EP2911871B1 - Antriebsvorrichtung - Google Patents

Antriebsvorrichtung Download PDF

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Publication number
EP2911871B1
EP2911871B1 EP13736530.0A EP13736530A EP2911871B1 EP 2911871 B1 EP2911871 B1 EP 2911871B1 EP 13736530 A EP13736530 A EP 13736530A EP 2911871 B1 EP2911871 B1 EP 2911871B1
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EP
European Patent Office
Prior art keywords
force
transmission element
output
drive
input
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Active
Application number
EP13736530.0A
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German (de)
English (en)
French (fr)
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EP2911871A1 (de
Inventor
Joerg Rauschenberger
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Modus One GmbH
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Modus One GmbH
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Publication of EP2911871A1 publication Critical patent/EP2911871A1/de
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/10—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by toggle mechanism
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/10—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by toggle mechanism
    • B30B1/14—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by toggle mechanism operated by cams, eccentrics, or cranks

Definitions

  • 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 Weganlenkddling 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.
  • 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.
  • 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.
  • controllable servomotors are connected to roller spindles, which are installed directly in the main power flow.
  • 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.
  • 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.
  • 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,
  • a drive device 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 toastanlenkddling 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
  • 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.
  • 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 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 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.
  • 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.
  • the transmission element has two separate transmission members, which is rotatably mounted about the pivot point, wherein the matterssanlenk Vietnamese and the Profishaw Vietnamese are each formed on one of the transmission members, wherein the transmission members are rotatably connected to each other in different angles of rotation.
  • 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.
  • 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.
  • the Huaweianschddling 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 Ninsch Vietnamese and the input member adjustable.
  • 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.
  • pivot point of the transmission element is made displaceable relative to the output unit.
  • 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.
  • an angular position of the Ninth Sears is designed to be changeable for the starting position of the output member.
  • the angle of the toggle lever can be adjusted, whereby different force-displacement curves of the transmission element can be adjusted.
  • the prayeranschddling is mounted on an eccentric hub on the transmission element to the angle of Adjust knee lever.
  • the eccentric hub is preferably fixed in different rotational positions on the transmission element.
  • the angle can be adjusted with a high degree of freedom and with little effort.
  • the eccentric hub is preferably fixable in different rotational positions on the transmission element to adjust the angle of the second toggle lever.
  • 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.
  • the connecting element is mounted on the output unit by means of an eccentric hub to adjust the angle of the knee lever.
  • the eccentric hub is preferably fixable in different rotational positions on the output unit in order to realize the different storage positions.
  • 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.
  • the contestanlenkddling the transmission element, theroisanlenk Vietnamese 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.
  • 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.
  • an angle between the entrance center point and the exit connection point is designed to be exchangeable or adjustable.
  • a linear adjustment device is formed on the transmission element, on which the input connection point is mounted.
  • 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.
  • the drive unit has an eccentric drive.
  • the drive device can be driven by means of a continuous electric motor.
  • the drive unit has a spindle drive.
  • the drive unit is connected to the input connection point by means of a connection unit which has at least one connecting rod.
  • 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.
  • connection unit has a lever which is connected to the input connection point.
  • lever arm of the lever is designed to be adjustable.
  • lever is designed as a one-sided lever.
  • lever is designed as a two-sided lever.
  • the lever is designed as a triangular lever having two pivot points and a bearing point, which span a triangle.
  • 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.
  • connection unit has a second rotatably mounted transmission element with two articulation points, wherein an angle between the articulation points is exchangeable.
  • the force-displacement curve of the output member can be set even more precisely.
  • the output unit has a knee joint.
  • the output unit is formed by an eccentric.
  • the output unit can be realized with technically simple means in a compact design.
  • 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.
  • a drive device can be used for different processing methods, taking advantage of the different power transmissions.
  • a drive device is shown schematically and generally designated 10.
  • the drive device 10 serves to drive a forming device 12.
  • 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 concertanlenkddling 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.
  • the input coupling point 30 can also be connected directly to the spindle of the spindle drive 14.
  • 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.
  • the drive unit 14 may also be a servo-controlled hydraulic cylinder.
  • the output link 34 which is articulated at the Vietnamese spirit, forms, together with the rotatably mounted at the pivot point 26 transmission element 18 is a Congressskniehebel 42 having a characteristic force-displacement curve.
  • the force-displacement curve is adjustable via an angle 44 of the toggle lever 42 of the Vietnamese spirit, and the like.
  • 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.
  • 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.
  • 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.
  • 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 .
  • 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.
  • 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.
  • the variably adjustable additional angle 48 of the force-displacement curve of the output member 22 is almost arbitrarily adjustable.
  • 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.
  • 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 °.
  • 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 mattersskniehebels 46 is particularly favorable and the lever of the Ninkniehebels 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 matterssanlenk Vietnamese 30, the Camillanlenk Vietnamese 28 and the pivot point 26 form an angle of about 190 °.
  • S1 the angle 44 of the Vietnameseskniehebels 42 is very small and the angle 48 of the mattersskniehebel 46 about 90 °.
  • S1 the position of the working stroke, which is in Fig.
  • 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 matterssanlenkddling 30 and the réelleanlenkddling 28, so that a change of the angle 44 of the Vietnameseskniehebels 42 can be done only by replacing the transmission element 18.
  • 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.
  • 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.
  • 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 °.
  • the transmission element 18 is mounted rotatably offset to the right at the output unit 16 at the pivot point 26 ', wherein the matterssanlenkddling 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 Vietnamese tokens 42' is an acute angle of about 30 ° and the angle 48 'of the matterssskniehebels 46 about 90 °.
  • 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.
  • 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.
