JP2015533656A - Drive device - Google Patents

Abstract

The present invention comprises a drive unit (14) providing a drive force (30), an input member (20) and a translationally movable output member (22), and progressively between the input member and the output member. A driven unit (16) having typical force / stroke characteristics and a transmission element (18) rotatably supported at a fulcrum (26), the transmission element having a torque Is connected to the drive unit so as to be able to transmit (38) and has an output pivot point (28), which forms a toggle lever (42) with the transmission element. A connecting element (34) is pivotally connected to the input member of the driven unit so that force can be transmitted to the driven unit, and the force / stroke characteristic line of the output member. To set the output member's Is changeable angle of the toggle lever (44) is in connection with the originating location, a driving device for in particular driving the deforming device.

Description

  The present invention is a driven unit having at least one driving unit that provides a driving force or a driving moment, an input member, and a translationally movable output member, and is provided between the input member and the output member. A driven unit having a progressive force / stroke characteristic line and a transmission element rotatably supported by a fulcrum. The transmission element can transmit torque to the transmission element. Is connected to the drive unit and has an output pivot point, and the output pivot point is pivotally connected to a connection element that forms a toggle lever together with the transmission element, The connecting element is connected to the input member of the driven unit so as to be able to transmit a force to the driven unit. Apparatus on.

  This type of drive is used to provide a defined force / stroke characteristic line to the output member, for example, to drive or operate a press or punching machine.

  For the machining of workpieces, different force / stroke characteristic lines are required with respect to the tool movement sequence for different machining steps, for example deep drawing, embossing, cutting / punching. In this case, a pure drawing process usually requires a nearly constant force characteristic line over a long stroke, while embossing or coining requires a high force peak with an extremely progressive characteristic line. It is. In contrast, the cutting process requires a high force in a short stroke range, which is rather accompanied by a reverse characteristic line.

  Different drive concepts of the press are usually used for different processing types and different requirements on deformation technology.

  For the drawing process, a hydraulic drive is preferably used, since a substantially constant force characteristic line is provided for a relatively long stroke distance by the hydraulic drive. In the hydraulic drive device, various speed courses can be well adjusted by flow control, and a switching point between the high speed stroke and the work stroke can be arbitrarily selected.

  A disadvantage of hydraulic drives is the compressibility of hydraulic oil such that the compression is in the relatively high single percent range under the required system pressure. Such a compression rate generates high heat, which adversely affects the energy balance of the hydraulic method. Further, the control of the force / stroke characteristic line of the tool is impaired by the compressibility of the hydraulic oil, and the action of the force is performed with a slight rigidity. Thus, for example, the coining process can be performed only with an excessively large force because hard rolling is difficult due to a soft force action. At the end of the punching process, the spring energy largely stored by the compression rate is suddenly released. The cutting impact caused by this generates a loud noise.

  Mechanical drive systems in the form of eccentrics, cams and toggle joints usually have low energy requirements and high rigidity. However, in this case, in a drive device equipped with a conventional continuously operating electric motor, the possibility of change in the process progress is limited, and the additional work that requires time and effort increases the work process, the tool installation height. Now, the tool speed can only be changed within a small range. Furthermore, control during the work process is not possible. Mechanical drive devices have progressive force / stroke characteristic lines, which are very prominent in toggle lever drive devices. For this reason, such a drive device can only be used conditionally, for example, for a drawing process with a long working stroke.

  In mechanical drive systems, mechanical flywheels are usually used to limit the moment of the motor and level the force, which further increases the technical effort, for example with a switchable clutch. Generally, the capital investment cost of a conventional mechanical system is high, and it is limited to a progressive force / stroke characteristic line.

  With the introduction of a servo drive device during workpiece processing, the deformation process can be controlled over a very wide range, both in the case of a hydraulic drive device and in the case of a mechanical drive device. In order to avoid the disadvantages of the hydraulic drive, for example, a controllable servo motor is connected to a roller spindle that is directly integrated into the main power transmission path. In this case, however, the drive system must be designed for maximum force peaks and the stroke speed is limited to the maximum speed possible with a spindle well below the processing speed in the hydraulic cylinder.

  Alternatively, the servomotor can be directly connected to the drive shaft of the eccentric or toggle lever with extremely high torque without a spindle or transmission stage. As a result, an extreme peak occurs in the moment characteristic line, and a peak also occurs in the electrical required output of the drive device. This requires laborious energy storage, which increases the technical effort of the entire system in the form of a capacitor or a separate flywheel that is fed. Eventually, the entire system must be designed correspondingly to absolute moment peaks or force peaks, which is expected to make the technical effort significantly higher than is actually technically necessary.

  A drive device for a press machine in which a drive shaft having no spindle or transmission stage is driven is disclosed, for example, in DE 102 2005 38583.

  A disadvantage of the known drive devices is that they are technically laborious and / or are defined according to the force / stroke characteristic lines that are limited by the system, depending on the drive technology.

  The object of the present invention is to drive a drive device, in particular a deformation processing device, which can be used flexibly in accordance with various processing steps and is inexpensive due to low energy consumption in both production and operational use. It is providing the drive device for.

  In the drive device of the type described at the outset, according to the first solution, a toggle lever is associated with the starting position of the output member in order to set the force / stroke characteristic line of the output member. This is solved by the fact that the angle can be changed.

  In the drive device of the type described at the beginning, according to the second solution of the present invention, the problem is that the force / stroke characteristic of the transmission element is set in order to set the force / stroke characteristic line of the output member. This is solved by selecting the line in the same direction or in the opposite direction with respect to the force / stroke characteristic line of the driven unit.

  Furthermore, according to the third solution, the above-mentioned problem is achieved by a slide that can move in translation, by the first solution or the second solution for driving the slide, or by an embodiment of the invention. This is solved by a press module for a deformation processing device provided with at least one driving device according to the above.

  Finally, the above-mentioned problem is solved by a modular press system for machining a workpiece having a plurality of press modules according to the third means of solving the present invention.

  According to the first solution of the present invention, the angle of the toggle lever connected to the output member having the progressive force / stroke characteristic line is adjustable, so that the force / stroke characteristic line of the transmission element is adjusted. Since the output member can be variably adjusted, various force / stroke characteristic lines can be provided to the output member. This is obtained by adjusting various lever actions at various angles of the toggle lever, thereby adjusting the transmission of various forces of the toggle lever. By combining the transmission element with the driven unit, the force / stroke characteristic lines of both elements are superimposed, whereby almost arbitrary force / stroke characteristic lines can be set in the output member.

  In the second solution of the present invention, the force / stroke characteristic line of the transmission element can be selected in the same direction or the reverse direction with respect to the force / stroke characteristic line of the driven unit. By adding the force / stroke characteristic lines, almost arbitrary force / stroke characteristic lines of the output member can be set.

  Overall, therefore, both solutions of the present invention allow the drive to be used for various machining or deformation steps, which allows the drive to be used flexibly. This completely solves the problem of the present invention.

  In a preferred embodiment, the output pivot point of the connection element is connected to the input member of the specific drive member and the length of the connection element or the distance between the output pivot point and the input member is adjustable. .

  As a result, the angle of the toggle lever, and hence the lever of the toggle lever, can be adjusted with little effort with respect to the working stroke, whereby the force / stroke characteristic line of the transmission element can be set with little effort.

  It is further preferable that the fulcrum of the transmission element is formed so as to be able to be shifted relative to the driven unit.

  This changes the angle of the toggle lever, so that the lever of the transmission member can be adjusted with respect to the working stroke, and at the same time, the transmission member and the connecting element can be manufactured with little technical effort.

