EP2911871B1 - Drive apparatus - Google Patents

Description

The present invention relates to a drive device, in particular for driving a forming device, with a drive unit that provides a driving force or a drive torque, an output unit having an input member and a translationally movable output member, wherein the output unit has a progressive force-displacement curve between the Input member and the output member having, and with 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 a Ausgangsanlenkpunkt to 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 such that a force on the output unit is transferable.

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 these 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 drives 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, the control of the force-displacement curve of the tool is affected, and the force is applied with low 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 requirement and a 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 coupling. In general, the investment costs of conventional mechanical systems are high and offer only limited variation in terms of processing as they are limited to a progressive force-displacement curve.

The introduction of servo drives in the machining of workpieces allows the forming processes to be controlled over a very wide range, both in hydraulic and in mechanical drives. 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 moments and thus peaks in the electrical power requirement of the drives, thereby consuming energy storage is 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 or gear stage is driven, for example, is known from the DE 10 2005 038 583 A1 ,

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

The publication DE 20 2006 004 470 U1 shows a press-hardening press with a frame which comprises a press table and is mounted with a vertically movable plunger by means of a knee-joint mechanism to the press frame and vertically movable.

The publication FR 2486 451 A1 shows a further press arrangement according to the preamble of claim 1,

It is therefore the object of the present invention to provide a drive device, in particular for driving a forming device, which can be used more flexibly for different machining operations and is inexpensive, both in production and in operational use due to low energy consumption.

Therefore, according to claim 1 and a first aspect of the invention, a drive device is provided, comprising a drive device, in particular for driving a forming device, comprising: at least one drive unit, which provides a drive force or a drive torque, an output unit comprising an input member and a translationally movable output member wherein the output unit has a progressive force-displacement profile between the input member and the output member, 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 input coupling point and an output coupling point, wherein at the Ausgangsanlenkpunkt a connecting element is articulated, which forms a toggle lever with the transmission element wherein the connecting element with the Input member of the output unit is connected such that a force on the output unit is transferable, wherein an angle of the toggle lever is interchangeable for an initial position of the output member to adjust the force-displacement curve of the output member, wherein the transmission element has two separate transmission members, the order the pivot point are rotatably mounted, 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.

In one embodiment of the drive device, a force-displacement curve of the transmission element can be selected in the same direction or in opposite directions to the force-displacement curve of the output unit in order to set the force-displacement curve of the output element.

Furthermore, the above object according to a second aspect is achieved by a press module for a forming device with a translationally movable plunger and with at least one drive device for driving the plunger according to the first 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 second 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-displacement curves can be provided. This is achieved in that at different angles of the toggle lever different leverage and thus different power transmission of the toggle lever can be adjusted. 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 one embodiment of the present invention, the force-displacement profile of the transmission element can be selected in the same direction or in opposite directions to the force-displacement curve of the output unit, by adding the force-displacement characteristics of the transmission element and the output unit, an almost arbitrary force can be achieved. Path-course of the output element can be adjusted.

It is provided that 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.

Furthermore, 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.

Overall, the drive device according to the first aspect thus can be used for different processing or forming steps, 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 Ausgangslenkpunkt 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 pivot point 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 set a lever of the transfer member Uber the working 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 Ausgangsanlenkpunkts 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 the angle of Adjust knee 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 the second knee lift! adjust. 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.

Thereby, 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 knee 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.

Thereby, the angle of the toggle lever can be adjusted with little effort, whereby the flexibility in the adjustment of the Kraftwegverlaufes the output member can be further increased.

In a particular embodiment, the Ausgangsanlenkpunkt the transmission element, the Eingangsanlenkpunkt the transmission element and the connecting element on the output unit each supported by 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 entrance center point and the exit connection point is designed to be exchangeable or adjustable.

As a result, further force-displacement characteristics 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 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.

Thereby, 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 precisely to the transmission element.

It is further preferred if the drive unit is connected to the input connection point by means of a connection unit which has at least one connecting rod.

As a result, with little technical effort, the power can be transmitted from the drive unit to the transmission element, whereby the second toggle lever can be realized at the same time with a technically low outlay.

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

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 designed to be adjustable.

As a result, it is possible to set the maximum force provided by the output member 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 into the input connection point during the stroke can be varied 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 exchangeable.

