EP2363215B1 - Umformeinrichtung - Google Patents

Umformeinrichtung Download PDF

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Publication number
EP2363215B1
EP2363215B1 EP20100002282 EP10002282A EP2363215B1 EP 2363215 B1 EP2363215 B1 EP 2363215B1 EP 20100002282 EP20100002282 EP 20100002282 EP 10002282 A EP10002282 A EP 10002282A EP 2363215 B1 EP2363215 B1 EP 2363215B1
Authority
EP
European Patent Office
Prior art keywords
eccentric
drive means
drive
coupling
designed
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.)
Active
Application number
EP20100002282
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2363215A1 (de
Inventor
Wilfried Abt
Helmut Aichele
Carsten Brechling
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.)
Hinterkopf GmbH
Original Assignee
Hinterkopf 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 Hinterkopf GmbH filed Critical Hinterkopf GmbH
Priority to ES10002282T priority Critical patent/ES2398642T3/es
Priority to EP20100002282 priority patent/EP2363215B1/de
Priority to US13/040,691 priority patent/US8997544B2/en
Publication of EP2363215A1 publication Critical patent/EP2363215A1/de
Application granted granted Critical
Publication of EP2363215B1 publication Critical patent/EP2363215B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D51/00—Making hollow objects
    • B21D51/16—Making hollow objects characterised by the use of the objects
    • B21D51/26—Making hollow objects characterised by the use of the objects cans or tins; Closing same in a permanent manner
    • B21D51/2615—Edge treatment of cans or tins
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D22/00—Shaping without cutting, by stamping, spinning, or deep-drawing
    • B21D22/02—Stamping using rigid devices or tools
    • 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
    • B30B1/26—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 cams, eccentrics, or cranks
    • B30B1/263—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 cams, eccentrics, or cranks work stroke adjustment means
    • 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
    • B30B1/26—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 cams, eccentrics, or cranks
    • B30B1/266—Drive systems for the cam, eccentric or crank axis
    • 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
    • B30B1/26—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 cams, eccentrics, or cranks
    • B30B1/28—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 cams, eccentrics, or cranks the cam, crank, or eccentric being disposed below the lower platen or table and operating to pull down the upper platen or slide
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/04—Frames; Guides
    • B30B15/041—Guides
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49716—Converting

Definitions

  • the invention relates to a forming device for cup-shaped hollow body with a machine frame, a drive device, a workpiece turntable for receiving hollow bodies and a tool carrier for holding machining tools, wherein the workpiece rotary table and tool carrier are opposite and rotatable about an axis of rotation to each other and along the axis of rotation are mutually linearly adjustable and the drive device comprises first drive means for providing a rotary step movement and second drive means for providing a cyclic linear movement between the workpiece rotary table and the tool carrier, in order to enable a deformation of the hollow bodies by means of the processing tools in a plurality of successive processing steps. Furthermore, the invention relates to a method for adjusting a phase position between the first drive means, which is to provide a rotary step movement and second drive means for providing a cyclic linear movement for a forming device for cup-shaped hollow body.
  • a forming machine is known, with the cup-shaped hollow body made of metal, in particular aluminum, from a substantially cylindrical sleeve-shaped initial state partially reshaped, in particular locally retracted, to be able to seal, for example, in the region of the opening a cap or a spray valve.
  • the known forming machine has a machine frame, on which a Support tube is formed. On an outer surface of the support tube, a workpiece rotary table is rotatably mounted. In a recess bounded by the support tube, a linearly displaceable guide tube is accommodated, at the end region of which the tool carrier is attached.
  • a drive device is received, which is designed to generate an intermittent rotary movement of the workpiece rotary table and to produce an oscillating linear movement of the guide tube and the associated tool carrier.
  • the tools provided on the tool carrier in particular forming tools, can be brought into engagement with the hollow bodies held on the workpiece rotary table in order to process them locally, in particular to plastically deform them.
  • the hollow bodies Due to the intermittent rotational movement of the workpiece rotary table, the hollow bodies can be brought into serial contact with the tools mounted on the tool carrier table in order to achieve a stepwise deformation of the hollow bodies from an initial geometry to a target geometry.
  • a device for processing cylindrical metal containers in which a plurality of workpiece holders are accommodated on a rotatably mounted support disk and can be deformed by tools which are fixed to a further support disk, which can perform a linear oscillating relative movement relative to the first support disk.
  • a motor and a gear transmission are provided for the rotational movement of the carrier disk, wherein the carrier disk is fixed after each rotation step by means of a centering device.
  • the second carrier disk is attached to a hydraulic press which provides the desired linear motion.
  • the object of the invention is to provide a forming device which can be adapted in a simple manner to the hollow body to be processed.