  • the transmission element 18 can be installed or connected so that different force-displacement profiles of the output member 22 are adjustable.
  • 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 matterssanlenk Vietnamese 30, shown schematically.
  • the same elements are designated by the same reference numerals, in which case only the special features are explained.
  • 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 nowadayssanlenkddling 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.
  • 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.
  • 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 Vietnamesespleuels.
  • the input force 36 is amplified in its effect on the input connection point 30.
  • the ratio is reversed, the input force 36 is thus reduced in their effect.
  • the ratio is balanced.
  • 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 matterssanlenk Vietnamese 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.
  • 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 Weganlenkddling 64, which forms a fixed lever to the bearing point 62 and further has an etc.
  • the matterssanlenkddling 66 which is connected to the drive unit 14, wherein the matterssanlenk Vietnamese 66 variable or slidably is formed so that the lever of the matterssanlenk Vietnamese 66 can be varied relative to the bearing point 62.
  • 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.
  • 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.
  • FIGS. 7a to c is a further adjustment variant of the drive device 10 with the one-sided lever 60 shown.
  • 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.
  • Fig. 8 shows a further embodiment of the drive device 10 with a length-adjustable output connector 34.
  • 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.
  • 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.
  • 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 Trustarbeithubposition is about 90 ° and by the choice of the connection position of the Anlenk Vietnameses 30 of the angle 48 of the matterssskniehebels 46 has about 120 °.
  • the output connection point 28 can also be displaced in different connection variants in order to vary the angle 44.
  • 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 matterssanlenk Vietnamese 30 is formed on the input member 70 and the réelleanlenk Vietnamese 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 matterssanlenkwhis 30 and the technicallyanlenkiss 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.
  • the drive unit 14 is connected via a two-sided lever 74 to the Taiwansanlenkddling 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.
  • 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 Ninkniehebels 42 can be adjusted by simple means.
  • the force of the drive unit 14 can be deflected via the two-sided lever and the size of the transferable force can also be adjusted.
  • Fig. 10 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 Taiwansanlenk Vietnamese 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 Anlenk Vietnameses 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.
  • 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.
  • 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.
  • a particularly compact design of the drive device 10 is generally possible.
  • 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 nowadayssanlenkddling 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.
  • the triangular lever 82 is rotatably mounted about the pivot point 88, which is mounted above the triangle lever 82.
  • 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.
  • the triangular lever 82 is rotatably mounted about the pivot point 88, which is mounted below the triangular lever 82.
  • the force 36 which is exerted by the drive unit 14, transmitted in the opposite direction to the articulation point 30.
  • a thrust force becomes a tensile force and vice versa.
  • 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 etcsanlenkddling 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 inventorsanlenk Vietnamese 66 and the Vietnamese cuisine 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.
  • 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.
  • 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 Harmonkniehebels is about 130 °. This results in a progressive force-displacement curve.
  • 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 matterssanlenk Vietnameses 30 and the Camillanlenk Vietnameses 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.
  • 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 matterssanlenk Vietnamese 30 and the Vietnameselenk Vietnamese 28 is realized relative to the pivot point 26.
  • 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 Huaweiskniehebels 42 in the starting position Fig. 15a is set. This results in an approximately constant force-displacement curve of the output member 22.
  • Fig. 15b is an end position of the working stroke for the setting Fig. 15a shown.
  • 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.
  • 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 matterssanlenk Vietnameses 110 and the technicallyanlenk Vietnameses 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 concertanlenk Vietnamese 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.
  • 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 Anlenkddlings up and a pressure load down. As a result, the direction of movement of the output member 22 can be reversed for the same movement of the drive unit 14.
  • Fig. 16c 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.
  • 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.
  • the direction of movement of the output member 22 can be reversed so that the output member 22 is moved upward, as the Ninanschddling 112 is moved upward, as by a Arrow 115 is indicated.
  • 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.
  • 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.
  • Fig. 16f a further embodiment of the drive device 10 is shown schematically, in which the partssanlenk Vietnamese 30 is continuously linearly adjustable and different réelleanlenka 28 can be selected.
  • the same elements are designated by the same reference numerals, only special features are explained here.
  • the The designedsanlenk Vietnamese 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 Koreaskniehebels 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
  • 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.
  • 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 Jerusalemanschddlingen 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.
  • 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.
  • 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.
  • an output unit 16 can be formed by simple means.
  • 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.
  • the drive device 10 can be driven by simple means.
  • 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.
  • the input connecting element 32 forms with a center of the eccentric disc and the eccentric pivot point 120, the prayerskniehebel 42nd
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 technicallyanlenkddlingen 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.
  • the drive motor 136 may also be connected to the respective spindle wheel 134 by means of a gear or a drive belt.
  • 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 réelleanlenkddling 28.
  • Fig. 22 is the pivot point 28 selected or connected, whereas the pivot point 28 'is solved.
  • 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.
  • 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 matterssanlenkddling 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 réelleanlenkddling 28.
  • the second rotary disk 154 can be fixed to the transmission element 118 in different rotational positions, to vary the position of the mecanicanlenk Vietnameses 28 and adjust the angle 44 of the bell crank 42 accordingly.
  • a third hub 158 is formed and rotatably supported 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.
  • the connecting element 34 is mounted to transmit the power from the transmission element 18 to the output unit 16.
  • the connecting element 34 has the adjusting device 68 for a further variation of the toggle lever 42.
  • the leverage ratios of the drive device 10 can be generally adjusted with a great many possible variations and almost infinitely.
  • Fig. 23 also only one or two of the illustrated rotors 150, 154, 158 may have.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Press Drives And Press Lines (AREA)
EP13736530.0A 2012-10-25 2013-07-05 Antriebsvorrichtung Active EP2911871B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012110207 2012-10-25
PCT/EP2013/064298 WO2014063841A1 (de) 2012-10-25 2013-07-05 Antriebsvorrichtung

