EP2911871A1 - Dispositif d'entraînement - Google Patents

Dispositif d'entraînement

Info

Publication number
EP2911871A1
EP2911871A1 EP13736530.0A EP13736530A EP2911871A1 EP 2911871 A1 EP2911871 A1 EP 2911871A1 EP 13736530 A EP13736530 A EP 13736530A EP 2911871 A1 EP2911871 A1 EP 2911871A1
Authority
EP
European Patent Office
Prior art keywords
drive device
output
transmission element
force
drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP13736530.0A
Other languages
German (de)
English (en)
Other versions
EP2911871B1 (fr
Inventor
Joerg Rauschenberger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Modus One GmbH
Original Assignee
Modus One GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Modus One GmbH filed Critical Modus One GmbH
Publication of EP2911871A1 publication Critical patent/EP2911871A1/fr
Application granted granted Critical
Publication of EP2911871B1 publication Critical patent/EP2911871B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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 which provides a drive force or a drive torque, an output unit having an input member and a translationally movable output member, wherein the output unit is a progressive force-displacement Course between the input member and the output member, and having a transmission element which is rotatably mounted at a pivot point, wherein the transmission element is connected to the drive unit such that a torque is transferable to the transmission element, and wherein the transmission element has an Nathananlenkddling on in which a connecting element is articulated, which forms a toggle lever with the transmission element, wherein the connecting element is connected to the input member of the output unit in such a way that a force can be transmitted to the output unit.
  • Such drive devices serve to provide the output member a defined force-displacement curve, for example, to drive or press a press or a punch.
  • hydraulic drives are preferably used, since they provide an approximately constant force curve for longer strokes.
  • Different speed curves can be set well in hydraulic drives by controlling the flow rate and a switching point between rapid and working stroke can be chosen arbitrarily.
  • a disadvantage of the hydraulic actuators is the compressibility of the hydraulic oil, which is a compression in the higher single-digit percentage range at the necessary system pressures. This compressibility results in a high heat development, which has a negative effect on the energy balance of the hydraulic process. Further, the compressibility of the hydraulic oil affects the control of the force-displacement curve of the tool, and the force is applied with little rigidity. Therefore, for example, calibration processes are possible only with oversized forces, as a hard knocking is made difficult by the softness of the force. At the completion of a punching process is due to the compressibility highly stored spring energy suddenly released. The resulting cutting impact generates a high noise emission.
  • both hydraulic and mechanical drives over a very wide range can be controlled.
  • 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.
  • a drive for a press in which the drive shaft without spindle o- the gear stage is driven, for example, is known from DE 10 2005 038 583 A1.
  • a disadvantage of the well-known drive devices is that they are technically complex and / or are determined depending on the drive technology on a system-related force-displacement curve.
  • a press module for a forming device with a translationally movable plunger and at least one drive device for driving the plunger according to the first or second aspect or according to an embodiment of the present invention.
  • the angle of the toggle lever is adjustable, which is connected to the output member having a progressive force-displacement curve
  • the force-displacement curve of the transmission element is variably adjustable, so that at the output member different force-path profiles can be provided. This is achieved by different lever effects and thus different power transmissions of the toggle lever can be adjusted at different angles of the toggle lever.
  • the force-displacement curve of the transmission element in the same direction or opposite to the force-displacement curve of the output unit can be selected, can by adding the force-displacement profiles of the transmission element and the output unit can be set almost any force-displacement curve of the output member.
  • the drive device according to both aspects of the present invention is therefore used for different processing or forming steps. reversible, whereby the drive device can be used flexibly. Accordingly, the object of the invention is completely solved.
  • 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 output steering point 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.
  • the fulcrum of the transmission element is made displaceable relative to the output unit.
  • the angle of the toggle lever can be changed and thus adjust a lever of the transmission member on the power stroke, at the same time the transmission member and the connecting element can be made technically less expensive.
  • an angular position of the starting articulation point 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 adjust the angle of the toggle lever.
