows a variant of the embodiment from FIG. 16a. The same elements are designated by the same reference numerals, in which case only the special features are explained.

The length adjustment member 68 is set in this embodiment so that the pivot point of the output unit 16 is offset and the output member 22 is moved by a tensile load of the Anlenkpunkts up and a pressure load down. As a result, the direction of movement of the output member 22 can be reversed for the same movement of the drive unit 14.

FIG. 16c shows a further embodiment of the drive device 10 from FIG. 16a, in which the output unit 16 has a plurality of different articulation points in order to enable a length adjustment and a force / displacement variation. The same elements are designated by the same reference numerals, in which case only the special features are explained.

The output unit 16 has a rigid plate or disc which is rotatably mounted and is articulated to a driven connecting rod, which is connected to the output member 22 and forms a toggle lever. The rigid disc has a plurality of different articulation points 1 13 ', 1 13 ", 1 13"', on which the input member 20 can be articulated. As a result, a further length adjustment and thus a corresponding angular adjustment of the toggle lever can be realized, whereby an additional force / displacement variation is made possible.

In Fig. 16d, another embodiment of the drive device 10 is shown schematically, in which the transmission element 102 is connected by means of a length adjustment element with the output unit 16, in this embodiment has a rigid plate or disc with three points of articulation and forms a toggle lever. The same elements are designated by the same reference numerals, only special features are explained here.

In that the transmission element 102 is connected to the rigid plate or disk of the output unit 16, the direction of movement of the output member 22 can be reversed, so that the output member 22 is moved upward, as the Ausgangsanlenkpunkt 1 12 is moved upward, as indicated by an arrow 1 15. As a result, the direction of movement of the output member 22 can be reversed with simple means and at the same time the required installation space for the drive device 10 can be reduced.

In Fig. 16e, another embodiment of the drive device 10 is shown schematically. The same elements are designated by the same reference numerals, in which case only the special features are explained.

The drive device 10 of FIG. 16e has compared to the embodiment of FIG. 16d, two output units 16, 16 ', which are formed by two parallel toggle lever and connected by a connecting rod 1 17. The connecting rod 1 17 connects the two output units 16, 16 'such that the two output members 22, 22' are moved in parallel with the same force / displacement curve. As a result, a more uniform distribution of force on the tool 24 can be achieved.

In Fig. 16f, a further embodiment of the drive device 10 is shown schematically, in which the Eingangsanlenkpunkt 30 is continuously linearly adjustable and different Ausgangsanlenkpunkte 28 can be selected. The same elements are designated by the same reference numerals, only special features are explained here.

The input coupling point 30 is mounted on the transmission element 18 so as to be linearly displaceable at different distances from the pivot point 26 by means of a linear adjusting device 1 19, in order to move the lever of the corresponding input branch. lever 46. The transfer element 18 has different output linkage points 28, 28 ', 28 "to bias the link 34 against the transfer element 18 in different positions and to adjust the angle of the corresponding toggle lever 42. The link 34 has different points of articulation Alternatively or additionally, the connecting element 34 may have the length adjustment element 68. The mode of operation of the mounting of the connection element 34 at the output connection points 28, 28 ', 28 "is hereinafter explained in more detail.

In Fig. 16g, a variant of the embodiment of Fig. 16f is shown schematically. The same elements are designated by the same reference numerals, only special features are explained here.

In this case, the connecting element 34 has different connecting points in order to fix the connecting element 34 at the various output connecting points 28, 28 ', 28 "and a plurality of connecting points or bearing points in order to fix the connecting element 34 to the input member of the output unit 16 The output unit 16 also has a plurality of articulation points 20, 20 ', which can form the input member 20, 20' of the output unit 16 and can be correspondingly connected differently with the connecting element 34. This results in a large number variations in the adjustment of the angle 44 of the bell crank 42 possible.

It is understood that the variants of FIGS. 16f and 16g can also be combined with the previous embodiments, in particular with the parallel toggle levers of FIG. 16e.