  • the second drive means comprise a Hubverstellan extract, which is designed for an adjustment of a working stroke of the cyclic linear movement in response to a control signal of a control device and / or for a continuous adjustment of the power stroke and that the drive means comprises adjusting means for adjusting a Phase position between the rotational step movement and the cyclic linear movement are formed.
  • the hollow bodies to be machined by the forming device may differ from one another with respect to their outer geometry and with respect to the size and arrangement of the regions to be formed on the hollow body.
  • a second embodiment of a hollow body may have a compact design and only require machining in the region of the container opening.
  • a larger or smaller stroke of the cyclic linear motion is required.
  • the processing tools for processing near the bottom region of a slender and elongated hollow body are driven deep into the hollow body, for which a large working stroke of the second drive means is required.
  • a predefinable acceleration of the processing tools during the cyclic linear movement can it is intended to adapt the frequency of the cyclic linear movement to the working stroke.
  • a lower frequency of the cyclic linear motion can be selected for a large stroke than is the case for a small stroke.
  • the Hubverstellan teaspoon invention which is connected to a preferably designed as a machine control control device, from which a control signal for the desired power stroke is sent to the Hubverstellan eleven.
  • An adjustment of the working stroke can be made during the operation of the forming device, preferably, an adjustment of the working stroke takes place at a standstill of the forming device.
  • the adjustment of the working stroke can be made completely automated and without manual intervention of an operator.
  • control device is designed such that it controls the Hubverstellan eleven correspondingly when entering a new value for the stroke or that a running in the control device processing and / or adjustment program can cause the automated and automatic adjustment of working stroke. Additionally or alternatively, a continuous adjustment of the working stroke is possible, so that the working stroke can be adapted exactly to the needs of the machining process for the hollow body.
  • the adjusting means which are designed to set a phase position between the rotary step movement and the cyclic linear movement, depending on For example, an optimization of the frequency for the cyclic linear movement can be provided for the processing of hollow bodies to be carried out. For a predeterminable temporal overlap between the cyclic linear movement and the rotary step movement is provided.
  • the adjusting means are provided which allow a targeted phase change between the cyclic linear movement and the rotary step movement.
  • the adjustment of the phase position takes place when the first coupling device is open and thus without positive coupling between the first and the second drive means.
  • a change in the phase position without canceling the forced coupling between the drive means can be made.
  • first drive means and the second drive means are kinematically positively coupled and that the drive means comprises a first clutch means for temporary separation of the positive coupling between the first drive means and the second drive means.
  • the kinematic positive coupling of the two drive means ensures that the rotational step movement of the first drive means and the cyclic linear movement of the second drive means always run synchronously with each other.
  • the kinematic positive coupling of the two drive means is ensured by a transmission device, for example a lever mechanism, a gear transmission, a belt drive or a combination thereof.
  • This phase shift may be expressed, for example, to the effect that before the adjustment of the power stroke, the cyclic linear movement only takes place when no rotational step movement takes place, while after the adjustment of the working stroke there is a temporal overlap between rotary step movement and cyclic linear movement.
  • the case may occur that the machining tools are still in engagement with the hollow bodies when the next rotary step movement is initiated. Since this can lead to damage to the hollow bodies and / or to the forming device, it is advantageous if a phase shift between rotary step movement and cyclic linear movement is avoided.
  • the first coupling device which is brought before the adjustment of the power stroke from a coupled state in which there is a forced coupling between the first and second working means in a decoupled state in which the positive coupling between the drive means is released.
  • the first clutch device is reactivated, so that the desired positive coupling of the two drive means is restored.
  • the adjusting means are coupled to the control device in order to ensure a, in particular stepless, adjustment of the phase position as a function of the control signal provided to the Hubverstellanssen the control device.
  • an automated adjustment of the phase position is possible, a direct mechanical intervention in the forming device by an operator can be omitted.
  • This simplifies the operation of the forming device since the phase position can be entered via an operator interface of the control device or optionally automated depending on Parameters such as the working stroke and / or the geometry of the hollow body to be processed in the control device is determined.
  • this increases the process reliability for the machining process, since unwanted or critical operating conditions for the forming device can be avoided.
  • the adjustment of the phase position can be made continuously to allow the most accurate processing of the hollow body.
  • the second drive means comprise a crank mechanism, which is kinematically coupled to a drive motor designed to provide a rotational movement and to the first drive means, and in that the coupling device is arranged between the crank mechanism and the first drive means.
  • the crank mechanism is used to convert the rotational movement of the drive motor, which may be in particular an electric motor, in the cyclic linear motion, which is introduced to the tool carrier and / or the workpiece rotary table. Due to the kinematic coupling of the crank mechanism with the first drive means compliance with tight tolerances between the rotary step movement and the cyclic linear motion is favored. Accordingly, the first coupling device is arranged between the crank mechanism and the first drive means.