Publications (2)

Publication Number Publication Date
EP2911871A1 EP2911871A1 (de) 2015-09-02
EP2911871B1 true EP2911871B1 (de) 2017-03-29

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EP13736530.0A Active EP2911871B1 (de) 2012-10-25 2013-07-05 Antriebsvorrichtung

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EP (1) EP2911871B1 (enrdf_load_stackoverflow)
JP (1) JP6133429B2 (enrdf_load_stackoverflow)
WO (1) WO2014063841A1 (enrdf_load_stackoverflow)

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DE102014109144B4 (de) 2014-06-30 2021-12-30 Modus One Gmbh Verbesserte C-Gestell-Presse
AT517264B1 (de) * 2015-05-29 2018-04-15 Andritz Ag Maschf Vorrichtung zum Verdichten von gestapelten Blättern oder Scheiben aus Zellstoff
CN107416721B (zh) * 2017-04-13 2023-04-14 上海江南制药机械有限公司 一种高压支撑平稳升降机构
CN110030349A (zh) * 2019-05-13 2019-07-19 常州轻工职业技术学院 一种四杆三级串联力放大机构
CN110370704A (zh) * 2019-07-22 2019-10-25 江苏扬力数控机床有限公司 一种基于连杆机构大吨位全电伺服折弯机
CN112661054B (zh) * 2020-12-29 2025-03-14 苏州华日金菱机械有限公司 一种高抗反作用力上下机构
CN115783932B (zh) * 2022-11-18 2025-07-04 日立电梯（中国）有限公司 一种电梯安全钳提拉装置

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FR2486451A1 (fr) * 1980-07-08 1982-01-15 Forichon Gaston Presse a genouillere
JPS58103996A (ja) * 1981-12-17 1983-06-21 Aida Eng Ltd Ｃ形フレ−ムプレス
JPH07108400A (ja) * 1993-10-13 1995-04-25 Amino:Kk 高速リンク式油圧プレス装置
JPH10249590A (ja) * 1997-03-11 1998-09-22 Kawasaki Yukou Kk サーボモータ駆動のリンクモーションプレスおよびそ のプレス制御方法
JPH11129096A (ja) * 1997-10-28 1999-05-18 Ishikawajima Harima Heavy Ind Co Ltd トランスファプレス
DE19918700A1 (de) * 1999-04-26 2000-11-02 Mueller Weingarten Maschf Hydromechanischer Pressenantrieb
DE19935657A1 (de) * 1999-07-29 2001-02-01 Schuler Pressen Gmbh & Co Presse mit Auswerfereinrichtung für unterschiedliche Auswerferhübe
JP3857134B2 (ja) * 2001-12-28 2006-12-13 旭精機工業株式会社 プレス機械
JP2004034057A (ja) * 2002-07-01 2004-02-05 Morita & Co:Kk プレス機
DE202006004470U1 (de) * 2006-03-21 2006-06-14 Schnupp, Konrad Presshärtepresse
DE102009045543B4 (de) * 2009-09-15 2020-07-09 Rudholzer Gmbh Thermoformanlage und Antriebseinheit sowie ein Verfahren zum Betreiben der Thermoformanlage

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JP6133429B2 (ja) 2017-05-24
JP2015533656A (ja) 2015-11-26
WO2014063841A1 (de) 2014-05-01
EP2911871A1 (de) 2015-09-02

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