  • the eccentric hub is preferably fixed in different rotational positions on the transmission element. As a result, the angle can be adjusted with a high degree of freedom and with little effort.
  • 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 toggle 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 setting of the Kraftwegverlaufes the output member can be further increased.
  • the dormitory of the transmission element, theinsanlenk Vietnamese advantamige advantames the transmission element and the connecting element is mounted on the output unit respectively by means of an eccentric hub, so that a versatile variable adjustment of the Kraftwegverlaufes the drive device can be provided in general.
  • 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 input articulation point and the output articulation point is changeable or adjustable.
  • a linear adjustment device is formed on the transmission element, on which the input connection point is mounted.
  • connection points is formed on the transmission element, which form different positions for the input coupling point and / or the Ninth.
  • the transmission member can be manufactured with little technical effort, since the angle of the first and the second toggle lever can be changed only by a displacement of the input connection element and / or the connecting element and thus can be dispensed with elaborate adjustment mechanisms.
  • the transmission element has two separate transmission members, which is rotatably mounted about the pivot point, wherein the matterssanlenk Vietnamese and the complicatanlenk 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.
  • the handling of the transmission element in general and the adjustment of the angle of the toggle lever is easier.
  • 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 torque can be transmitted to the transmission element with little mechanical effort, which at the same time a particularly compact design is possible.
  • 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 articulation point by means of a connection unit which has at least one connecting rod.
  • a connection unit which has at least one connecting rod.
  • connection unit has a lever which is connected to the Letsanlenkddling.
  • lever arm of the lever is adjustable.
  • the maximum force provided by the output member can be adjusted with little technical effort.
  • 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.
  • connection unit has a second rotatably mounted transmission element with two articulation points, wherein an angle between the articulation points is changeable.
  • 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.
  • a drive device can be used for different processing methods, taking advantage of the different power transmissions.
  • Fig. 1 is a schematic representation of a drive device for driving a forming device
  • variable input lever drive device and associated force-displacement characteristics
  • FIG. 8 shows a particular embodiment of the drive device with length-adjustable output connecting rod
  • FIG. 9 shows an embodiment of the drive device with two-sided input lever with variable lever arm and fixed abutment and two separate disk-shaped transmission members.
  • FIG. 10 shows an embodiment of the drive device with two-sided input lever and variable abutment.
  • Fig. 1 1 shows an embodiment of the drive device with two-sided input lever with variable lever arm and fixed abutment.
  • FIG. 12 shows an embodiment of the drive device with a triangular lever as input lever and upper bearing point.
  • 13 shows an embodiment of the drive device with triangular lever and lower bearing point;
  • Fig. 17 shows an embodiment of the drive device with an eccentric as
  • FIG. 20 shows an embodiment of the drive device with a torque motor, which is connected via a connecting rod with the transmission unit.
  • Fig. 21 force-displacement curves of different settings of the drive device
  • Fig. 22 is a detailed illustration of the adjustable transmission element of Figs. 16f and g;
  • Figure 23 shows an embodiment of the drive device with eccentrically rotatably mounted articulation points.
  • 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 formed as a spindle drive 14 and transmits via the input link 32, which is formed in this particular embodiment as a connecting rod, a force on the thoroughlysanlenkddling 30, wherein the force 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 connection element 34 which is articulated at the output connection point 28, together with the transmission element 18 rotatably mounted at the pivot point 26, forms an output knee lever 42, which has a characteristic force-displacement profile.
  • the force-displacement curve is adjustable via an angle 44 of the toggle lever 42 of the Camillanlenkddlings 28.
  • the angle 44 is adjustable or exchangeable for a specific starting position of the output member 22 or for a predefined position of the output member 22, so that a working stroke of the drive apparatus 10 begins at different settings with different values of the angle 44.
  • force-displacement characteristics of the transmission element 18 can be adjusted, which run in the same direction or in opposite directions to the force-displacement curve of the output unit 16, so that as a result different force-displacement characteristics of the output member 22 can be adjusted.