  • crank mechanism comprises a double eccentric arrangement with a first eccentric and a second eccentric engaging the second eccentric, which serves as Hubverstellan eleven, wherein a connecting rod engages on one of the eccentric, for a kinematic coupling of the workpiece rotary table or the tool carrier to the crank gear is trained.
  • Double eccentric arrangement a low-backlash, in particular backlash-free, implementation of the rotational movement of the drive motor in the cyclic linear movement of the tool carrier and / or the workpiece rotary table can be achieved.
  • the double eccentric arrangement allows the desired stroke adjustment by relative, in particular stepless, rotation of the two intermeshing eccentrics.
  • the connecting rod which converts the circular motion of the double eccentric in a linear movement
  • the coupling carriage is preferably guided linearly on the machine frame and coupled to the tool carrier and / or the workpiece rotary table in order to transmit to cyclic linear movement.
  • the adjusting means comprise a locking device which can be adjusted between a release position and an engagement position for fixing an eccentric of the Doppelezzenteran kann and which can be controlled by the control device.
  • the locking device allows relative rotation of one eccentric of the double eccentric assembly relative to the other eccentric of the double eccentric assembly to permit the desired adjustment of the power stroke.
  • the locking device is preferably designed for a positive engagement in the eccentric and prevents movement, in particular a rotation, of this eccentric during the adjustment of the power stroke.
  • crank mechanism and / or the drive motor and / or at least one eccentric of the double eccentric arrangement and / or the first drive means is assigned a sensor device for determining the respective rotary position, which is connected to the control device.
  • the sensor device which can be, for example, an absolute angle sensor or an incremental rotation angle sensor, and which is also referred to as an encoder
  • the rotational position of the respective sampled component can be determined and in the form of a, preferably electrical, sensor signal the control device is transmitted.
  • the phase position of the rotary step movement relative to the cyclic linear motion can be determined to make a correction of the phase position in a subsequent step using the adjustment.
  • a value table is stored in the control device in which each position of the double eccentric arrangement is assigned a correction value for the phase position between the rotary step movement and the cyclic linear movement.
  • the position of the double eccentric arrangement results from the relative position of the two eccentrics, which can be determined, for example, by respectively associated sensor devices. Starting from this position of the double eccentric arrangement, a determination of the actual phase position between rotary step movement and cyclic linear movement can be made on the basis of the value table or a corresponding calculation algorithm stored in the control device be and compared with a desired phase position for the corresponding position of the Doppelezzenteran accent. In a subsequent step, the desired phase position can then be set.
  • the adjusting means are formed by the drive motor, the locking device and the control device.
  • the drive motor is used to effect the relative rotation of the two eccentrics of the double eccentric arrangement. This can be done, for example, that one of the eccentric is locked in rotation with the aid of the locking device and the other eccentric is relatively rotated by the drive motor by initiating a rotational movement on the crank gear to effect, in particular stepless, adjustment of the power stroke.
  • the control device is preferably designed such that it can drive the drive motor for carrying out rotational movements in the range of fractions of a revolution, for example with an angular resolution of 1 degree.
  • the latter Due to the reduction between the rotational movement provided by the drive motor and the rotational movement of the double eccentric arrangement, the latter can thus be set with an angular resolution which is considerably smaller than the angular resolution for driving the drive motor, so that a continuous adjustment of the working stroke is practically possible.
  • the crank gear comprises a gear wheel, which is coupled to the drive motor and with which the first eccentric is rotatably connected, wherein the connecting rod engages the second eccentric and a second coupling device is designed for a releasable positive coupling of the first eccentric with the second eccentric.
  • the gear can be rotatably mounted, for example by means of bearing journals on a bearing block.
  • the gear on a circumferential outer toothing, in which engages a drive pinion, which is coupled directly or via a gear stage, for example via a flywheel, with the drive motor.
  • On the gear of the first eccentric is rotatably mounted, preferably integrally formed. The eccentric serves to add a translation component to a pure rotational movement of the gear wheel.
  • the first eccentric is encompassed by the second eccentric, which is rotatably mounted on the first eccentric and depending on the relative position relative to the first eccentric increases the translation component of the first eccentric, leaves unchanged or reduced.
  • the connecting rod is rotatably mounted, preferably a connecting rod eye of the connecting rod engages around the second eccentric and thereby enables the transmission of the combined superimposed rotary and linear movements, for example, to a coupling slide.
  • the locking device is designed for engagement in the second eccentric.
  • the second eccentric can be determined for the adjustment of the working stroke by means of the locking device.
  • the second coupling device is driven to the Forced coupling between the two eccentrics to solve.