  More preferably, the angular position of the output pivot point can be changed in relation to the starting position of the output member.

  As a result, the angle of the toggle lever can be selectively adjusted, whereby various force / stroke characteristic lines of the transmission element can be set.

  In order to adjust the angle of the toggle lever, it is further preferred if the output pivot point is supported by an eccentric rotating disk of the transmission element. In this case, the eccentric rotating disk can preferably be fixed to the transmission element at various rotational positions.

  As a result, the angle can be adjusted with a little effort with a high degree of freedom.

  In order to adjust the second toggle lever, it is further preferred if the input pivot point is supported on an eccentric disk of the transmission element. In this case, in order to adjust the angle of the second toggle lever, the eccentric rotating disk can be fixed to the transmission element, preferably at various rotational positions.

  As a result, the angle of the second toggle lever can be adjusted steplessly, whereby the change of the force / stroke characteristic line of the output member is flexible and can be adjusted with little effort.

  In order to adjust the angle of the toggle lever, it is further preferred that the connecting element is supported on the driven unit via an eccentric rotating disk. In this case, in order to realize various support positions, the eccentric rotating disk can be preferably fixed to the driven unit at various rotational positions.

  As a result, the angle of the toggle lever can be adjusted with little effort, and the flexibility in setting the force / stroke characteristic line of the output member can be greatly increased.

  In a special embodiment, the output pivot point of the transmission element, the input pivot point of the transmission element, and the connecting element in the driven unit are each supported by an eccentric rotating disk, so that in general the force / stroke of the drive device. The characteristic line can be variably set in many ways.

  It is further preferred if an input pivot point is formed on the transmission element, and an input connection element that forms a second toggle lever with the transmission element is pivoted on the input pivot point. .

  Thereby, a large torque can be transmitted to the transmission element with a little technical effort.

  It is further preferred if the angle between the input pivot point and the output pivot point is configured to be changeable or adjustable.

  Thereby, another force / stroke characteristic line of the transmission member is set, and as a whole, the variability of the force / stroke characteristic line of the output member is enhanced.

  It is further preferred if a linear adjustment device is formed on the transmission element and the input pivot point is supported on the linear adjustment device. As a result, the lever of the second toggle lever can be easily adjusted, whereby the force / stroke characteristic line of the driving device can be further changed.

  It is further preferred if the transmission element is formed with a plurality of connection points which form different positions for the input pivot point and / or the output pivot point.

  Thereby, the angle of the first toggle lever and the second toggle lever can be changed simply by shifting the input connection element and / or the connection element, and thus a troublesome adjustment mechanism can be omitted, The transmission member can be manufactured with little technical effort.

  The transmission element has two separate transmission members that are rotatably supported around the fulcrum, and the input pivot point and the output pivot point are respectively the two transmission members. It is further preferable if the two transmission members can be coupled to each other at various rotation angles so as not to rotate.

  Thereby, both the transmission members can be easily rotated relative to each other and can be connected to each other at various rotation angles, so that the angle of the second toggle lever can be adjusted with little effort. This generally makes handling of the transmission element easier and the adjustment of the angle of the toggle lever is easier.

  It is further preferred if the drive unit provides a drive moment and the drive unit is connected to the transmission element directly or via a connecting rod.

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

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

  Thereby, a drive device can be driven by the electric motor which operates continuously.

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

  Thereby, a large force can be accurately transmitted to the transmission element.

  It is further preferred if the drive unit is connected to the input pivot point by a connection unit having at least one connecting rod.

  Thus, the force from the drive unit can be transmitted to the transmission element with a little technical effort, and in this case, the second toggle lever can be formed with a little technical effort at the same time.

  More preferably, the connection unit has a lever connected to the input pivot point.

  As a result, an accurate force can be applied to the transmission element with little technical effort.

  It is further preferred if the lever arm of the lever is formed to be adjustable.

  This makes it possible to adjust the maximum force provided by the output member with little technical effort.

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

  This allows the lever arm and hence the transmission of force to be changed without changing the direction of movement of the input pivot point.

  It is optionally preferred if the lever is formed as a double-sided lever.

  Thereby, the movement direction of the input pivot point, and hence the movement direction of the output member can be changed.

  It is further preferred if the lever is formed as a triangular lever, which has two pivot points and one supporting point which together form a triangle.

  This makes it possible to change the ratio of the drive force to the force applied to the input pivot point during the stroke by means of technically simple means, thereby making the force / stroke characteristic line additionally variable. Can be made particularly uniform.

  It is further preferred if the connecting unit has a second transmission element rotatably supported with two pivot points, and the angle between the two pivot points can be changed. It is.

  Thereby, the force / stroke characteristic line of the output member can be set more precisely.

  More preferably, the driven unit has a toggle joint.

  As a result, an accurate and direct force can be transmitted to the output member with little technical effort.

  It is selectively preferable if the driven unit is formed by an eccentric body.

  As a result, the driven unit can be realized in a compact configuration form with little technical effort.

  In general, the various alternations of the drive can set various force / stroke characteristic lines of the output member, which makes the variability of the drive as a whole especially for the various work steps. Can be used for deformation processing. In this case, the various large forces can be adjusted so that they rise constantly or linearly over the working stroke, but progressively, i.e. with an exponential force characteristic line over the working stroke. The force or torque provided by the drive unit is constant throughout the course of the stroke, despite the various characteristic lines, and no output peak occurs. The various force and stroke characteristic lines can be set only by mechanical adjustment of the drive, so that they can be changed by a relatively small and energy efficient drive unit. The advantages of direct force action with high rigidity and conservative energy use of the drive and mechanical force transmission can be exploited.

  Thus, the drive can be used for various processing methods, in which case the advantages of various force transmissions are utilized.

  It will be appreciated that the features described above and those described below can be used not only in the respective combinations described, but also in other combinations or alone without departing from the scope of the invention.

  Embodiments of the invention are illustrated and described in detail below.