  • the input link 32 which is hinged to the input link 30, forms an input link 46 together with the transfer element 18.
  • the input link 46 has an angle 48 formed between the input link 32 and the pivot point 26 at the input link 30. If the angle 44 is set to a small value in an initial position of the output member 22, the working stroke of the connecting member 34 starts with a large force (reverse toggle), which drops over the power stroke and at an angle 44 of about 90 ° ends with a low value.
  • 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 angle 48 in the force input region of the transmission element 18, namely 90 ° at about half a stroke acts on the transmission element, a maximum moment in the central region, whereas it reaches a minimum at the beginning and at the end of the stroke.
  • the force-displacement curve of the output member 22 is greatly smoothed and comes relatively close to a constant course over a wide stroke range. Exceptions are the extreme positions, especially the end of the stroke, since in the extended position the force of the toggle lever goes to infinity. If necessary, the stroke should therefore be stopped beforehand. If, however, the angle 44 is set to a value of about 90 ° in an initial position of the output member 22, the working stroke of the connecting element 34 begins with a small force which increases over the working stroke and ends at an angle 44 of near 180 ° with a maximum , This progressive course reinforces the likewise progressive course of the output member 22. As a result, a highly progressive, at the end of the working stroke extremely increasing force-path curve of the output member 22, as explained in more detail below. This course can be additionally influenced by a variation of the angle 48, namely again amplified or attenuated.
  • the force-displacement characteristic of the output member 22 can be set differently depending on the angle 44 for an initial position of the output member 22, whereby the drive apparatus 10 can be used for different operations.
  • 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 triangle lever, wherein the angle 44 in an initial position of the output member 22 has approximately 90 °.
  • the angle 48 of the input lever 46 is about 45 ° in the home position.
  • the input linkage point 30, the output linkage point 28 and the pivot point 26 span an angle of about 100 °.
  • FIGS. 2a to c The three different positions of the power stroke S are shown in FIGS. 2a to c and the different positions of FIGS. 2a to c are marked S1, S2 and S3 in the diagram in FIG. 2d.
  • Figures 3a to c show the drive device 10 in three different positions of the power stroke S and Fig. 3d shows an associated force-displacement curve for the three positions of the power stroke S.
  • the drive device 10 corresponds to the drive device of Figures 2a to c wherein the transmission element 18 is formed with changed angles 44, 48 of the output knee lever 42 and the input knee lever 46.
  • the same elements are designated by the same reference numerals, in which case only the special features are explained.
  • the transmission element 18 is designed as a one-piece, rigid element, in which the input connection point 30, the output connection point 28 and the pivot point 26 form an angle of approximately 190 °. In the illustrated in Fig.
  • This force-displacement curve of the transmission element 18 shown in FIGS. 3 a to c is formed approximately counter to the progressive force-displacement curve of the output unit 16, so that in the sum over a long distance an approximately linear force-displacement History of the output member 22 results.
  • This force-displacement curve is shown for the three positions of the working stroke S1, S2, S3 in FIG. 3d.
  • the transmission elements 18 shown in Figures 2a to c and 3a to c are formed as a rigid one-piece elements with a fixed angle between the matterssanlenkddling 30 and the Caribbeanlenkddling 28 so that a change of the angle 44 of the Vietnamese cramps 42 only by replacing the Transmission element 18 can take place.
  • Fig. 4a to c an alternative embodiment of the transmission element 18 in different installation positions and in different positions of the power stroke S is shown.
  • the same elements are designated by the same reference numerals, in which case only the special features are explained.
  • the transmission element 18 is formed as a rigid element and in this embodiment has a semicircular disk shape.
  • the transmission element 18 has four connection positions, which are formed as round recesses are.
  • the terminal positions serve to connect the input connector 32 in different positions to the transmission member 18 and to articulate at the different positions, respectively, to realize different angles of the output knee lever 42 or the input knee lever 46.
  • One of the terminal positions serves to rotatably support the transmission element 18 at different positions and to form the pivot point 26 accordingly.