  • the drive of the drive motor which rotates the gear and the rotatably received thereon first eccentric relative to the detected, in particular blocked, second eccentric until the desired relative position of the two eccentric reaches and thus the desired stroke is set.
  • the second coupling device is engaged again and the locking device disengaged to ensure a free rotation of the gear with the two now again rotatably connected to each other eccentrics.
  • the coupling means are assigned actuating means which are designed for activation by the control device and which allow an optional opening or closing of the coupling device, in particular in dependence on an operating state of the drive means.
  • actuating means an automated, power-operated control of the coupling device is possible.
  • the actuating means are electrically or fluidly actuated, whereby a simple and compact construction of the actuating means can be achieved.
  • the coupling device is designed as a clamping set with at least two clamping rings, wherein adjacently arranged clamping rings have mutually correspondingly executed conical surfaces.
  • a clamping set allows a reliable frictional and with respect to the relative rotational positions optional determination of rotatably connected to each other components, such as the second eccentric with the first Eccentric.
  • the clamping set comprises at least two clamping rings, which each have mutually corresponding conical surfaces.
  • the conical surfaces taper in the direction of a rotational axis of symmetry of the clamping rings, so that by applying a clamping force in the direction of the rotational axis of symmetry radially inwardly and / or outwardly directed radial forces can be exerted by the clamping rings on adjacent components, for example, to set a socket on a shaft. Due to the rotationally symmetrical design of the conical surfaces, the opposing clamping rings can be brought into any desired angular position to each other, so that a rotational relative movement at an angle of 1 degree or smaller between the adjacent components, such as the two eccentrics of the Doppelezzenteran angel are possible.
  • first drive means which are provided for providing a rotary step movement and second drive means, which are provided for providing a cyclic linear movement for a forming device for cup-shaped hollow body
  • second drive means which are provided for providing a cyclic linear movement for a forming device for cup-shaped hollow body
  • the object of the invention with the features of claim 15 is achieved. It is provided that between the first and the second drive means, a first coupling means for a temporary cancellation of a forced coupling between the drive means is arranged and that the second drive means are designed as a crank mechanism with a double eccentric arrangement for stroke adjustment of the cyclic linear movement. Furthermore, a drive motor is provided, which is coupled to the crank mechanism.
  • the method comprises the steps of: detecting an idle state of the drive device, releasing the first clutch means for canceling the positive coupling between the first and second drive means, performing the stroke adjustment by means of the double eccentric arrangement, adjusting the phase position between the first and second drive means, closing the first clutch means for restoring the positive coupling between the first and second drive means.
  • the control device, the drive motor and the double eccentric arrangement are designed such that the adjustment of the working stroke and / or the phase position can be stepless and / or automated, in particular without mechanical intervention of an operator.
  • One in the FIG. 1 illustrated forming device 1, which is used in particular for forming cup-shaped hollow bodies, comprises a machine frame 2, on which a workpiece rotary table 3 and a tool carrier 4 are arranged.
  • the workpiece rotary table 3 is rotatably mounted on the machine frame 2, while the tool carrier 4 is exemplarily linearly movably received on the machine frame 2.
  • the workpiece rotary table 3 is thus mounted so as to be rotatable relative to the machine frame 2 and the tool carrier 4 about an axis of rotation 5.
  • the tool carrier 4 can be moved linearly along the axis of rotation 5 relative to the machine frame 2 and the workpiece rotary table 3.
  • the forming device 1 further comprises a drive device 6, which is designed to provide an intermittent rotational movement or rotational step movement and to provide a cyclically oscillating linear movement.
  • the drive device 6 is designed to provide the rotary step movement to the workpiece rotary table 3 and to provide the cyclically oscillating linear movement to the tool carrier 4.
  • the drive mechanism 6 comprises a double eccentric arrangement 8.
  • the double eccentric arrangement 8 which also includes an eccentric shaft 9 and an eccentric cam 10, serves as an eccentric crankshaft that can be adjusted with respect to the crank stroke to provide a circular circulation movement for a closer one designated connecting rod eye of a connecting rod. 7
  • the forces necessary for driving the connecting rod 7 are provided, for example, by a drive motor 11 designed as an electric motor, which is coupled to a flywheel 13 via a belt drive 12, which is designed as an exemplary V-ribbed belt.
  • the flywheel 13 can be brought into force-transmitting connection with a drive pinion 15 via a flywheel clutch 14 that can be coupled during operation of the forming device 1.
  • the drive pinion 15 is in engagement with a main gear 16, which is received rotatably mounted on two support webs 17, of which due to the sectional view of FIG. 1 only one is visible.
  • main gear 16 On the main gear 16 are in mirror image Arrangement two, preferably in each case integrally formed, exemplarily cylindrical bearing pin 18 attached, which are arranged concentrically to the main gear 16 and engage in a manner not shown in one of the support cheek 17 respectively associated storage and serve the pivot bearing of the main gear 16.