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 little technical 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 characteristics 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 below can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention.

Fig. 1

eine schematische Darstellung einer Antriebsvorrichtung zum Antreiben einer Umformvorrichtung;

Fig. 2a bis d

eine schematische Darstellung einer Ausführungsform der Antriebsvorrichtung in unterschiedlichen Positionen und einem entsprechenden progressiven Kraft-Weg-Verlauf;

Fig. 3a bis d

die Ausführungsform der Antriebsvorrichtung aus Fig. 2a bis d mit alternativem Übertragungselement und eine zugehörige flache Kraft-Weg-Kennlinie;

Fig. 4a bis d

eine weitere Ausführungsform der Antriebsvorrichtung mit versetzbarem Übertragungselement und verschiedenen Eingangsanlenkpunkten und zugehörige Kraft-Weg-Kennlinien;

Fig. 5a bis d

eine weitere Ausführungsform der Antriebsvorrichtung mit Dreieckshebel und zugehörige Kraft-Weg-Kennlinien;

Fig. 6a bis d

eine weitere Ausführungsform der Antriebsvorrichtung mit variablem Eingangshebel und zugehörige Kraft-Weg-Kennlinien;

Fig. 7a bis d

eine Einstellung der Antriebsvorrichtung aus Fig. 6a bis c mit verkürztem Hub zugunsten hoher Kraft und eine zugehörige Kraft-Weg-Kennlinie;

Fig. 8

eine besondere Ausführungsform der Antriebsvorrichtung mit längenverstellbarer Ausgangspleuelstange;

Fig. 9

eine Ausführungsform der Antriebsvorrichtung mit zweiseitigem Eingangshebel mit variablem Hebelarm und festem Widerlager sowie zwei separaten scheibenförmigen Übertragungsgliedern;

Fig. 10

eine Ausführungsform der Antriebsvorrichtung mit zweiseitigem Eingangshebel und variablem Widerlager;

Fig. 11

eine Ausführungsform der Antriebsvorrichtung mit zweiseitigem Eingangshebel mit variablem Hebelarm und festem Widerlager;

Fig. 12

eine Ausführungsform der Antriebsvorrichtung mit einem Dreieckshebel als Eingangshebel und oberem Lagerpunkt;

Fig. 13

eine Ausführungsform der Antriebsvorrichtung mit Dreieckshebel und unterem Lagerpunkt;

Fig. 14a, b

eine detaillierte Darstellung einer konstruktiven Ausführungsform der Antriebsvorrichtung mit stufenloser Verstellung in der Einstellung eines progressiven Kraft-Weg-Verlaufs;

Fig. 15a, b

eine detaillierte Darstellung der Antriebsvorrichtung aus Fig. 14a, b; in der Einstellung eines konstanten Kraft-Weg-Verlaufs;

Fig. 16a bis g

Ausführungsformen der Antriebsvorrichtung mit zwei drehbar gelagerten Übertragungselementen bzw. mit einer Scheibe als Eingangsglied der Abtriebseinheit;

Fig. 17

eine Ausführungsform der Antriebsvorrichtung mit einem Exzenter als Abtriebseinheit;

Fig. 18

eine Ausführungsform der Antriebsvorrichtung mit Exzenter als Antriebseinheit;

Fig. 19

eine Ausführungsform der Antriebsvorrichtung mit direktem Momentantrieb;

Fig. 20

eine Ausführungsform der Antriebsvorrichtung mit einem Momentenmotor, der über eine Pleuelstange mit der Übertragungseinheit verbunden ist;

Fig. 21

Kraft-Weg-Verläufe von unterschiedlichen Einstellungen der Antriebsvorrichtung;

Fig. 22

eine detaillierte Darstellung des einstellbaren Übertragungselements aus Figur 16f und g; und

Figur 23

eine Ausführungsform der Antriebsvorrichtung mit exzentrisch drehbar gelagerten Anlenkpunkten.