  • FIG. 4a to c are each two different Anschluß L. Storage options of the transmission element 18 shown, wherein a first connection variant is shown by solid lines and a second connection variant is shown with dashed lines.
  • the input coupling point 30 and the output coupling point 28 are arranged at an angle of approximately 190 ° relative to the pivot point 26, so that in the starting position of the power stroke S1 illustrated in FIG. 4a the angle 44 of the output knee lever 42 is approximately 90 ° and the angle 48 of the input lever 46 has an obtuse angle of about 120 °.
  • the transmission element 18 is rotatably mounted 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 starting position of the working stroke S1 shown in Fig. 4a of the angle 44 'of the output knee lever 42' is an acute angle of about 30 ° and the angle 48 'of the input buckle lever 46 about 90 °.
  • Fig. 4d two force-displacement curves for the two installation variants of the transmission element 18 are shown in accordance with a solid and a dashed line. Due to the particular adjustment of the angles 44, 48 via the working stroke positions S1, S2, S3 shown in FIGS. 4a to c, the transmission element 18 in the first installation variant has a progressive force-displacement curve, so that as a result of the total force -Weg course of the output member 22, which is shown in Fig. 4d, has a progressive course.
  • the transmission element 18 on a force-displacement curve which is in opposite directions to the progressive force-displacement curve of the output unit 16 or in other words in the position S1, a large power transmission in the position S2, an average power transmission, in the Position S3 allows a low power transmission, so that as a result, the total force-displacement curve of the output member 22 over the working stroke between S1 and S3 is substantially constant, as shown in Fig. 4d.
  • the transmission element 18 can be installed or connected so that different force-displacement paths of Output member 22 are adjustable.
  • FIGS. 5a to c A variant of the drive device 10 from FIGS. 4a to c with an additional intermediate lever, which is connected between the drive unit 14 and the input linkage point 30, is shown schematically in FIGS. 5a to c.
  • the same elements are designated by the same reference numerals, in which case only the special features are explained.
  • FIGS. 5 a to c show a first variant with solid lines, in which the drive unit 14 is connected to a one-sided triangular lever 50 in order to transmit the introduced force 36 to the input coupling point 30.
  • the triangular lever 50 is designed as a one-sided lever and has a bearing point 52 and two articulation points 54, 56 for a connecting rod of the drive unit 14 and for an output connecting rod for connecting to the transmission element 18.
  • FIGS. 5a to c show a second connection variant without the triangular lever 50 with dashed lines, which substantially corresponds to the second connection variant from FIGS. 4a to c.
  • the triangular lever 50 By the triangular lever 50, the input force 36 in its effect on the matterssanlenk Vietnamese 30 in addition to the variation of the force acting angle 48 is still changed by the relative to the fulcrum 52 different ratio of the resulting lever arms of the force direction 36 and thembispleuels between the articulation points 56 and 30.
  • the lever arm of the driving force 36 with respect to the fulcrum 52 is larger than the resultant lever arm of the connecting rod.
  • the input force 36 is amplified in its effect on the input connection point 30.
  • FIGS. 6a to c A further variant of the drive device 10 is shown schematically in FIGS. 6a to c.
  • the drive unit 14 is connected via a variable one-sided lever 60 with the 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 connection variants of the one-sided lever 60 are shown in FIGS. 6a to c, wherein a variant with a small lever is shown with solid lines and a second connection variant with a large lever is shown with dashed lines.
  • the one-sided lever 60 is mounted at one bearing point 62 on one side and has an administratanlenkddling 64, which forms a fixed lever path to the bearing point 62 and further includes anetcanlenkddling 66 which is connected to the drive unit 14, wherein the matterssanlenk Vietnamese 66 variable or displaceable is formed so that the lever of the matterssanlenk Vietnamese 66 can be varied relative to the bearing point 62.
  • FIG. 6d two force-displacement curves of the two connection variants of the figures 6a to c for the different working stroke positions S1, S2, S3 are shown, wherein the variant with a small lever of the one-sided lever 60 with a solid line and the second variant with a large lever of the one-sided lever 60 is shown as a dashed line.