  • the inner eccentric 9 is fixedly mounted on the main gear 16, while the outer eccentric 10 is adjustably mounted on the main gear 16 to adjust the crank stroke of the double eccentric 8 for the connecting rod 7 can.
  • the outer eccentric 10 can be decoupled from the inner eccentric 9 by means of a coupling, not shown, and rotated about a normal to the plane of representation pivot axis, preferably continuously, relative to the inner eccentric 8 for stroke adjustment , Subsequently, the clutch is closed again, so that the two eccentrics 9 and 10 are again coupled to transmit power.
  • the indexing gear 20 converts the continuous rotational movement of the output gear 19 into a discontinuous, intermittent rotational step movement, which is transmitted to the workpiece rotary table 3 via a stepping shaft 22 and a stepping gear 23.
  • an internal toothing is provided on the workpiece rotary table 3 24 is formed, in which the stepping gear pinion 23 engages to transmit the rotary step movement of the stepping gear 20 on the workpiece rotary table 3, which then completes the rotary step movement about the axis of rotation 5.
  • a servo drive can be used, which allows an electrically controlled rotary step movement.
  • the workpiece rotary table 3 is rotatably mounted on a support plate 26 by means of a rotary bearing 25.
  • the support plate 26 is part of a first machine frame part, which also comprises a support frame 31.
  • the support frame 31 has the task of deriving the torques, which act on the support plate 26 by the weight forces of the components mounted on the support plate 26, described in more detail below, into a base plate 32.
  • the rotary bearing 25 comprises, for example, a support ring 26 mounted on the preferably annular bearing ring 28 having a bearing surface on a circumferential outer surface for a plurality of rolling elements 29 shown schematically.
  • the rolling elements 29 are arranged between the bearing ring 28 and a bearing ring 28 opposite, formed on the workpiece rotary table 3 by way of example as a circumferential collar 63 bearing surface 30 and are held by a cage, not shown in position. Together with the bearing ring 28 and the peripheral collar 63, they form a radial bearing which ensures a low-friction rotary movement of the workpiece rotary table 3 with high precision, in particular with respect to the axis of rotation 5 and the tool carrier 4.
  • the sliding bearing ring 62 and the oppositely disposed surface of the workpiece rotary table 3 are supplied by an unspecified lubrication circuit with an intermittent or continuous lubricant supply with lubricant.
  • a support tube 33 is attached, which serves as an example for supporting and linear mounting of the tool carrier 4.
  • the support tube 33 has an exemplary annular cross-section in a cross-sectional plane oriented normal to the axis of rotation 5, not shown.
  • a cylindrical inner surface 35 of the support tube 33 serves as a sliding bearing surface for a coupling slide 34 which is coupled to the connecting rod 7 and serves to implement the combined rotational and linear movement of the connecting rod 7 in a linear movement.
  • the coupling carriage 35 includes by way of example a tubular body 37, on which a bearing pin 38 is mounted for the pivotable mounting of the connecting rod 7.
  • a bearing pin 38 is mounted for the pivotable mounting of the connecting rod 7.
  • On the base body 37 are radially outwardly a plurality of, preferably annular, sliders 39, for example of plain bearing bronze, arranged, which are designed for a sliding movement on the inner surface 35 of the exemplary, made of metal, support tube 33.
  • bearing rails 40 are mounted, which are used as linear guide elements for the tool carrier 4 serve.
  • the bearing rails 40 are arranged at the same angular pitch about the axis of rotation 5, for example in a 120-degree graduation or a 90-degree graduation.
  • linear guides 42 are mounted, which engage around the bearing rails 40 each U-shaped.
  • the linear guides 42 may be formed, for example, as recirculating ball bearings, in which a plurality of cylindrical or spherical rolling elements are received in a guideway and allow a linear relative movement relative to the respective bearing rails 40.
  • the linear guides 42 are braced against each other by not shown clamping means in the radial direction and / or in the circumferential direction of the support tube 33, whereby a backlash, in particular backlash-free, linear bearing of the tool carrier 4 relative to the support tube 33 is achieved. Due to the linear guides 42 of the tool carrier 4 is rotatably received on the support tube 33.
  • a closing plate 43 is attached to the connecting rod 7 facing away from the end face, which carries a threaded spindle 44.
  • the threaded spindle 44 extends, for example, in parallel, in particular concentrically, to the axis of rotation 5.
  • Two spindle nuts 45, 46 spaced apart from each other along the axis of rotation 5 engage in the external thread of the threaded spindle 44 (not shown).
  • the two spindle nuts 45, 46 are rotatably and linearly connected to each other.