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

Fig. 1

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 Fig. 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 Fig. 6a to c with shortened stroke in favor of high force and an associated force-displacement characteristic;

Fig. 8

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

Fig. 9

an embodiment of the drive device with two-sided input lever with variable lever arm and fixed abutment and two separate disc-shaped transmission members;

Fig. 10

an embodiment of the drive device with two-sided input lever and variable abutment;

Fig. 11

an embodiment of the drive device with two-sided input lever with variable lever arm and fixed abutment;

Fig. 12

an embodiment of the drive device with a triangular lever as an input lever and upper bearing point;

Fig. 13

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 view of the drive device 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

An embodiment of the drive device with an eccentric as the output unit;

Fig. 18

an embodiment of the drive device with eccentric drive unit;

Fig. 19

an embodiment of the drive device with direct torque drive;

Fig. 20

an embodiment of the drive device with a torque motor which is connected via a connecting rod to the transmission unit;

Fig. 21

Force-displacement curves of different settings of the drive device;

Fig. 22

a detailed view of the adjustable transmission element FIG. 16f and G; and

FIG. 23

an embodiment of the drive device with eccentrically rotatably mounted pivot 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 designed as a spindle drive 14 and transmits a force to the input connection point 30 via the input connection element 32, which in this particular embodiment is designed as a connecting rod the power 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 link 34, which is articulated at the Ausgangsanlenkpunkt 28, forms, together with the rotatably mounted at the pivot point 26 transmission element 18 is a Ausgangsskniehebel 42 having a characteristic force-displacement curve. 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 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 lever) that drops over the power stroke and at an angle 44 of about 90 ° with a small Value ends. 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. This results in a highly progressive, at the end of the working stroke extremely increasing force-displacement 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, 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 device 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 triangular 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 Figures 2a to c and the different positions of the FIGS. 2a to c are in the diagram in Fig. 2d marked accordingly with S1, S2 and S3.

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

FIGS. 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 the FIGS. 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.

The transmission element 18 is formed in this embodiment as a one-piece rigid element in which the Eingangsanlenkpunkt 30, the Ausgangsanlenkpunkt 28 and the pivot point 26 form an angle of about 190 °. In the in Fig. 3a illustrated starting position of the power stroke, which is denoted by S1, the angle 44 of the Ausgangsskniehebels 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 working stroke, which is in Fig. 3b is denoted by S2 and 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 is transmitted from the transmission element 18. This force-way course in the FIGS. 3a to c illustrated transmission element 18 is formed approximately in opposite directions 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 curve of the output member 22 results. This force-displacement curve is for the three positions of the working stroke S1, S2, S3 in FIG Fig. 3d shown.

The in the FIGS. 2a to c and 3a to c illustrated transmission elements 18 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 can be done only by replacing the transmission element 18.

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

The transmission element 18 is designed 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 FIGS. 4a to c each two different connection or storage options of the transmission element 18 are 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 connection point 30 and the output connection point 28 are arranged at an angle of approximately 190 ° relative to the pivot point 26, so that in the in Fig. 4a illustrated starting position of the working stroke S1 of the angle 44 of the output Ziehhebel 42 is about 90 ° and the angle 48 of the input Ziehhebel 46 has an obtuse angle of about 120 °.

In the second connection variant (shown in dashed lines), the transmission element 18 is mounted rotatably offset 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 in Fig. 4a illustrated starting position of the working stroke S1 of the angle 44 'of the Ausgangskniehebels 42' is an acute angle of about 30 ° and the angle 48 'of the Eingangsskniehebels 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 special adjustment of the angle 44, 48 over in the FIGS. 4a to c shown working stroke positions S1, S2, S3, the transmission element 18 in the first installation variant on a progressive force-displacement curve, so that as a result of the total force-displacement curve of the output member 22, the in Fig. 4d is shown, 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 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 Fig. 4d is shown.

Due to the particular embodiment of the in the FIGS. 4a to c illustrated transmission element 18 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 profiles of the output member 22 are adjustable.

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

In the FIGS. 5a to c a first variant is shown in solid lines, in which the drive unit 14 is connected to a one-sided triangle lever 50 in order to transmit the introduced force 36 to the Eingangsanlenkpunkt 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.

In the Fi Guren 5a to c is a second connection variant without the triangle lever 50 shown with dashed lines, which essentially the second connection variant of the FIGS. 4a to c equivalent.