  • the maximum force transmitted by the drive device 10 can be varied, wherein, as shown in FIG. 6d, the force-displacement curve is only shifted in parallel. This results in a further possibility of variation for the use of the drive device 10.
  • FIGS. 7a to c show another setting variant of the drive device 10 with the one-sided lever 60.
  • the transmission element 18 is compared to the variants of Fig. 6a to c even closer to the output unit 16 towards offset rotatably supported.
  • the same elements are designated by the same reference numerals, in which case only the special features are explained.
  • FIG. 8 shows a further embodiment of the drive device 10 with a length-adjustable output connecting element 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 at this Embodiment remain fixed.
  • a first variant with a short connecting element is shown in FIG. 8 with solid lines, whereas a second variant with an extended connecting element is shown with dashed lines.
  • the same elements are designated by the same reference numerals, in which case only the special features are explained.
  • the transmission element 18 is formed as a rigid one-piece disc which is rotatably mounted at the pivot point 26.
  • the transmission element 18 has three connection points at which the input connection element 32 can be steered at two different positions in order to adjust the angle 48 of the input knee lever 46, and the output connection element 34 is articulated at the output connection point 28.
  • 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.
  • the input linkage point 30 is formed in the outer terminal position, wherein the length adjustment member 68 is shortened such that the angle 44 in the illustrated in Fig. 8 toastariashubposition is about 90 ° and through the choice of the connection position of the Anlenkddlings 30 of the angle 48 of the matterssskniehebels 46 has about 120 °.
  • connection point 30 is articulated on the interior of the connection points, so that an angle of approximately 30 ° is formed between the two points 28, 30'.
  • the length adjustment The guiding element 68 is extended in such a way that, in the starting position of the working stroke position shown in FIG. 8, the angle 44 'of the output knee lever 42 is pointed and has less than 45 °.
  • the angle 48 'of the input knee lever 46 in this Anlagenhubposition is about 90 °. From this setting results in an approximately linear force-displacement curve of the output member 22, which corresponds to the representation in Fig. 3d.
  • the output linkage 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 connected to different angular positions of the input linkage point 30 and the Vietnameselenkiss 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 a 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 Vietnameseskniehebels 42 are set by simple means can.
  • the force of the drive unit 14 can be deflected via the two-sided lever and the size of the transferable force can also be adjusted.
  • FIG. 10 schematically shows a variant of the drive device 10 from FIG. 9.
  • the same elements are designated by the same reference numerals, in which case only the special features are explained.
  • the drive unit 14 is connected via the two-sided lever 74 to the 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.
  • the two-sided lever 74 it is likewise possible, as in the embodiment according to FIG. 9, to set different forces on the output member 22.
  • FIG. 1 a further variant of the drive device 10 of FIG. 9 is shown schematically.
  • the same elements are designated by the same reference numerals, in which case only the special features are executed.
  • the drive unit 14 is arranged laterally next to the transmission element 18 and connected to the two-sided lever 74 via the displaceable articulation point 76.
  • the force 36 exerted by the drive unit 14 is transmitted in the same direction to the transmission element 18.
  • 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 matterssanlenkddling 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.
  • the force 36 is transmitted in the same direction from the drive unit 14 to the input connection point 30.
  • FIG. 13 schematically shows a variant of the drive device 10 from FIG. 12.
  • the same elements are designated by the same reference numerals, in which case only the special features are explained.
  • the triangular lever 82 is rotatably mounted about the pivot point 88, which is mounted below the triangular lever 82.
  • FIGS. 14 a and b schematically illustrate a detailed embodiment of the drive device 10 with a variable one-sided lever 60 and a variable transmission element 18 in different working stroke positions.
  • the same elements are designated by the same reference numerals, in which case only the special features are explained.
  • the variable lever 60 is rotatably supported about the fulcrum 62.
  • the output link 64 is connected to the input link 30 of the transfer element 18 via the input link 32.