  • the second spindle nut 46 is a, preferably hydraulically controllable, linear actuator 48 and a servo motor 49 assigned.
  • the object of the servomotor 49 which is preferably designed as a torque motor and coupled to the second spindle nut 46, rotatably mounted rotor 50 and a stator 51 includes, which is rotatably received in a driver 52, therein, the two spindle nuts 45, 46 by To move rotation along the threaded spindle 44 and thereby allow an adjustment of a starting position of the tool carrier 4 along the threaded spindle 44.
  • the task of the linear adjusting device 48 which can exert a force in the direction of the axis of rotation 5 on the second spindle nut 46, is to brace the second spindle nut 46 relative to the first spindle nut 45 and thus a backlash-free power transmission between the threaded spindle 44 and the driver 52 permit, in which the spindle nuts 45 and 46 are received stationary and rotationally movable.
  • the driver 52 is exemplarily designed as a substantially rotationally symmetrical body and has a circumferential flange 53, to which a tubular coupling means 54 is attached, which is designed for a force-transmitting connection with the tool carrier 4.
  • the flange 53 and the coupling means 54 are dimensioned such that they are slightly elastically deformed due to the transmitted from the tool carrier 4 on the workpiece rotary table 3 forces while possibly occurring tilting of the coupling carriage 34 and the driver 47 take about tilt axes transversely to the axis of rotation 5 at least partially so that these are not or at most proportionally be transferred to the tool carrier 4.
  • a particularly high degree of precision is achieved for the processing of the hollow body 55 accommodated on the workpiece rotary table.
  • a plurality of the same angular distribution to the axis of rotation 5 arranged, also referred to as a chuck workpiece holder 55 are mounted, in each of which cup-shaped hollow body 56 are added.
  • a tool carrier 4 opposite the workpiece rotary table 3 corresponding tool holders 57 corresponding to the workpiece holders 55 are arranged, which are equipped with machining tools 58, for example with forming tools.
  • the clutches are first brought into an engaged, force-transmitting position.
  • the starting position of the tool carrier 4 along the axis of rotation 5 by driving the servo motor 49 and the coupled thereto spindle nuts 45, 46 can be adjusted. Subsequently, the spindle nuts 45, 46 are locked by means of the linear adjusting device 48 on the threaded spindle 44.
  • the drive motor 11 is acted upon by electrical voltage and generates a rotational movement, which is passed through the belt drive 12 to the flywheel 13.
  • the power transmission with the flywheel 13 connected drive pinion 15 sets the main gear 16 in motion.
  • a crank movement is introduced onto the connecting rod 7 by means of the double eccentric arrangement 8.
  • the stepping gear 20 is set in motion via the driven gear 19.
  • the workpiece rotary table 3 is offset by the stepping gear 20 and the associated stepping shaft 22 and the stepping gear 23 and the internal teeth 24 in a rotary step movement about the rotation axis 5.
  • the rotary step movement of the workpiece rotary table 3 and the oscillating linear movement of the tool carrier 4 are coordinated such that the workpiece rotary table 3 rests in the time interval in which the attached to the tool carrier 4 processing tools 58 are in engagement with the hollow bodies 56.
  • the workpiece rotary table 3 completes the rotary step movement, when the processing tools 58 are not engaged with the hollow bodies 56.
  • the machining tools 58 can be sequentially brought into engagement with the hollow bodies 56 in the course of the combined linear and rotary step movement of the tool carrier 4 and the workpiece rotary table 3 in order to achieve a stepwise deformation of the hollow bodies 56.
  • the support webs 17, which essentially form the second machine frame section 59 have a dimensionally stable design and are firmly anchored to the base plate 32, which in turn has a large mass and thus the interference influences can not be moved or only to a small extent in motion.
  • the support plate 26, which carries both the support tube 33 for guiding the tool carrier 4 and the bearing ring 28 for pivotal mounting of the workpiece rotary table 3, is also dimensionally stable and is not or only slightly deformed by the forces occurring during operation of the forming device 1.
  • the support plate 26 is connected via an articulated coupling region 60 to the base plate 32.
  • the support frame 31 has a significantly higher elasticity than the support plate 26, one of the support plate 26, workpiece turntable 3, 4 tool carrier and support tube 33 formed machining unit 61 are considered to be inherently rigid and thereby with respect to the machining process precise assembly.
  • the processing unit 61 is elastically connected to the base plate 32 via the coupling region 60 and the support frame 31. The movement provided by the connecting rod 7 is introduced into the processing unit 61 by means of the coupling carriage 34, which is received slidingly in the support tube 33.
  • the coupling means 54 arranged between the coupling slide 34 and the tool carrier 4 decouples any tilting movements of the coupling slide 34, so that the tool carrier 4 is subjected to a pure linear movement. Since the tool carrier 4 is also accommodated by means of the prestressed, in particular play-free linear guides 42 on the bearing rails 40, an accurate positioning of the processing tools 58 with respect to the hollow bodies 56 is ensured.