By virtue of the triangular lever 50, the action of the input force 36 in addition to the variation in the force acting angle 48 is further modified by the relative difference between the resultant lever arms of the force direction 36 and the connecting rod between the pivot points 56 and 30 relative to the fulcrum 52 the working stroke position S1, the lever arm of the driving force 36 with respect to the fulcrum 52 is greater than the resultant lever arm of the Verbindungspleuels. 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 he in Fig. 5d is shown by a solid line. In comparison, the connection variant without the triangular lever 50 has a linearly increasing force-displacement curve over the same working stroke, as it likewise (as a dashed line) in FIG Fig. 5d is shown.

In the FIGS. 6a to c is a further variant of the drive device 10 is shown schematically. 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.

In the FIGS. 6a to c two variants of the connection of the one-sided lever 60 are shown, wherein a variant with a small lever is shown by 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 a Ausgangsanlenkpunkt 64, which forms a fixed lever to the bearing point 62 and further has an Eingangsanlenkpunkt 66 which is connected to the drive unit 14, wherein the Eingangsanlenkpunkt 66 variable or slidably is formed so that the lever of the Eingangsanlenkpunkts 66 can be varied relative to the bearing point 62.

In Fig. 6d are two force-displacement curves of the two connection variants from the FIGS. 6a to c for the different working stroke positions S1, S2, S3, wherein the variant with small lever of the one-sided lever 60 is shown in a solid line and the second variant with a large lever of the one-sided lever 60 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, as shown in FIG Fig. 6d is shown, 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.

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

Due to the offset 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 interaction with the in Fig. 1 already described 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 based on the Fig.3 ad described, but at a higher level of strength, at the expense of a shorter working stroke. By the one-sided lever 60, the basic translation of the introduction of force in the Eingangsanlenkpunkt 30 in the transmission element 18, as already described Fig. 6 ad described, varied and the total strength is thus reinforced again. In the result can be set by a high power over a shortened stroke S, as in Fig. 7d is shown.

Fig. 8 shows a further embodiment of the drive device 10 with a length-adjustable output connector 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 remain fixed in this embodiment. A first variant with a short connecting element is in Fig. 8 shown with solid lines, whereas a second variant with 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 in Fig. 8 illustrated input connection point 30 is formed in the outer terminal position, wherein the length adjustment member 68 is shortened such that the angle 44 in the in Fig. 8 illustrated Ausgangsarbeithubposition is about 90 ° and by 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 the representation in Fig. 2d equivalent.

In the in Fig. 8 illustrated second connection variant of the input coupling point 30 'is articulated to the interior of the connection points, so that between the two points 28, 30' an angle of approximately 30 ° is formed. The length adjustment element 68 is extended so that in the in Fig. 8 illustrated starting position of the working stroke position of 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 the representation in Fig. 3d equivalent. 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 connection 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 connectable to different angular positions of the Eingangsanlenkpunktes 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 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 Ausgangskniehebels 42 can be adjusted by simple means. 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.

In Fig. 10 is a variant of the drive device 10 from Fig. 9 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 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. Due to the particular embodiment of the two-sided lever 74 can also be as in the embodiment according to Figure 9 set different forces on the output member 22.

In Fig. 11 is another variant of the drive device 10 from Fig. 9 shown schematically. The same elements are designated by the same reference numerals, in which case only the special features are executed.

At the in Fig. 11 illustrated variant, the drive unit 14 is arranged laterally adjacent to the transmission element 18 and connected via the sliding articulation point 76 with the two-sided lever 74. 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 is 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.

In Fig. 13 is a variant of the drive device 10 from Fig. 12 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. 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.

In the FIGS. 14a and b is a detailed embodiment of the drive device 10 with a variable one-sided lever 60 and a variable transmission element 18 shown schematically 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 is shown an initial position of the working stroke, in which the angle 44 is about 90 ° and in Fig. 14b an end position of the power stroke is shown schematically, in which the angle 44 of the Ausgangskniehebels is about 130 °. This results in a progressive force-displacement curve.

In the FIGS. 15a and b is the detailed embodiment of the FIGS. 14a and b shown in an alternative setting with respect to the relative angular position of the Eingangsanlenkpunkts 30 and the Ausgangsanlenkpunkts 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 in the FIGS. 15a and b 1, the input member 70 and the output member 72 of the transmission element 18 are set at a different angular position to each other, so that a larger angle of about 270 ° between the Eingangsanlenkpunkt 30 and the Ausgangsanlenkpunkt 28 is realized relative to the pivot point 26. Further, the pivot point 26 is relative to the setting of the FIGS. 14a, b offset to the output unit 16, so that a smaller angle 44 of the Ausgangsskniehebels 42 in the starting position Fig. 15a is set. This results in an approximately constant force-displacement curve of the output member 22. In Fig. 15b is an end position of the working stroke for the setting Fig. 15a shown.