FIG. 17 schematically shows a variant of the drive device 10 from FIG. 9 with an alternative output unit. The same elements are designated by the same reference numerals, in which case only the special features are explained. The output connection element 34 with the length adjustment element 68 is connected to an eccentric 1 14, which forms the output unit of the drive device 10.

The eccentric 1 14 has the input member 20 which is rotatably mounted eccentrically about a pivot point 1 16 and the output member 22 moves in accordance with translational depending on the rotational position. As a result, an output unit 16 can be formed by simple means.

In Fig. 18, an alternative embodiment of the drive device 10 is shown schematically with an alternative drive unit. The drive device 10 has an eccentric 1 18, which forms the drive unit. The eccentric 1 18 is mounted eccentrically about a pivot point 120 and is driven with a torque by a drive unit, so that a force by means of the input connection member 32 is transferable to the transmission element 18. As a result, the drive device 10 can be driven by simple means. In a simple embodiment, the input connection element 32 of the eccentric member 1 18 is connected directly to the input member 20 of the output unit and additionally has the length adjustment element 68. The transmission element 18 is formed by the eccentric disc, wherein a rotational movement of the eccentric 1 18 acts directly on the input member 20. In this case, the input connecting element 32 forms with a center of the eccentric disc and the eccentric pivot point 120, the Ausgangsskniehebel 42nd

In Fig. 19, an alternative embodiment of the drive device 10 is shown schematically. The same elements are designated by the same reference numerals, in which case only the special features are explained.

The transmission member 18 is formed in this embodiment as a simple lever, which is driven in a circle by a torque motor, and is mounted in the center 26 and in the pivot point 26 of the motor. In this embodiment, the transmission element 18 has only the output connection point 28, which is connected to the output unit 16 via the output connection element 34. This embodiment illustrated in FIG. 19 forms the simplest embodiment of the invention. However, in contrast to the previously presented embodiments, the motor is not utilized uniformly over the course of the stroke and must be designed for a high torque peak, ie be oversized.

In Fig. 20, another embodiment of the drive device 10 is shown schematically. The same elements are designated by the same reference numerals, in which case only the special features are explained.

The transmission element 18 is connected via a connecting rod with a torque motor 122 to transmit the torque 38 to the transmission element 18. This represents an alternative drive option for the drive device 10. Thus, the tips are avoided in the moment demand compared to the embodiment described in Fig. 19 and the engine can therefore be made smaller.

In Fig. 21, different force-displacement curves are shown schematically in relation to each other, which is adjustable by the different settings or the different embodiments of the present invention.

It is clear that the settings both short strokes with high forces and large strokes with constant high or low forces are adjustable. Furthermore, progressive force-displacement curves can be set, as well as linearly increasing force-displacement curves can be realized. For all the curves shown, the driving forces are constant over the entire stroke. An exception to this is only the embodiment of FIG. 19.

As a result, a variable use of the drive device 10 is possible, which can be adapted to the requirements of different processing or forming steps, and yet due to the uniform demand for driving force economical use of drive units in the smallest possible Design allows and at the same time allows the waiver of expensive energy storage devices.

In Fig. 22, the different Ausgangsanlenkpunkte 28 of the transmission element 18 are shown in detail. The same elements are designated by the same reference numerals, in which case only the special features are explained.

The connecting element 34 or the connecting rod 34 can be connected at the different output connection points 28, 28 'by means of plug connections in order to articulate the connecting rod 34 in different positions on the transmission element 18. The connection between the connecting rod 34 and the connecting element 18 in this case has on the connecting rod 34 a plug connection 130 into which a movably mounted plug element 132 can be inserted in order to connect the connecting element 18 to the connecting rod 34. The plug-in elements 132 each have a plurality of parallel locking pins, which engage in corresponding receptacles of the respective connectors 130. As a result, the diameter of the individual locking pins can be kept small and a favorable length-diameter ratio of the locking pins can be achieved. The connecting element 18 in this case has two parallel rigid plates, between which the connecting rod 34 is guided laterally and articulated by the connection between the plug-in elements 132 and the connector 130 at the different Ausgangsanlenkpunkten 28, 28 'and connectable to the transmission element.