  • a locking device 70 which has a pivotally mounted on the machine frame 2 locking lever 71, for example, designed as a hydraulically controllable cylinder Adjusting means 72 and a protruding on the outer eccentric 10 in the axial direction locking bolt 73 includes.
  • the outer eccentric 10 can be determined by the adjusting means 72 is driven by the control device, not shown, and the locking lever 71 pivoted so that it can come into engagement with the locking bolt 73. Subsequently the drive motor 11 is controlled by the control device such that the main gear 16 is a slow, in the representation of FIG. 1 preferably takes place in a clockwise rotation, performs. During this rotational movement, both the inner eccentric 9 and the outer eccentric 10 are initially moved, until the locking pin 73 comes into engagement with the fork-shaped locking lever 71. From this point, a further rotation of the outer eccentric 10 is prevented by the pivoted-locking lever 71, while the inner eccentric 9 can rotate relative to the outer eccentric 10 upon further rotation of the main gear 16.
  • phase position between cyclic linear movement and rotary step movement may change. This is due to the fact that the upper and the lower dead center of the double eccentric arrangement 8, which result from the position of the two eccentrics 9, 10 relative to one another, move relative to the connecting rod 7 during adjustment. Without compensation for the adjusted phase position, a predefinable time sequence of cyclic linear movement and rotary step movement would no longer be guaranteed after stroke adjustment.
  • phase position of the above timing can be specified and adapted exactly to the needs of the machining process for the hollow body.
  • FIG. 2 For the sake of clarity, only the components of the forming device 1 which are essential for these setting processes are shown in FIG FIG. 1 shown. Some of the in the FIG. 2 For the sake of clarity, the components shown are themselves not in the FIG. 1 shown, but form integral parts of the forming device according to the FIG. 1 ,
  • the drive motor 11 is connected via the belt drive 12 in conjunction with the flywheel 13 and can initiate a rotational movement to the flywheel 13 with a corresponding control by a control device 80.
  • the flywheel 13 is associated with the flywheel 14, which by an internal, not shown adjusting means between a disengaged and a force-transmitting Position can be switched.
  • the actuating means in the flywheel clutch 14 is connected to the control device 80 for receiving a corresponding switching signal.
  • the output gear 15 mounted rotatably, which meshes with the main gear 16 and thus allows initiation of the rotational movement of the flywheel 13 to the main gear 16, if the flywheel clutch 14 is engaged.
  • the first eccentric 9 is integrally formed, further integrally formed bearing pin 18 are also attached to the main gear 16, which is for a pivotal mounting of the main gear 16 to the in FIG. 2 not shown support cheeks 17 are provided.
  • the output gear 19 meshes with the main gear 16 and thus enables the transmission of the rotational movement to the stepping gear clutch 21.
  • a not-shown adjusting means is integrated, that the stepping gear clutch 21 can switch between a disengaged and a power transmitting position.
  • This actuating means is also connected to the controller 80 for receiving a corresponding switching signal.
  • the rotational movement of the output gear 19 can be transmitted to the indexer 20, which generates from the continuous rotational movement of the main gear 16, a rotary step movement with a predetermined angular increment.
  • This rotary stepping movement is via the Shaschaltwelle 22 and the step switching pinion 23 transmitted to the workpiece rotary table 3.
  • the outer eccentric 10 On the inner eccentric 9 of the outer eccentric 10 is mounted rotatably.
  • the outer eccentric 10 has a thin-walled sleeve section 81, on which a clamping set 82 designed as a switchable coupling is arranged.
  • the clamping set 82 comprises a double conical ring 83 bearing against the circumference of the sleeve section 81 and two clamping rings 84 resting on the respective conical outer surfaces of the double conical ring 83, which are each conical on an inner circumference.
  • the clamping set 82 is associated with a clamping means 85, which is adapted to initiate axial forces on the two clamping rings 84 in order to approach them in the axial direction or to remove each other and thus initiation of radial clamping forces on the double cone ring 83 and thus on the sleeve portion 81 of outer eccentric 10 to allow.
  • the outer eccentric 10 can optionally be rotatably or rotatably mounted on the inner eccentric 9 in response to a control signal of the control device 80 which acts on the clamping means 85.
  • the outer eccentric 10 can be fixed by means of the locking device 70, to subsequently make the relative adjustment of the inner eccentric 9 relative to the outer eccentric 10 and thus the adjustment of the power stroke for the connecting rod 7.
  • 10 is the main gear 16 and the rotationally fixed connected inner eccentric 9 associated with a rotation angle sensor 86, the sensor signal is transmitted to the control device 80.