It is a figure which shows schematically the drive device which drives a deformation | transformation processing apparatus. It is a figure which shows one embodiment of a drive device roughly. Fig. 2b shows the drive device of Fig. 2a in different positions. Fig. 2b shows the drive device of Fig. 2a in a further different position. It is a figure which shows the progressive force and stroke characteristic line which the drive device of FIGS. 2a-2c has. Fig. 2b shows the drive device of Fig. 2a with an optional transmission element. Fig. 2b shows the drive device of Fig. 2b with selective transmission elements. Fig. 2b shows the drive device of Fig. 2c with selective transmission elements. FIG. 4 is a diagram showing a flat force / stroke characteristic line belonging to the drive device of FIGS. FIG. 6 shows another embodiment of a drive device with transmission elements that can be displaced and various input pivot points. Fig. 4b shows the drive device of Fig. 4a in different positions. Fig. 4b shows the drive device of Fig. 4a in a further different position. FIG. 4 is a diagram showing a force / stroke characteristic line belonging to the driving device of FIGS. 4a to 4c. It is the figure which showed another embodiment of the drive device provided with the triangular lever. Fig. 5b shows the drive device of Fig. 5a in different positions. Fig. 5b shows the drive device of Fig. 5a in a further different position. FIG. 6 is a diagram showing a force / stroke characteristic line belonging to the driving device of FIGS. 5a to 5c. It is the figure which showed another embodiment of the drive device provided with the variable input lever. Fig. 6b shows the drive device of Fig. 6a in different positions. Fig. 6b shows the drive device of Fig. 6a in a further different position. FIG. 6 is a diagram showing a force / stroke characteristic line belonging to the drive device of FIGS. 6a to 6c. FIG. 6b shows the drive of FIG. 6a adjusted to have a short stroke in favor of high forces. 7b shows the drive device of FIG. 7a in different positions. Fig. 7b shows the drive device of Fig. 7a in a further different position. It is a figure which shows the force and stroke characteristic line which belongs to the drive device of FIG. FIG. 7 shows a special embodiment of a drive device with an adjustable length output connecting rod. FIG. 4 is a diagram showing an embodiment of a drive device having an input lever on both sides with a variable lever arm, a stationary support, and two separate disc-shaped transmission members. It is a figure which shows the embodiment of the drive device provided with the input lever and variable support part of both sides. It is a figure which shows the embodiment of the drive device provided with the input lever of the both sides which has a variable lever arm and a non-moving support part. It is a figure which shows the embodiment of the drive device provided with the triangular lever as an input lever, and an upper support point. It is a figure which shows the embodiment of the drive device provided with the triangular lever and the lower support point. It is a figure which shows in detail the structural embodiment of the drive device adjusted steplessly in the setting of a progressive force-stroke characteristic line. 14b shows the drive device of FIG. 14a in different positions. 14b shows in detail the drive device of FIG. 14a set on a constant force / stroke characteristic line; Fig. 15b shows the drive device of Fig. 15a in different positions. It is the figure which showed the embodiment of the drive device provided with two transmission elements and the length adjustment element which were supported rotatably. It is a figure which shows the example of a change of the embodiment of FIG. Figure 16b shows another variation of the embodiment of Figure 16a with a rigid plate. FIG. 16b shows yet another variation of the embodiment of FIG. 16a having a rigid plate. FIG. 17c shows yet another variation of the embodiment of FIG. 16a having two driven units. FIG. 16a shows yet another variation of the embodiment of FIG. 16a. FIG. 16a shows yet another variation of the embodiment of FIG. 16a. It is a figure which shows the embodiment of the drive device provided with the eccentric body as a to-be-driven unit. It is a figure which shows the embodiment of the drive device provided with the eccentric body as a drive unit. It is a figure which shows the embodiment of the drive device provided with the direct moment drive device. It is a figure which shows the embodiment of the drive device provided with the torque motor connected to the transmission unit via the connecting rod. It is a figure which shows the force and stroke characteristic line of the drive device set variously. FIG. 16f shows in detail the adjustable transmission element shown in FIGS. 16f and 16g. It is the figure which showed the embodiment of the drive device which has the pivot point supported so that eccentric rotation was possible.

  FIG. 1 schematically shows a drive device, which is designated by the reference numeral 10 as a whole. The driving device 10 is used to drive the deformation processing device 12. The drive device 10 and the deformation processing device 12 together form a module, in particular a press module.

  The driving device 10 includes a driving unit 14 and a driven unit 16. The drive unit 14 is connected to the driven unit 16 via the transmission element 18. In this embodiment, the driven unit 16 is formed as a toggle lever, which is generally mechanically connected to the transmission element 18 via the input member 20. The driven unit 16 further generally has one output member 22, which is movable linearly or translationally, and in the example of use schematically shown here, on the slide 24. It is connected. The slide 24 supports the lower part of the mold 24 in the deformation processing apparatus 12.

  The transmission element 18 is supported so as to be rotatable about a fulcrum 26. The transmission element 18 has a first pivot point 28 that forms the output pivot point 28 of the transmission element 18. The transmission element 18 further has a second pivot point 30 that forms the input pivot point 30 of the transmission element 18. The input pivot point 30 is connected to the drive unit 14 via an input connection element 32. The output pivot point 28 is connected to the driven unit 16 via the output connection element 34 or to the input member 20 of the driven unit 16.

  The drive unit 14 is designed as a spindle drive 14 and in this particular embodiment transmits the force to the input pivot point 30 via an input connection element 32 which is formed as a connecting rod. This force is shown schematically in FIG. Alternatively, the input pivot point 30 may be directly connected to the spindle of the spindle drive 14. Thus, torque is transmitted to the transmission element 18 that is rotatably supported. This torque is schematically indicated by arrow 38. Torque 38 is transmitted to the input member 20 via the output connection element 34 so that a corresponding force is transmitted to the output member 22 to move the slide 24 as shown schematically by the arrow 40. . In this embodiment, the driven unit 16 is formed as a toggle lever, and has a progressive force / stroke characteristic line between the input member 20 and the output member 22. In other words, the force applied to the slide 24 increases as the work stroke increases. This is based on the special lever action of the toggle lever 16. Alternatively, the drive unit 14 may be a servo controlled hydraulic cylinder.

  The output connecting element 34 pivoted to the output pivot point 28 forms one output toggle lever 42 with the transmission element 18 rotatably supported on the fulcrum 26. The output toggle lever 42 has characteristic force / stroke characteristic lines. This force / stroke characteristic line can be set via the angle 44 of the toggle lever 42 at the output pivot point 28. Since this angle 44 can be adjusted or changed according to a predetermined output position of the output member 22 or a predetermined position of the output member 22, the working stroke of the driving device 10 can vary various values of the angle 44. Start with the various adjustment states you have. As a result, the force / stroke characteristics of the transmission element 18 that change in the same direction or in the opposite direction with respect to the force / stroke characteristic line of the driven unit 16 are adjusted. As a result, various force / stroke characteristics of the output member 22 are adjusted. A line can be set.

  The input connection element 32 pivotally connected to the input pivot point 30 forms an input toggle lever 46 with the transmission element 18. The input toggle lever 46 has an angle 48 formed between the input connection element 32 and the fulcrum 26 at the input pivot point 30.

  If the angle 44 is adjusted to a small value at the starting position of the output member 22, the working stroke of the connecting element 34 is started with a large force (of the reverse toggle lever) and this force decreases over the working stroke. Finish with a small value at an angle 44 of about 90 °. When such a reverse progressive force / stroke characteristic line and the progressive characteristic line of the toggle lever 16 are synthesized, a force / stroke characteristic line of the output member 22 that changes to a concave shape is formed. This characteristic line has high initial and final forces and has a lowest point in the middle range. With a corresponding adjustment of the angle 48 in the force input range of the transmission element 18, i.e. 90 ° in about half the stroke, the transmission element 18 is subjected to a maximum moment in the middle range. On the other hand, the minimum is reached at the beginning and end of the process. By superimposing this convex moment characteristic line on the above-mentioned concave characteristic line of the subsequent element to be combined, the force / stroke characteristic line of the output member 22 becomes extremely flat and compared to a constant characteristic line over a wide stroke range. Approximate. Exceptions are extreme positions, especially at the end of the stroke. This is because the force of the toggle lever is infinite in the straight state. Therefore, in some cases, this process should be completed in advance. On the other hand, if the angle 44 is adjusted to a value of about 90 ° at the starting position of the output member 22, the working stroke of the connecting element 34 is started with a small force, which increases over the working stroke. Ending with a maximum at an angle 44 of about 180 °. Such a progressive characteristic line reinforces the progressive characteristic line of the output member 22 as well. This results in a remarkably progressive force / stroke characteristic line of the output member 22 that rises extremely at the end of the working stroke, as will be described in detail below. Such characteristic lines can be additionally influenced again by changing the angle 48, i.e. further strengthened or weakened.