  • the input connection point 66 is connected via a connecting rod to the drive unit 14, which is designed as a spindle drive 14 in this embodiment.
  • the 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 an initial position of the working stroke is shown, in which the angle 44 is about 90 ° and in Fig. 14b, an end position of the power stroke is schematically shown, in which the angle 44 of the Harmonkniehebels is about 130 °. This results in a progressive force-displacement curve.
  • Figures 15a and b the detailed embodiment of Figures 14a and b is shown in an alternative setting with respect to the relative angular position of the input linkage point 30 and the output linkage point 28 and the pivot point 26.
  • the same elements are designated by the same reference numerals, in which case only the special features are explained.
  • FIG. 15b shows an end position of the working stroke for the adjustment from FIG. 15a.
  • Fig. 16a another embodiment of the drive device 10 is shown schematically.
  • the same elements are designated by the same reference numerals, in which case only the special features are explained.
  • the transmission element 18 is formed by the input member 70 and the output member 72, which are rotatable relative to each other and rotatably connected to each other.
  • the output connector 34 has the length adjustment member 68 to adjust the angle 44 accordingly.
  • the drive unit 14 is connected via the two-sided lever 74 to a second transmission element 102, which is connected to the first transmission element 18 in order to transmit the force transmitted by the drive unit 14 as the torque 38 to the transmission element 18.
  • the transmission element 102 has an input member 104 and an output member 106 which are rotatably mounted at a pivot point 108 and which are rotatable with each other and rotatably connected to each other.
  • An input connection point 110 is formed on the input element 104, and an output connection point 12 is formed on the output element 106.
  • the input member 104 and the output member 106 are rotatable to each other and rotatably connected to each other to adjust different angular positions of the matterssanlenk Vietnameses 1 10 and the complicatanlenk Vietnameses 1 12 relative to each other.
  • the partssanlenk Vietnamese 1 10 is connected to the two-sided lever 74 and connected to transmit the power from the drive unit 14 to the transmission element 102.
  • the complicatanlenk Vietnamese 1 12 is connected by means of a connecting rod with the articulation point 30 of the transmission element 18 to a Force from the transmission element 102 to the transmission element 18 to transmit.
  • FIG. 16b shows a variant of the embodiment from FIG. 16a.
  • the same elements are designated by the same reference numerals, in which case only the special features are explained.
  • the length adjustment member 68 is set in this embodiment so that the pivot point of the output unit 16 is offset and the output member 22 is moved by a tensile load of the 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 shows a further embodiment of the drive device 10 from FIG. 16a, in which the output unit 16 has a plurality of different articulation points in order to enable a length adjustment and a force / displacement variation.
  • the same elements are designated by the same reference numerals, in which case only the special features are explained.
  • the output unit 16 has a rigid plate or disc which is rotatably mounted and is articulated to a driven connecting rod, which is connected to the output member 22 and forms a toggle lever.
  • the rigid disc has a plurality of different articulation points 1 13 ', 1 13 ", 1 13"', on which the input member 20 can be articulated.
  • Fig. 16d another embodiment of the drive device 10 is shown schematically, in which the transmission element 102 is connected by means of a length adjustment element with the output unit 16, in this embodiment has a rigid plate or disc with three points of articulation and forms a toggle lever.
  • the same elements are designated by the same reference numerals, only special features are explained here.
  • the direction of movement of the output member 22 can be reversed, so that the output member 22 is moved upward, as the Ninanschddling 1 12 is moved upward, as indicated by an arrow 1 15.
  • 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 another embodiment of the drive device 10 is shown schematically.
  • the same elements are designated by the same reference numerals, in which case only the special features are explained.
  • the drive device 10 of FIG. 16e has compared to the embodiment of FIG. 16d, two output units 16, 16 ', which are formed by two parallel toggle lever and connected by a connecting rod 1 17.
  • the connecting rod 1 17 connects the two output units 16, 16 'such that the two output members 22, 22' are moved in parallel with the same force / displacement curve. As a result, a more uniform distribution of force on the tool 24 can be achieved.