In general, the three setting possibilities of the embodiment are sufficient Fig. 14 and 15 or by the three degrees of freedom of the drive device 10 from the Figures 14 and 15 set a variety of different force-displacement paths of the output member 22, which generally improves the possibility of variation of the drive device 10 and is automatable.

In Fig. 16a a further 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 coupling point 110 is formed on the input element 104, and an output connection point 112 is formed on the output element 106. The input member 104 and the output member 106 are rotatably formed with each other and rotatably connected to each other to adjust different angular positions of the Eingangsanlenkpunkts 110 and the Ausgangsanlenkpunkts 112 relative to each other. The input linkage point 110 is connectable to the two-way lever 74 to transmit the power from the drive unit 14 to the transfer element 102. The Ausgangsanlenkpunkt 112 is connected by a connecting rod with the pivot 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.

In Fig. 16b is a variant of the embodiment of Fig. 16a shown. The same elements are designated by the same reference numerals, in which case only the special features are explained.

The length adjustment element 68 is set in this embodiment such that the articulation 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.

In Fig. 16c is another embodiment of the drive device 10 from Fig. 16a illustrated in which the output unit 16 has a plurality of different pivot points to allow 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 113 ', 113 ", 113"', 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 a further 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.

Characterized 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 112 is moved upward, as by a Arrow 115 is indicated. 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 a further 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 off Fig. 16e is opposite to the embodiment Fig. 16d two output units 16, 16 ', which are formed by two parallel toggle lever and are connected to each other by means of a connecting rod 117. The connecting rod 117 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 Eingangsanlenkpunkt 30 is mounted by means of a linear adjustment 119 on the transmission element 18 linearly adjustable at different distances to the pivot point 26 to the lever of the corresponding Eingangskniehebels 46. The transfer element 18 has different output linkage points 28, 28 ', 28 "to articulate the link 34 on the transfer element 18 in different positions and adjust the angle of the corresponding bellcrank 42. The link 34 has different points of attachment to different lengths For this purpose, the connecting element 34 may alternatively or additionally have the length adjustment element 68. The mode of operation of the mounting of the connecting element 34 at the output connection points 28, 28 ', 28 "is explained in more detail below.

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

The connecting element 34 in this case has different connection points to the connecting element 34 at the various Ausgangsanlenkpunkten 28, 28 ', 28 "and a plurality of connection points or bearing points in order to fix the connecting element 34 to the input member of the output unit 16. Die Verbindungspunkte bzw. 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. As a result, a plurality of variations of the Adjusting the angle 44 of the bell crank 42 possible.

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

In Fig. 17 is a variant of the drive device 10 from Fig. 9 shown schematically 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 114, which forms the output unit of the drive device 10.

The eccentric 114 has the input member 20 which is rotatably mounted eccentrically about a pivot point 116 and the output member 22 moves according to 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 118, which forms the drive unit. The eccentric 118 is mounted eccentrically about a pivot point 120 and is driven with a torque by a drive unit, so that a force can be transmitted to the transmission element 18 by means of the input connection element 32. 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 118 is connected directly to the input element 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 118 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 element 18 is formed in this embodiment as a simple lever, which is driven in a circular manner 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 in Fig. 19 However, the engine is not uniformly utilized in contrast to the previously presented versions on the stroke course and must be designed for a high torque peak, so be oversized.

In Fig. 20 a further 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 peaks in the momentary demand compared to in Fig. 19 described embodiment avoided and the engine can therefore be made smaller.

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

It becomes clear that the settings allow both short working strokes with high forces and large working strokes with constant high or low forces to be set. 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 execution according to 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 connecting points 28, 28 'by means of plug connections in order to steer 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, it being possible for only one of the plug elements 132 to be connected to one of the plug connections 130 at a time, the others not being connected to each other a corresponding rotation of the connecting rod 34 to ensure the respective Ausgangsanlenkpunkt 28. In Fig. 22 is the pivot point 28 selected or connected, whereas the pivot point 28 'is solved.