  Consequently, as a result, the force / stroke characteristic line of the output member 22 can be adjusted differently depending on the angle 44 for the starting position of the output member 22, so that the drive 10 can be used for various work steps. Can be used for By combining with an additional angle 48 which can be variably adjusted, the force / stroke characteristic line of the output member 22 can be adjusted almost arbitrarily.

  2a to 2c schematically show an embodiment of the drive device 10 at various positions in the working stroke S, and FIG. 2d shows the force-stroke characteristic lines resulting from this embodiment. Has been. In the embodiment of FIGS. 2 a-2 c, the transmission element 18 is formed as an integral rigid triangular lever, in which the angle 44 at the starting position of the output member 22 is approximately 90 °. The angle 48 of the input toggle lever 46 is about 45 ° at the starting position. The input pivot point 30, the output pivot point 28, and the fulcrum 26 form an angle of about 100 °.

  Three different positions of the working stroke S are shown in FIGS. 2a to 2c, and the different positions in FIGS. 2a to 2c are shown as S1, S2, S3 correspondingly in the graph of FIG. 2d.

  Due to the special lever action of the input pivot point 30 and the output pivot point 28 at the three positions of the working stroke S shown in FIGS. 2a to 2c, the output member 22 is significantly progressive or shown in FIG. Ascending force / stroke characteristic line is generated. In FIG. 2d, the individual positions of the work steps shown in FIGS. 2a to 2c are indicated by S1, S2, S3 correspondingly. As a result, the force transmitted from the output member 22 differs slightly between the working stroke S1 in FIG. 2a and the working stroke S2 in FIG. On the other hand, it can be seen that the force in the work process S3 corresponding to the position shown in FIG. This is because in the operation step S3 of FIG. 2c, the lever of the input toggle lever 46 is particularly advantageous, and the lever of the output toggle lever 42 extends particularly flat.

  3a to 3c show the drive device 10 at three different work strokes S, and FIG. 3d shows the force / stroke characteristic lines for these three work strokes S. . The drive device 10 corresponds to the drive device of FIGS. 2 a-2 c, and the transmission element 18 has a modified angle 44 of the output toggle lever 42 and a modified angle 48 of the input toggle lever 46. . The same reference numerals are given to the same members, and only special points will be described here.

  In this embodiment, the transmission element 18 is formed as an integral rigid element, in which the input pivot point 30, the output pivot point 28 and the fulcrum 26 have an angle of about 190 °. Is made. In the starting position of the work process indicated by reference numeral S1 in FIG. 3a, the angle 44 of the output toggle lever 42 is very small and the angle 48 of the input toggle lever 46 is about 90 °. Accordingly, a large force is transmitted from the transmission element 18 at such a position in the work process S1. In the position of the work stroke indicated by S2 in FIG. 3B, the angle 44 and the angle 48 are in the intermediate region, so that an intermediate force is transmitted from the transmission element 18, and the work stroke indicated by S3 in FIG. 3C. In this position, the angle 44 is 90 ° and the angle 48 is very large, so that the resulting lever arm of the drive 14 up to the fulcrum 26 is also very small and therefore a small force is transmitted from the transmission element 18. Such a force / stroke characteristic line of the transmission element 18 shown in FIGS. 3 a to 3 c is almost opposite to the progressive force / stroke characteristic line of the driven unit 16, and therefore, when combined, over a wide section. A substantially straight force / stroke characteristic line of the output member 22 is generated. Such force / stroke characteristic lines for the three positions of the work strokes S1, S2, S3 are shown in FIG. 3d.

  The transmission element 18 shown in FIGS. 2 a-2 c and 3 a-3 c is formed as an integral rigid element with a constant angle between the input pivot point 30 and the output pivot point 28. Therefore, the angle 44 of the output toggle lever 42 can be changed only by replacing the transmission element 18.

  In FIGS. 4 a-4 c, alternative embodiments of the transmission element 18 are shown in various installation positions and various work stroke S positions. The same reference numerals are given to the same members, and only special points will be described here.

  The transmission element 18 is formed as a rigid element and in this embodiment has the shape of a semi-disc. The transmission element 18 has four connection positions which are formed as circular openings. These connection positions are used when the input connection element 32 is connected to the transmission element 18 at various positions or pivoted at various positions in order to realize various angles of the output toggle lever 42 or the input toggle lever 46. Used for. One of these connection positions is used to rotatably support the transmission element 18 at various positions and correspondingly form a fulcrum 26.

  In FIGS. 4 a-4 c, two different connection possibilities or support possibilities of the transmission element 18 are shown. In this case, the first connection example is indicated by a solid line, and the second connection example is indicated by a dotted line.

  In the first connection example, the input pivot point 30 and the output pivot point 28 are arranged at an angle of about 190 ° relative to the fulcrum 26, which is shown in FIG. 4a. At the starting position of the work stroke S1, the angle 44 of the output toggle lever 42 is about 90 °, and the angle 48 of the input toggle lever 46 has an obtuse angle of about 120 °.

  In the second connection example (indicated by the dotted line), the transmission element 18 is shifted to the right toward the driven unit 16 and is rotatably supported at a fulcrum 26 '. In this case, the input pivot point 30 ′ is shifted by about 90 ° with respect to the first connection example, so that the angle 44 ′ of the output toggle lever 42 ′ is at the starting position of the work process S 1 shown in FIG. Is an acute angle of about 30 °, and the angle 48 ′ of the input toggle lever 46 is about 90 °.

  In FIG. 4d, the two force / stroke characteristic lines for both examples of incorporating the transmission element 18 are shown as solid and dotted lines, respectively. By special adjustment of the angles 44, 48 with respect to the working stroke positions S1, S2, S3 shown in FIGS. 4a to 4c, the transmission element 18 has a progressive force / stroke characteristic line in the first embodiment. As a result, the force / stroke characteristic line of the output member 22 shown in FIG. 4D has a progressive progression as a whole. In contrast to this, in the second assembling example, the transmission element 18 is opposite to the progressive force / stroke characteristic line of the driven unit 16, or in other words, a large force transmission at the position S1, and at the position S2. Since the intermediate force transmission has a force / stroke characteristic line that enables a slight force transmission at the position S3, as a result, as shown in FIG. 4d, the force / stroke characteristic line of the output member 22 is obtained. As a whole, almost constant time passes over the work process of S1-S3.

  Due to the special embodiment of the transmission element 18 with different connection positions for the pivot point 30 or the fulcrum 26 shown in FIGS. 4 a to 4 c, the transmission element 18 has different force-stroke characteristic lines of the output member 22. It can be incorporated or connected to be configurable.

  FIGS. 5 a-5 c show a variant embodiment of the drive device 10 shown in FIGS. 4 a-4 c, with an additional intermediate lever connected between the drive unit 14 and the input pivot point 30. The drive device 10 is shown schematically. The same reference numerals are given to the same members, and only special points will be described here.

  A first example is shown in solid lines in FIGS. In the first example, the drive unit 14 is connected to the one-side triangular lever 50 and transmits the introduced force 36 to the input pivot point 30. The triangular lever 50 is formed as a one-sided lever and has one support point 52 and two pivot points 54 and 56 for the connecting rod of the drive unit 14 or for the driven connecting rod connected to the transmission element 18. Have.

  5a to 5c, a second connection example without the triangular lever 50 is indicated by a dotted line, which substantially corresponds to the second connection example shown in FIGS. 4a to 4c. .