The plug-in elements 132 are each assigned a spindle wheel 134, which moves the respective plug element 132 in the axial direction and can accordingly insert into the plug connection 130 or detach from the plug connection 130. Spindle gear 134 translates rotational motion into axial movement to move plug members 132 accordingly. The spindle gear 134 and the spindle gears 134 are each rotatable by means of a drive motor 136 to move the plug elements 132 in the axial direction and into the plug connection 130 or to be released from the plug connection 130. The drive motor 136 is connected by means of a drive chain 138 with the respective spindle wheel 134 to the spindle wheel 134 accordingly to rotate. Alternatively, the drive motor 136 may also be connected to the respective spindle wheel 134 by means of a gear or a drive belt.

Through this connection between the connecting rod 34 and the transmission element 18, the output connection point 28 can be selected or adjusted with little effort, wherein in each case only one of the plug elements 132 can be connected to one of the plug connections 130, wherein the others are not connected are to ensure a corresponding rotation of the connecting rod 34 about the respective Ausgangsanlenkpunkt 28. In FIG. 22, the articulation point 28 is selected or connected, whereas the articulation point 28 'is released.

In Fig. 23, another embodiment of the drive device 10 is shown schematically. The same elements are designated by the same reference numerals, in which case only the special features are explained.

In the embodiment of Fig. 23, the respective articulation points are connected to the respective connecting rods 32, 34 and respectively mounted eccentrically on a turntable to adjust the respective articulation point or the articulation position.

The input connecting rod 32 is adjustably connected to the transmission element 18 by means of a first rotary disk 150. The first turntable 150 is rotatably mounted on the transmission element 18 and has an eccentrically formed pivot point 152, which forms the Eingangsanlenkpunkt 30. By rotating the turntable 150, the position of the input coupling point 30 can thus be varied by fixing the rotary disk 150 in different rotational positions on the transmission element 118.

The connecting element 34 is articulated by means of a second rotary disk 134 on the transmission element 18 or connected to the transmission element 1 18. The second hub 154 is rotatably mounted and has an eccentric steering point 156, which forms the Ausgangsanlenkpunkt 28. The second hub 154 can be fixed in different rotational positions on the transmission element 1 18, to vary the position of the Ausgangsanlenkpunkts 28 and adjust the angle 44 of the bell crank 42 accordingly.

On the output unit 16 or the plate of the output unit 16, a third hub 158 is formed and rotatably supported. The third hub 158 has an eccentric connecting point 160, which forms the input member 20 and the input articulation point of the output unit 16. At the Exzenteranlenkpunkt 160, the connecting element 34 is mounted to transmit the power from the transmission element 18 to the output unit 16. By rotation of the third hub 158 and the determination of the third hub 158 in the different rotational positions of the pivot point on the output unit 16 can be varied and adjusted accordingly, so as to provide a further variation possibility of the angle 44 and the Ausgangskniehebels 42. The connecting element 34 has the adjusting device 68 for a further variation of the toggle lever 42.

By the three turntables 150, 154, 158 with the eccentrically mounted articulation points 30, 156, 160, the leverage ratios of the drive device 10 can be generally adjusted with a great many variations and almost infinitely.

It is understood that the embodiment of Fig. 23 may also each have only one or two of the illustrated rotary disks 150, 154, 158.

Claims

Patent claims

Drive device (10), in particular for driving a forming device (12), with: at least one drive unit (14), which provides a driving force (30) or a drive torque, an output unit (16), which has an input member (20) and a translationally movable Output member (22), the output unit (16) having a progressive force-path curve between the input member (20) and the output member (22), a transmission element (18) which is rotatably mounted at a pivot point (26), wherein the transmission element (18) is connected to the drive unit (14) in such a way that a torque (38) can be transmitted to the transmission element (18), and wherein the transmission element (18) has an output articulation point (28) at which a connecting element ( 34) is articulated, which forms a toggle lever (42) with the transmission element (18), the connecting element (34) being connected to the input member (20) of the output unit (16) in such a way that a force can be transferred to the output unit (16). , characterized in that an angle (44) of the toggle lever (42) can be changed for a starting position of the output member (22) in order to adjust the force-path curve of the output member (22).