  • Fig. 16f a further embodiment of the drive device 10 is shown schematically, in which the partsanlenk 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 input coupling point 30 is mounted on the transmission element 18 so as to be linearly displaceable at different distances from the pivot point 26 by means of a linear adjusting device 1 19, in order to move the lever of the corresponding input branch. lever 46.
  • the transfer element 18 has different output linkage points 28, 28 ', 28 "to bias the link 34 against the transfer element 18 in different positions and to adjust the angle of the corresponding toggle lever 42.
  • the link 34 has different points of articulation Alternatively or additionally, the connecting element 34 may have the length adjustment element 68.
  • Fig. 16g a variant of the embodiment of Fig. 16f is shown schematically.
  • the same elements are designated by the same reference numerals, only special features are explained here.
  • the connecting element 34 has different connecting points in order to fix the connecting element 34 at the various output connecting points 28, 28 ', 28 "and a plurality of connecting points or bearing points in order to fix the connecting element 34 to the input member of the output unit 16
  • the output unit 16 also has a plurality of articulation points 20, 20 ', which can form the input member 20, 20' of the output unit 16 and can be correspondingly connected differently with the connecting element 34. This results in a large number variations in the adjustment of the angle 44 of the bell crank 42 possible.
  • FIGS. 16f and 16g can also be combined with the previous embodiments, in particular with the parallel toggle levers of FIG. 16e.
  • FIG. 17 schematically shows a variant of the drive device 10 from FIG. 9 with an alternative output unit.
  • the same elements are designated by the same reference numerals, in which case only the special features are explained.
  • the output connection element 34 with the length adjustment element 68 is connected to an eccentric 1 14, which forms the output unit of the drive device 10.
  • the eccentric 1 14 has the input member 20 which is rotatably mounted eccentrically about a pivot point 1 16 and the output member 22 moves in accordance with translational depending on the rotational position.
  • 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 1 18, which forms the drive unit.
  • the eccentric 1 18 is mounted eccentrically about a pivot point 120 and is driven with a torque by a drive unit, so that a force by means of the input connection member 32 is transferable to the transmission element 18.
  • the drive device 10 can be driven by simple means.
  • the input connection element 32 of the eccentric member 1 18 is connected directly to the input member 20 of the output unit and additionally has the length adjustment element 68.
  • the transmission element 18 is formed by the eccentric disc, wherein a rotational movement of the eccentric 1 18 acts directly on the input member 20.
  • the input connecting element 32 forms with a center of the eccentric disc and the eccentric pivot point 120, the Nathanskniehebel 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 member 18 is formed in this embodiment as a simple lever, which is driven in a circle by a torque motor, and is mounted in the center 26 and in the pivot point 26 of the motor.
  • the transmission element 18 has only the output connection point 28, which is connected to the output unit 16 via the output connection element 34.
  • This embodiment illustrated in FIG. 19 forms the simplest embodiment of the invention.
  • the motor is not utilized uniformly over the course of the stroke and must be designed for a high torque peak, ie be oversized.
  • FIG. 20 another embodiment of the drive device 10 is shown schematically.
  • the same elements are designated by the same reference numerals, in which case only the special features are explained.
  • the transmission element 18 is connected via a connecting rod with a torque motor 122 to transmit the torque 38 to the transmission element 18.
  • the tips are avoided in the moment demand compared to the embodiment described in Fig. 19 and the engine can therefore be made smaller.
  • the connecting element 34 or the connecting rod 34 can be connected at the different output connection points 28, 28 'by means of plug connections in order to articulate the connecting rod 34 in different positions on the transmission element 18.
  • the connection between the connecting rod 34 and the connecting element 18 in this case has on the connecting rod 34 a plug connection 130 into which a movably mounted plug element 132 can be inserted in order to connect the connecting element 18 to the connecting rod 34.
  • the plug-in elements 132 each have a plurality of parallel locking pins, which engage in corresponding receptacles of the respective connectors 130. As a result, the diameter of the individual locking pins can be kept small and a favorable length-diameter ratio of the locking pins can be achieved.