  The input lever 36 acting on the input pivot point 30 by means of the triangular lever 50, in addition to the change of the force acting angle 48, additionally differs with respect to the lever fulcrum 52, with the lever arm occurring in the force direction 36 and the pivot point 56. Is further modified by the ratio of connecting rods between 1 and 30. In the working position S1, the lever arm of the driving force 36 relating to the lever fulcrum 52 is larger than the lever arm of the connecting connecting rod. As a result, the input 36 acting on the input pivot point 30 is amplified. At the working position S3, this ratio is reversed, i.e. the action of the input 36 is attenuated. In the working position S2, this ratio is compensated. Thereby, when combined, the force in the driven unit 16 is increased in the first half of the working stroke and reduced in the second half as compared to the embodiment without the triangular lever 50. Therefore, a constant force / stroke characteristic line as shown by a solid line in FIG. 5d is generated over a large range of the work stroke. Compared to this, the connection example without the triangular lever 50 similarly has a force / stroke characteristic line that rises linearly over the same work stroke, as shown in FIG. 5d (as a dotted line). .

  In FIGS. 6 a-6 c, another embodiment of the drive device 10 is schematically shown. The drive unit 14 is in this case connected to the input pivot point 30 of the transmission element 18 via a variable one-sided lever 60. The same reference numerals are given to the same members, and only special points will be described here.

  6a to 6c show two connection examples of the one-sided lever 60. FIG. In this case, an example having a small lever is indicated by a solid line, and a second connection example having a large lever is indicated by a dotted line.

  The one-side lever 60 is supported on one side by a support point 62, has an output pivot point 64 that forms an invariable lever distance with respect to the support point 62, and is further connected to the drive unit 14. It has a pivot point 66. In this case, since the input pivot point 66 is formed to be variable or movable, the lever of the input pivot point 66 relative to the support point 62 can be changed.

  FIG. 6d shows two force / stroke characteristic lines for both connection examples for the different work stroke positions S1, S2, S3 shown in FIGS. 6a-6c. In this case, an example having a small lever of one side lever 60 is indicated by a solid line, and a second example having a large lever of one side lever 60 is indicated by a dotted line. The maximum force transmitted from the drive device 10 can be changed by changing the lever of the one-sided lever 60 or the lever action. In this case, as shown in FIG. 6d, the force / stroke characteristic lines are simply shifted in parallel. This creates another possibility of change using the drive device 10.

  FIGS. 7 a to 7 c show another adjustment example of the driving device 10 including the one-side lever 60. In this case, the transmission element 18 is shifted in a direction approaching the driven unit 16 and supported rotatably, as compared with the examples of FIGS. 6a to 6c. The same reference numerals are given to the same members, and only special points will be described here.

  Due to the displacement of the transmission element 18, the work process S of the output member 22 is shortened. The starting position of the output member 22 is in a region where the driven unit 16 already forms a high starting force due to its progressive force / stroke characteristic line. Due to the small value of the angle 44 (of the reverse toggle lever), the transmission element 18 transmits a high force at start-up to the driven unit 16 via the output pivot point 28, this force being reversed during the course of the work process. Decrease progressively. In cooperation with the influence of the angle 48 in the force introduction range of the transmission element 18 already described in FIG. 1, a substantially constant force / stroke characteristic line as described above based on FIGS. 3a to 3d is described. This is a higher power level and a shorter work path. By means of the one-sided lever 60, the basic conversion of the introduction of force on the input pivot point 30 in the transmission element 18 is variable as already explained with reference to FIGS. 6a to 6d, so that the overall force is further amplified. . As a result, this makes it possible to set a high force over the shortened working stroke S, as shown in FIG. 7d.

  FIG. 8 shows another embodiment of the drive device 10 with an adjustable length output connection element 34. Thereby, the same action as shifting the fulcrum 26 of the transmission element 18 is obtained, that is, the angle 44 can be changed. Therefore, in this embodiment, the fulcrum 26 can be fixed. A first example with a short connection element is shown in FIG. 8 by a solid line, whereas a second example with a long connection element is shown by a dotted line. The same reference numerals are given to the same members, and only special points will be described here.

  The transmission element 18 is formed as an integral rigid disk and is rotatably supported at a fulcrum 26. The transmission element 18 has three connection points, and in order to adjust the angle 48 of the input toggle lever 46, to these connection points, the input connection element 32 can be pivoted at two different positions, and The output connection element 34 is pivotally connected to the output pivot point 28. Further, the output connecting element 34 has a length adjusting element 68 so that the length of the output connecting element 34 can be changed and thereby the angle 44 of the output toggle lever 42 can be adjusted.

  In the first connection example shown in FIG. 8, the input pivot point 30 is formed at the outer connection position, in which case the length adjustment element 68 is at an angle 44 at the starting work stroke position shown in FIG. The angle 48 of the input toggle lever 46 has about 120 °, depending on the selection of the connection position of the pivot point 30. This results in a simple force / stroke characteristic line of the output member 22 corresponding to that shown in FIG. 2d by simple means.

  In the second connection example shown in FIG. 8, since the input pivot point 30 'is pivotally connected to the inner connection point, the angle between the points 28' and 30 'is approximately 30 °. Is formed. In the starting position of the work stroke position shown in FIG. 8, the length adjusting element 68 is long so that the angle 44 'of the output toggle lever 42 is an acute angle and smaller than 45 °. On the other hand, the angle 48 ′ of the input toggle lever 46 is about 90 ° at this working stroke position. Such an adjustment results in a substantially linear force / stroke characteristic line of the output member 22 corresponding to that shown in FIG. 3d. The different force / stroke characteristic lines of the output member 22 are adjusted even during extreme conditions by the selection of the pivot position on the transmission element 18 and the selection of the length of the output connection element 34 by the length adjustment element 68. be able to. In another embodiment, the output pivot point 28 can be shifted in different connection examples to change the angle 44.

  FIG. 9 schematically shows an alternative embodiment of the drive device 10, in which the transmission element 18 is formed by two rotatable disks. The transmission element 18 includes an input member 70 and an output member 72. The input pivot point 30 is formed on the input member 70, and the output pivot point 28 is formed on the output member 72. The input member 70 and the output member 72 are rotatably supported at the fulcrum 26. The input member 70 and the output member 72 are formed to be rotatable relative to each other, and are coupled to each other so as not to rotate relative to each other in order to transmit the torque 38 to the driven unit 16 at various relative rotation angles. (Not shown). The input member 70 and the output member 72 can be non-rotatably coupled to each other at various angular positions, so that the various angular positions of the input pivot point 30 and the output pivot point 28 are relative to each other. Can be adjusted. Furthermore, the output connecting element 34 has a length adjusting element 68 so that the angle 44 of the output toggle lever 42 can be adjusted accordingly.

  In this embodiment, the drive unit 14 is connected to the input pivot point 30 via both side levers 74, and the pivot point 76 of the drive unit 14 is movably supported by the both side levers 74. One fulcrum 78 is supported by a stationary support portion.

  In such an embodiment, it is particularly advantageous that the relative pivoting of the pivot points 28, 30 can be adjusted by means of the variable transmission element 18 in a simple manner and with little manipulation, in this case the length adjusting element. 68, the angle 44 of the output toggle lever 42 can be adjusted by simple means. Further, the magnitude of the force that can be transmitted can be adjusted by changing the force of the drive unit 14 via the levers 74 on both sides.

  FIG. 10 schematically shows a variation of the drive device 10 of FIG. The same reference numerals are given to the same members, and only special points will be described here. The drive unit 14 is connected to the input pivot point 30 via the levers 74 on both sides. In this embodiment, the support portion of the fulcrum 78 is slidable or variable, and the drive unit 14 is a fixed pivot. A landing point 80 is pivotally attached to both levers 74. According to a special embodiment of the double-sided lever 74, different forces on the output member 22 can be adjusted, similar to the embodiment shown in FIG.