In Fig. 23 a further 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 rod 32, 34 and each mounted eccentrically on a turntable to adjust the respective articulation point or the articulation position.

The input connecting rod 32 is articulated by means of a first hub 150 adjustable on the transmission element 18. 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 118. The second hub 154 is rotatably mounted and has an eccentric pivot point 156, which forms the Ausgangsanlenkpunkt 28. The second rotary disk 154 can be fixed to the transmission element 118 in different rotational positions, to vary the position of the Ausgangsanlenkpunkts 28 and adjust the angle 44 of the bell crank 42 accordingly.

On the output unit 16 and the plate of the output unit 16, a third hub 158 is formed and rotatably supported. The third rotary disk 158 has an eccentric connecting point 160 which forms the input member 20 or the input connecting 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 possible variations and almost infinitely.

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

Claims (15)

1. Drive apparatus (10), in particular for driving a forming apparatus (12), having:

   - at least one drive unit (14) which provides a drive force (30) or a drive moment,

   - an output unit (16) which has an input member (20) and an output member (22) which can be moved translationally, the output unit (16) having a progressive force-path curve between the input element (20) and the output element (22),

   - a transmission element (18) which is mounted rotatably at a pivot point (26), the transmission element (18) being connected to the drive unit (14) in such a way that a torque (38) can be transmitted to the transmission element (18), and the transmission element (18) having an input articulation point (30) and an output articulation point (28), a connecting element (34) being articulated on the output articulation point (28), which connecting element (34) forms a knee 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 transmitted to the output unit (16), it being possible for an angle (44) of the knee lever (42) to be changed for a starting position of the output member (22), in order to set the force-path curve of the output member (22),

   characterized in that the transmission element (18) has two separate transmission members (70, 72) which are mounted such that they can be rotated about the pivot point (26), the input articulation point (30) and the output articulation point (28) being configured in each case on one of the transmission members (70, 72), it being possible for the transmission members (70, 72) to be connected fixedly to one another so as to rotate together at different rotary angles.
2. Drive apparatus according to Claim 1, characterized in that a force-path curve of the transmission element (18) can be selected so as to run in the same direction as or in the opposite direction to the force-path curve of the output unit (16), in order to set the force-path curve of the output member (22).
3. Drive apparatus 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) can be set.
4. Drive apparatus according to one of Claims 1 to 3, characterized in that the pivot point (26) of the transmission element (18) is configured such that it can be moved relative to the output unit (16).
5. Drive apparatus according to one of Claims 1 to 4, characterized in that the output articulation point (28) is mounted on an eccentric rotary disc (154) on the transmission element (18), in order to set the angle (44) of the knee lever (42).
6. Drive apparatus according to one of Claims 1 to 5, characterized in that an input connecting element is articulated at the input articulation point (30), which input connecting element (32) forms a second knee lever (46) with the transmission element (18).
7. Drive apparatus according to one of Claims 1 to 6, characterized in that the connecting element (34) is mounted on the output unit (16) by means of an eccentric rotary disc (158), in order to set the angle (44) of the knee lever (42).
8. Drive apparatus according to one of Claims 1 to 7, characterized in that the drive unit (14) provides a drive moment, the drive unit (14) being connected to the transmission element (18) directly or by means of a connecting rod.
9. Drive apparatus according to one of Claims 1 to 7, characterized in that the drive unit (14) has an eccentric drive (118).
10. Drive apparatus according to one of Claims 1 to 7, characterized in that the drive unit (14) has a spindle drive (14).
11. Drive apparatus according to one of Claims 1 to 10, characterized in that the input connecting element has at least one second rotatably mounted transmission element (102) with two articulation points (110, 112), it being possible for an angle between the articulation points (110, 112) to be changed.
12. Drive apparatus according to one of Claims 1 to 11, characterized in that the output unit (16) has a knee joint (16).
13. Drive apparatus according to one of Claims 1 to 12, characterized in that the output unit (114) is formed by an eccentric (114).
14. Press module for a forming apparatus (12), having a plunger (24) and at least one driving apparatus (10) for driving the plunger (24) according to one of Claims 1 to 13.
15. Modular press system for processing workpieces having a plurality of press modules according to Claim 14.

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