  • the connecting element 18 in this case has two parallel rigid plates, between which the connecting rod 34 is guided laterally and articulated by the connection between the plug-in elements 132 and the connector 130 at the different 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, wherein in each case only one of the plug elements 132 can be connected to one of the plug connections 130, wherein the others are not connected are to ensure a corresponding rotation of the connecting rod 34 about the respective réelleanlenkddling 28.
  • the articulation point 28 is selected or connected, whereas the articulation point 28 'is released.
  • FIG. 23 another embodiment of the drive device 10 is shown schematically.
  • the same elements are designated by the same reference numerals, in which case only the special features are explained.
  • the respective articulation points are connected to the respective connecting rods 32, 34 and respectively mounted eccentrically on a turntable to adjust the respective articulation point or the articulation position.
  • the input connecting rod 32 is adjustably connected to the transmission element 18 by means of a first rotary disk 150.
  • the first turntable 150 is rotatably mounted on the transmission element 18 and has an eccentrically formed pivot point 152, which forms the 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 1 18.
  • the second hub 154 is rotatably mounted and has an eccentric steering point 156, which forms the mecanicanlenkddling 28.
  • the second hub 154 can be fixed in different rotational positions on the transmission element 1 18, 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 or the plate of the output unit 16.
  • the third hub 158 has an eccentric connecting point 160, which forms the input member 20 and the input articulation point of the output unit 16.
  • 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 variations and almost infinitely.
  • Fig. 23 may also each have only one or two of the illustrated rotary disks 150, 154, 158.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Press Drives And Press Lines (AREA)

Abstract

La présente invention concerne un dispositif d'entraînement (10), en particulier pour entraîner un dispositif de formage (12), comprenant une unité d'entraînement (14) qui fournit une force d'entraînement (30) ou un couple d'entraînement, une unité de sortie (16) qui présente un organe d'entrée (20) et un organe de sortie (22) déplaçable par translation, l'unité de sortie (16) présentant une courbe force-trajet progressive entre l'organe d'entrée (20) et l'organe de sortie (22), un élément de transmission (18) qui est monté à rotation en un point de rotation (26), l'élément de transmission (18) étant relié à l'unité d'entraînement (14) de manière qu'un couple de rotation (38) puisse être transmis à l'élément de transmission (18) et l'élément de transmission (18) présentant un point d'articulation de sortie (28) auquel est articulé un élément de liaison (34) qui forme avec l'élément de transmission (18) un levier à genouillère (42), l'élément de liaison (34) étant relié à l'organe d'entrée (20) de l'unité de sortie (16) de manière qu'une force puisse être transmise à l'unité de sortie (16), un angle (44) du levier à genouillère (42) pouvant être changé pour une position de sortie de l'organe de sortie (22) afin d'ajuster la courbe force-trajet de l'organe de sortie (22).
EP13736530.0A 2012-10-25 2013-07-05 Dispositif d'entraînement Active EP2911871B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012110207 2012-10-25
PCT/EP2013/064298 WO2014063841A1 (fr) 2012-10-25 2013-07-05 Dispositif d'entraînement

Publications (2)

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

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EP13736530.0A Active EP2911871B1 (fr) 2012-10-25 2013-07-05 Dispositif d'entraînement

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Country Link
EP (1) EP2911871B1 (fr)
JP (1) JP6133429B2 (fr)
WO (1) WO2014063841A1 (fr)

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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
CN112661054A (zh) * 2020-12-29 2021-04-16 苏州华日金菱机械有限公司 一种高抗反作用力上下机构

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CS148900B1 (fr) * 1970-06-10 1973-05-24
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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Also Published As

Publication number Publication date
JP6133429B2 (ja) 2017-05-24
EP2911871B1 (fr) 2017-03-29
JP2015533656A (ja) 2015-11-26
WO2014063841A1 (fr) 2014-05-01

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