  FIG. 11 schematically shows another variation of the drive device 10 of FIG. The same reference numerals are given to the same members, and only special points will be described here.

  In the example shown in FIG. 11, the drive unit 14 is arranged laterally next to the transmission element 18 and is connected to the levers 74 on both sides via a slidable pivot point 76. Thereby, the force 36 applied from the drive unit 14 is transmitted to the transmission element 18 in the same direction. Such an embodiment generally provides a particularly compact configuration of the drive device.

  FIG. 12 schematically shows another embodiment of the drive device 10. The same reference numerals are given to the same members, and only special points will be described here.

  In this embodiment, the drive unit 14 is connected to the input pivot point 30 via a triangular lever 82. The triangular lever 82 has an input pivot point 84 and an output pivot point 86, and is rotatably supported by a fulcrum 88. In this embodiment, the triangular lever 82 is supported rotatably about a fulcrum 88 disposed above the triangular lever 82. Thereby, the force 36 from the drive unit 14 is transmitted to the input pivot point 30 in the same direction.

  FIG. 13 schematically shows a variation of the drive device 10 of FIG. The same reference numerals are given to the same members, and only special points will be described here.

  In the embodiment of FIG. 13, the triangular lever 82 is supported so as to be rotatable around a fulcrum 88 disposed below the triangular lever 82. Thereby, the force 36 applied from the drive unit 14 is transmitted to the pivot point 30 in the reverse direction. In other words, a tensile force is generated from the pressing force, and a pressing force is generated from the tensile force.

  14a and 14b schematically show a detailed embodiment of the drive device 10 with a variable one-sided lever 60 and a variable transmission element 18 in different working positions. The same reference numerals are given to the same members, and only special points will be described here.

  The variable lever 60 is supported so as to be rotatable about a fulcrum 62. The output pivot point 64 is connected to the input pivot point 30 of the transmission element 18 via the input connection element 32. The input pivot point 66 is connected via a connecting rod to a drive unit 14 which in this embodiment is formed as a spindle drive 14. The input pivot point 66 can be adjusted in the axial direction of the one-sided lever 60 by means of an adjusting screw 90, thereby the lever travel distance acting between the input pivot point 66 and the output pivot point 64 or fulcrum 62. The adjustment screw 90 can be used for adjustment. The adjusting screw 90 is connected to a corresponding rotary operating element 92 for ease of handling or for automation.

  The transmission element 18 has an input member 70 and an output member 72. The input member 70 and the output member 72 can be coupled to each other at various rotation angles so as not to rotate relative to each other, and are supported so as to be rotatable about the fulcrum 26. Each of the input member 70 and the output member 72 has one dentition section 94, which dentition sections 94 are adjustable relative to each other by a gear 96 to adjust the angular position. Thereby, the relative position of the input pivot point 30 with respect to the output pivot point 28 can be adjusted automatically, preferably by simple means.

  The fulcrum 26 is slidably supported, and is formed to be slidable or movable relative to the driven unit 16 by an adjusting screw 98. The adjusting screw 98 is connected to the operating element 100 so as to adjust the corresponding position of the fulcrum 26, preferably by means of a motor.

  FIG. 14a shows the starting position of the work process. At this starting position, the angle 44 is about 90 °. FIG. 14b schematically shows the end position of the work process. In this end position, the angle 44 of the output toggle lever is about 130 °. This produces a progressive force / stroke characteristic line.

  FIGS. 15 a and 15 b show the detailed embodiment shown in FIGS. 14 a and 14 b with selective adjustment with respect to the relative angular position of the input pivot point 30, the output pivot point 28 and the fulcrum 26. . The same reference numerals are given to the same members, and only special points will be described here.

  In the adjustment shown in FIGS. 15 a and 15 b, the input member 70 and the output member 72 of the transmission element 18 are adjusted to different angular positions, so that the input pivot point 30 is relative to the fulcrum 26. And a relatively large angle of about 270 ° is formed between the output pivot point 28 and the output pivot point 28. Furthermore, the fulcrum 26 is displaced towards the driven unit 16 relative to the adjustment shown in FIGS. 14a and 14b, so that a relatively small angle of the output toggle lever 42 at the output position of FIG. 15a. 44 is adjusted. Thereby, a substantially constant force / stroke characteristic line of the output member 22 is generated. FIG. 15b shows the end position of the work process for the adjustment shown in FIG. 15a.

  In general, depending on the three adjustability of the embodiment shown in FIGS. 14 and 15, or on the three degrees of freedom of the drive device 10 shown in FIGS. The force / stroke characteristic line is adjusted, which generally improves the variability of the drive 10 in general and can be automated.

  In FIG. 16a, another embodiment of the drive device 10 is schematically shown. The same reference numerals are given to the same members, and only special points will be described here.

  The transmission element 18 is formed by an input member 70 and an output member 72. The input member 70 and the output member 72 are rotatable relative to each other and can be coupled to each other so as not to rotate relative to each other. The output connecting element 34 has a length adjusting element 68 for adjusting the angle 44 accordingly. The drive unit 14 is coupled to the second transmission element 102 via a double-sided lever 74, and the second transmission element 102 transmits the force transmitted from the drive unit 14 to the transmission element 18 as a torque 38. Connected to the first transmission element 18. The transmission element 102 includes an input member 104 and an output member 106. The input member 104 and the output member 106 are rotatably supported by a fulcrum 108, are rotatable with respect to each other, and are relatively rotated with respect to each other. Can be combined impossible. An input pivot point 110 is formed on the input member 104, and an output pivot point 112 is formed on the output member 106. The input member 104 and the output member 106 are formed to be rotatable relative to each other and can be coupled to each other so as not to rotate relative to each other. Can be adjusted. The input pivot point 110 is or can be coupled to the levers 74 on both sides in order to transmit the force from the drive unit 14 to the transmission element 102. The output pivot point 112 is connected to the pivot point 30 of the transmission element 18 via a connecting rod in order to transmit the force from the transmission element 102 to the transmission element 18. With such an embodiment having two adjustable transmission elements 18, 102, which are rotatably supported, and a lever 74 on both sides, the force / stroke characteristic line of the output member 22 can be adjusted very accurately. .

  FIG. 16b shows a variation of the embodiment of FIG. 16a. The same reference numerals are given to the same members, and only special points will be described here.

  In this embodiment, the length adjusting element 68 is displaced in the pivot point of the driven unit 16, and the output member 22 is moved upward by the tensile load of the pivot point, and downward by the pressing load. It is adjusted to be moved. Thereby, when the drive unit 14 performs the same movement, the movement direction of the output member 22 can be reversed.

  FIG. 16c shows another embodiment of the drive device 10 shown in FIG. 16a. In this embodiment, the driven unit 16 has a plurality of different pivot points to allow for length adjustment and modification of force / stroke characteristic lines. The same reference numerals are given to the same members, and only special points will be described here.

  The driven unit 16 has a rigid plate or disk, the rigid plate or disk is rotatably supported, and is pivotally attached to the driven connecting rod. The driven connecting rod Is connected to the output member 22 and forms a toggle lever. The rigid disc has a plurality of different pivot points 113 ′, 113 ″, 113 ′ ″, and the input member 20 can be pivotally mounted on these pivot points. This makes it possible to adjust the length of the toggle lever and thus to adjust the angle accordingly, which makes it possible to change the additional force / stroke characteristic line.