Drive device according to claim 1 or the preamble of claim 1, characterized in that a force-path curve of the transmission element (18) can be selected in the same or opposite direction to the force-path curve of the output unit (16) in order to determine the force-path curve. Adjust the course of the output element (22).

3. Drive device according to claim 1 or 2, characterized in that the output articulation point (28) of the transmission element (18) is connected to the input member (20) of the output unit (16) and a length of the connecting element (34) is adjustable.

4. Drive device according to one of claims 1 to 3, characterized in that the pivot point (26) of the transmission element (18) is designed to be displaceable relative to the output unit (16).

5. Drive device according to one of claims 1 to 4, characterized in that an angular position of the output articulation point (28) is designed to be changeable for the starting position of the output member (22).

6. Drive device according to one of claims 1 to 4, characterized in that the output articulation point (28) is mounted on an eccentric rotary disk (154) on the transmission element (18) in order to adjust the angle (44) of the toggle lever (42).

7. Drive device according to one of claims 1 to 5, characterized in that an input articulation point (30) is formed on the transmission element (18), to which an input connecting element (32) is articulated, which with the transmission element (18) has a second toggle lever ( 46) forms.

8. Drive device according to claim 7, characterized in that the input articulation point (30) is mounted on an eccentric rotary disk (150) on the transmission element (18) in order to set an angle (48) of the second toggle lever (46).

9. Drive device according to one of claims 1 to 8, characterized in that the connecting element (34) is mounted on the output unit (16) by means of an eccentric rotary disk (158) in order to adjust the angle (44) of the toggle lever (42).

10. Drive device according to one of claims 7 to 9, characterized in that an angle between the input articulation point (30) and the output articulation point (28) is designed to be changeable.

1 1 . Drive device according to one of claims 7 to 10, characterized in that a linear adjustment device (1 19) is formed on the transmission element (18), on which the input articulation point (30) is mounted.

12. Drive device according to one of claims 1 to 1 1, characterized in that a plurality of connection points are formed on the transmission element (18), which form different positions for the input articulation point (30) and / or the output articulation point (28).

13. Drive device according to one of claims 1 to 1 1, characterized in that the transmission element (18) has two separate transmission members (70, 72) which are rotatably mounted about the pivot point (26), the input articulation point (30) and the Output articulation points (28) are each formed on one of the transmission members (70, 72), wherein the transmission members (70, 72) can be connected to one another in a rotationally fixed manner at different angles of rotation.

14. Drive device according to one of claims 1 to 13, characterized in that the drive unit (14) provides a drive torque, the drive unit (14) being connected to the transmission element (18) directly or by means of a connecting rod.

15. Drive device according to one of claims 1 to 13, characterized in that the drive unit (14) has an eccentric drive (1 18).

16. Drive device according to one of claims 1 to 13, characterized in that the drive unit (14) has a spindle drive (14).

17. Drive device according to claim 15 or 16, characterized in that the drive unit (14) is connected to the input articulation point (30) by means of a connecting unit which has at least one connecting rod (32).

18. The drive device according to claim 17, wherein the connection unit comprises a lever (50; 60; 74) connected to the input articulation point (30).

19. Drive device according to claim 18, characterized in that at least one lever arm of the lever (60; 74) is designed to be adjustable.

20. Drive device according to claim 18 or 19, characterized in that the lever (60) is designed as a one-sided lever (60).

21. Drive device according to claim 18 or 19, characterized in that the lever (74) is designed as a two-sided lever (74).

22. Drive device according to one of claims 1 to 21, characterized in that the input connecting element has at least a second rotatably mounted transmission element (102) with two articulation points (1 10, 1 12), an angle between the articulation points (1 10, 1 12 ) is changeable.

23. Drive device according to one of claims 1 to 22, characterized in that the output unit (16) has a knee joint (16).

24. Drive device according to one of claims 1 to 22, characterized in that the output unit (1 14) is formed by an eccentric (1 14).

25. Press module for a forming device (12), with a ram (24) and at least one drive device (10) for driving the ram (24) according to one of claims 1 to 24.

26. Modular press system for processing workpieces with a plurality of press modules according to claim 25.