  In FIG. 16d, another embodiment of the drive device 10 is schematically shown. In this embodiment, the transmission element 102 is coupled to the driven unit 16 by a length adjustment element, which in this embodiment has a rigid plate or disk with three pivot points. And forms a toggle lever. The same reference numerals are given to the same members, and only special points will be described here.

  Due to the transmission element 102 being coupled to the rigid plate or disk of the driven unit 16, the direction of movement of the output member 22 can be reversed so that, as indicated by the arrow 115, When the output pivot point 112 is moved upward, the output member 22 can be moved upward. Thereby, the movement direction of the output member 22 can be reversed by simple means, and at the same time, the necessary construction space for the drive device 10 can be reduced.

  In FIG. 16e, another embodiment of the drive device 10 is schematically shown. The same reference numerals are given to the same members, and only special points will be described here.

  Unlike the embodiment of FIG. 16d, the drive device 10 of FIG. 16e has two driven units 16, 16 ′. These two driven units 16 and 16 ′ are formed by two parallel toggle levers, and are connected to each other by one connecting rod 117. The connecting rod 117 connects the two driven units 16 and 16 'so that the two output members 22 and 22' move in parallel with the same force / stroke characteristic line. As a result, a uniform force distribution on the tool 24 is obtained.

  In FIG. 16f, another embodiment of the drive device 10 is schematically shown. In this embodiment, the input pivot point 30 is adjustable continuously and linearly, and various output pivot points 28 can be selected. The same reference numerals are given to the same members, and only special points will be described here.

  The input pivot point 30 is supported linearly along the transmission element 18 by the linear adjustment device 119 so as to be adjustable at various intervals with respect to the fulcrum 26, and the lever of the corresponding input toggle lever 46 is operated. It is adjusting. The transmission element 18 has different output pivot points 28, 28 ′, 28 ″ for pivoting the connecting element 34 to the transmission element 18 at various positions and adjusting the angle of the corresponding toggle lever 42. Yes. The connection element 34 has different connection points or support points to adjust the various lengths between the output pivot point 28 and the input member 20 of the driven unit 16. For this purpose, the connection element 34 can optionally or additionally have a length adjustment element 68. The functional form of supporting the connecting element 34 at the output pivot points 28, 28 ', 28' 'will be described in more detail.

  FIG. 16g schematically shows a variation of the embodiment of FIG. 16f. The same reference numerals are given to the same members, and only special points will be described here.

  The connection element 34 in this case has various connection points for fixing the connection element 34 to the various output pivot points 28, 28 ′, 28 ″, and the connection element 34 is connected to the input of the driven unit 16. A plurality of connection points or support points are provided for fixing to the member. The connection point or support point is in this case replaced by a length adjustment element 68. The driven unit 16 further has a plurality of pivot points 20, 20 '. These pivot points can form the input members 20, 20 ′ of the driven unit 16 and can thus be connected to the connection element 34 in various ways. This allows a number of changes in the adjustment of the angle 44 of the toggle lever 42.

  It can be seen that the embodiment shown in FIGS. 16f and 16g can be combined with the previous embodiment, in particular with the parallel toggle lever described in FIG. 16e.

  FIG. 17 schematically shows a variation of the drive device 10 of FIG. 9 with selective driven units. The same reference numerals are given to the same members, and only special points will be described here.

  The output connection element 34 including the length adjusting element 68 is connected to an eccentric body 114 that forms a driven unit of the driving apparatus 10.

  The eccentric body 114 has an input member 20 that is supported so as to be eccentrically rotatable about a fulcrum 116. The input member 20 translates the output member 22 correspondingly in a translational manner according to the rotational position. move. Thus, the driven unit 16 can be formed by simple means.

  FIG. 18 schematically shows an alternative embodiment of the drive device 10 with an optional drive unit. The drive device 10 includes an eccentric body 118 that forms the drive unit 14. Since the eccentric body 118 is eccentrically supported around the fulcrum 120 and is driven by the torque of the drive unit, the force can be transmitted to the transmission element 18 by the input connection element 32. Thereby, 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 member 20 of the driven unit 16 and additionally has a length adjustment element 68. In this case, the transmission element 18 is formed by an eccentric disk, and the rotational movement of the eccentric body 118 directly acts on the input member 20. In this case, the input connecting element 32 having the center point of the eccentric disk and the eccentric fulcrum 120 forms the output toggle lever 42.

  FIG. 19 schematically shows an alternative embodiment of the drive device 10. The same reference numerals are given to the same members, and only special points will be described here.

  In this embodiment, the transmission element 18 is formed as a simple lever that is driven in a circular shape by a torque motor, and is supported on a central point 26 or a fulcrum 26 of the motor. The transmission element 18 has in this embodiment only an output pivot point 28, which is connected to the driven unit 16 via an output connection element 34. This embodiment shown in FIG. 19 constitutes the simplest embodiment of the present invention. However, unlike the embodiments described above, the motor is not uniformly loaded across the stroke characteristic line, but is designed for high moment peaks, i.e. excessively dimensioned.

  FIG. 20 schematically shows another embodiment of the drive device 10. The same reference numerals are given to the same members, and only special points will be described here.

  The transmission element 18 is connected to the torque motor 122 via a connecting rod, and transmits torque 38 to the transmission element 18. This shows the selective driving possibility of the driving device 10. Thereby, unlike the embodiment shown in FIG. 19, the peak in the required moment can be avoided, and therefore the motor can be made smaller.

  FIG. 21 schematically shows various force / stroke characteristic lines that can be adjusted according to different adjustments or embodiments of the present invention so that they can be compared with each other.

  In this case, it is clear that the adjustment can adjust both a short working stroke with high force and a large working stroke with constant high or low force. Further, a progressive force / stroke characteristic line can be set, and a linearly rising force / stroke characteristic line can be realized. In all the characteristic lines shown, the driving force is constant over the entire stroke characteristic line. This exception is only the embodiment of FIG.

  Therefore, as a result, the drive device 10 that can be adapted to the requirements of various processing steps or deformation processing steps can be used variably. Economical use is possible in the smallest possible form of configuration, and at the same time, a troublesome energy storage device can be omitted.

  In FIG. 22, the various output pivot points 28 of the transmission element 18 are shown in detail. The same reference numerals are given to the same members, and only special points will be described here.

  The connecting element 34 or the connecting rod 34 can be connected to the various output pivot points 28, 28 ′ by plug-in coupling, and the connecting rod 34 is pivotally connected to the transmission element 18 at various positions. The connection between the connecting rod 34 and the transmission element 18 in this case has a plug connection 130 at the connecting rod 34, which is movably supported by a plug. An element 132 can be introduced, whereby the transmission element 18 is connected to the connecting rod 34. Each plug-in element 132 has a plurality of parallel plug-in pins, which engage with corresponding receptacles in each plug-in connection 130. Thereby, the diameter of each insertion pin can be kept small, and the favorable length-diameter ratio of an insertion pin is obtained. The transmission element 18 in this case has two parallel rigid plates between which the connecting rod 34 is guided laterally, so that the plug element 132 and the plug connection 130 are Can be pivoted to different output pivot points 28, 28 'by connection between them and connectable to the transmission element.

  Each plug element 132 is provided with a spindle gear 134 which can move each plug element 132 in the axial direction and is accordingly introduced into the plug connection 130. Or can be removed from the plug-in connection 130. The spindle gear 134 transmits the rotational movement as an axial movement in order to move the plug-in element 132 accordingly. One or more spindle gears 134 can each be rotated by a drive motor 136 to move the plug element 132 axially and introduce it into or disconnect from the plug connection 130. The drive motor 136 is connected to each spindle gear 134 by a drive chain 138 and rotates the spindle gear 134 accordingly. Alternatively, the drive motor 136 can be connected to each spindle gear 134 by a gear or drive belt.

  Such a connection between the connecting rod 34 and the transmission element 18 allows the output pivot point 28 to be selected or adjusted with little effort. In this case, it is always possible to connect only one plug-in element 132 to one of the plug-in connections 130 each time, without connecting the other plug-in connections 130, and in each case the output pivot point 28 in each case. A corresponding rotation of the connecting rod 34 around the center is ensured. In this case, in FIG. 22, the pivot point 28 is selected or connected, whereas the pivot point 28 'is not connected.

  FIG. 23 schematically shows another embodiment of the drive device 10. The same reference numerals are given to the same members, and only special points will be described here.

  In the embodiment of FIG. 23, each pivot point is connected to each connecting rod 32, 34, and each pivot point is eccentrically supported on the rotating disk in order to adjust the pivot point or pivot position each time. Yes.

  The input connecting rod 32 is pivotally attached to the transmission element 18 by a first rotating disk 150. The first rotating disk 150 is rotatably supported by the transmission element 18 and has an eccentrically formed pivot point 152 that forms the input pivot point 30. Therefore, the position of the input pivot point 30 can be changed by the rotation of the rotary disk 150. In this case, the rotating disk 150 is fixed to the transmission element 18 at various rotational positions.

  The connecting element 34 is pivotally connected to or connected to the transmission element 18 by a second rotating disk 154. The second rotating disk 154 is rotatably supported and has an eccentric pivot point 156 that forms an output pivot point 28. The second rotating disk 154 can be secured to the transmission element 18 at various rotational positions to change the position of the output pivot point 28 and adjust the angle 44 of the toggle lever 42 accordingly.

  A third rotating disk 158 is formed on the driven unit 16 or the plate of the driven unit 16 and is rotatably supported. The third rotating disk 158 has an eccentric pivot point 160 that forms the input member 20 or the input pivot point of the driven unit 16. A connecting element 34 for transmitting the force from the transmission element 18 to the driven unit 16 is supported at the eccentric pivot point 160. Due to the rotation of the third rotating disk 158 and the fixing of the third rotating disk 158 at various rotational positions, the pivot point in the driven unit 16 can be changed and adjusted accordingly, This can provide further variability of the angle 44 and the output toggle lever 42. The connecting element 34 has an adjusting device 68 for further modification of the toggle lever 42.

  By means of three rotating disks 150, 154, 158 with eccentrically supported pivot points 30, 156, 160, the lever ratio of the drive device 10 is generally adjusted almost continuously with a great deal of variability. can do.

  It will be appreciated that the embodiment shown in FIG. 23 may have only one or only two of the illustrated rotating disks 150, 154, 158, respectively.

Claims (26)

At least one drive unit (14) providing a drive force (30) or drive moment;
A driven unit (16) having an input member (20) and a translationally movable output member (22), the progressive force between the input member (20) and the output member (22) A driven unit (16) having a stroke characteristic line;
A transmission element (18) rotatably supported at a fulcrum (26), the transmission element (18) being capable of transmitting torque (38) to the transmission element (18). Is connected to the drive unit (14) and has an output pivot point (28). The output pivot point (28) has a toggle lever (42) together with the transmission element (18). Is connected to the input element (20) of the driven unit (16), and the force can be transmitted to the driven unit (16). Connected to be
A drive device (10), in particular a drive device (10) for driving a deformation processing device,
The angle (44) of the toggle lever (42) can be changed in relation to the starting position of the output member (22) in order to set the force / stroke characteristic line of the output member (22). A drive device, particularly a drive device for driving a deformation processing device.   In order to set the force / stroke characteristic line of the output member (22), the force / stroke characteristic line of the transmission element (18) is the same as the force / stroke characteristic line of the driven unit (16). The drive device according to claim 1, which can be selected in the direction or in the reverse direction.   The output pivot point (28) of the transmission element (18) is connected to the input member (20) of the driven unit (16), and the length of the connection element (34) is adjustable. The drive device according to claim 1 or 2, wherein there is a drive device.   The fulcrum (26) of the transmission element (18) is configured to be able to be shifted relative to the driven unit (16). Drive device.   5. The device according to claim 1, wherein the angular position of the output pivot point (28) can be changed in relation to the starting position of the output member (22). Drive device.   The output pivot point (28) is supported on an eccentric rotating disk (154) of the transmission element (18) to adjust the angle (44) of the toggle lever (42). 5. The drive device according to claim 1.   An input pivot point (30) is formed on the transmission element (18), and a second toggle lever (46) is formed at the input pivot point (30) together with the transmission element (18). 6. The drive device as claimed in claim 1, wherein the input connection element is pivotally connected.   In order to adjust the angle (48) of the second toggle lever (46), the input pivot point (30) is supported on an eccentric rotating disk (150) of the transmission element (18). Item 8. The driving device according to Item 7.   To adjust the angle (44) of the toggle lever (42), the connecting element (34) is supported on the driven unit (16) via an eccentric rotating disk (158). The drive device according to any one of 1 to 8.   The drive device according to any one of claims 7 to 9, wherein an angle between the input pivot point (30) and the output pivot point (28) is changeable.   11. The linear adjustment device (119) is formed in the transmission element (18), and the linear pivot device (119) supports the input pivot point (30). The driving device according to claim 1.   2. The transmission element (18) is formed with a plurality of connection points forming different positions for the input pivot point (30) and / or the output pivot point (28). The drive device according to any one of 11 to 11.   The transmission element (18) has two separate transmission members (70, 72) supported rotatably about the fulcrum (26), and the input pivot point (30) and the The output pivot point (28) is formed on one of the transmission members (70, 72), respectively, so that the transmission members (70, 72) cannot rotate with respect to each other at various rotation angles. The drive device according to claim 1, wherein the drive device can be coupled.   The drive unit (14) provides a drive moment, the drive unit (14) being connected to the transmission element (18) directly or via a connecting rod. The drive device according to item.   14. The drive device according to claim 1, wherein the drive unit (14) comprises an eccentric drive device (118).   14. The drive device according to claim 1, wherein the drive unit (14) has a spindle drive device (14).   17. Drive device according to claim 15 or 16, wherein the drive unit (14) is connected to the input pivot point (30) by a connecting unit having at least one connecting rod (32).   18. Driving device according to claim 17, wherein the connecting unit comprises a lever (50; 60; 74) connected to the input pivot point (30).   19. The drive device according to claim 18, wherein at least one lever arm (60; 74) of the lever (60; 74) is adjustable.   20. Drive device according to claim 18 or 19, wherein the lever (60) is formed as a one-sided lever (60).   20. Drive device according to claim 18 or 19, wherein the lever (74) is formed as a double-sided lever (74).   The input connection element has at least one second transmission element (102) rotatably supported with two pivot points (110, 112), the two pivot points ( The drive device according to any one of claims 1 to 21, wherein the angle between 110, 112) is changeable.   23. A drive device according to claim 1, wherein the driven unit (16) has a toggle joint (16).   23. A drive device according to any one of claims 1 to 22, wherein the driven unit (114) is formed by an eccentric body (114).   Deformation device (12) comprising one slide (24) and at least one drive (10) according to any one of claims 1 to 24 for driving the slide (24). ) For press module.   A modular press system for machining a workpiece, comprising a plurality of press modules according to claim 25.

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