  • the relative rotation of the two eccentrics 9, 10 can preferably be determined when the outer eccentric 10 is fixed by means of the locking device 70, as this also its rotational position is known.
  • the rotational position of the inner eccentric 9 is detected by the rotation angle sensor 86. Once the desired relative rotation between inner eccentric 9 and outer eccentric 10 is reached, the outer eccentric 10 by driving the clamping means 85 rotatably fixed to the inner eccentric 9.
  • phase position of the outer eccentric 10 is first fixed by means of the clamping set 82 rotatably on the inner eccentric 9.
  • the flywheel clutch 14 is closed, but the stepper clutch 20 is opened.
  • the locking device 70 is in the neutral position, so that the rotational movement of the outer eccentric 10 does not hinder becomes.
  • the control device 80 can drive the drive motor 11 to bring the connecting rod 7 by rotation of the main gear 16 in the desired position. This can be done with an angular resolution due to the reduction of the rotational movement between the drive motor 11 and main gear 16 and a suitable design of the control device 80, which practically allows a continuous adjustment of the phase angle between cyclic linear movement and rotary step movement.
  • a value table or an algorithm is stored in the control device 80, with the aid of which the phase shift of the cyclic linear movement relative to the rotary step movement can be determined on the basis of the previously made adjustment of the working stroke.
  • the phase angle can additionally be checked via the interrogation of the rotary position of the workpiece rotary table 3 by means of the workpiece rotary table sensor 88, which is, for example, an incremental rotary angle sensor or an inductively operating proximity sensor.
  • a linear sensor 87 may additionally be provided, the signal of which is provided to the control device 80 and can be compared there with the signals of the rotational angle sensor 86.
  • the stepping gear clutch 21 can be closed again. As a result, the forced coupling between the cyclic linear movement and the rotary step movement is restored.
  • FIG. 1 a conveyor belt and a conveyor belt associated Ladesters for a provision of hollow bodies in the tangential direction to a loading position of the workpiece rotary table 3 and another conveyor belt with an associated unloading for removal of hollow bodies in the tangential direction of a discharge position of the workpiece rotary table 3 and other peripheral devices such they are known in the art.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Machine Tool Units (AREA)
EP20100002282 2010-03-05 2010-03-05 Umformeinrichtung Active EP2363215B1 (de)

Priority Applications (3)

Application Number Priority Date Filing Date Title
ES10002282T ES2398642T3 (es) 2010-03-05 2010-03-05 Dispositivo de conformado
EP20100002282 EP2363215B1 (de) 2010-03-05 2010-03-05 Umformeinrichtung
US13/040,691 US8997544B2 (en) 2010-03-05 2011-03-04 Forming device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20100002282 EP2363215B1 (de) 2010-03-05 2010-03-05 Umformeinrichtung

Publications (2)

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EP2363215A1 EP2363215A1 (de) 2011-09-07
EP2363215B1 true EP2363215B1 (de) 2012-10-31

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US9352375B2 (en) * 2013-09-11 2016-05-31 Stolle Machinery Company, Llc Actuator with variable speed servo motor for redraw assembly
CN104226847B (zh) * 2014-08-19 2016-03-09 安徽迎驾贡酒股份有限公司 自动马口铁罐成型机
WO2016051224A1 (en) 2014-10-03 2016-04-07 Martinenghi, S.R.L. Device for forming hollow bodies
ES2767410T3 (es) 2015-02-06 2020-06-17 Hinterkopf Gmbh Dispositivo de conformación
US11117337B2 (en) 2019-03-15 2021-09-14 Promess, Inc. Reciprocating press
CN111195927A (zh) * 2020-01-21 2020-05-26 陈政 双偏心电动斩骨机
EP3922372A1 (en) 2020-06-09 2021-12-15 Simat SRL Forming machine for ends of tubes
CN111745019A (zh) * 2020-07-02 2020-10-09 无锡韦恩科技有限公司 一种铝合金门窗冲压工作站
TWI766335B (zh) * 2020-08-07 2022-06-01 鴻勁精密股份有限公司 移動平台及電子元件移送裝置

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US3270544A (en) * 1963-06-26 1966-09-06 Reynolds Metals Co Can forming apparatus
DE3779290D1 (de) 1987-01-21 1992-06-25 Frattini Costr Mecc Maschine zum formen von konus und flansch an spruehdosen und dergleichen.
CH677336A5 (es) * 1988-08-31 1991-05-15 Bruderer Ag
DE9200550U1 (es) 1992-01-18 1992-04-09 Lempenauer, Peter, 8940 Memmingen, De
DE4307535A1 (de) * 1993-03-10 1994-09-15 Mueller Weingarten Maschf Hubverstelleinrichtung für einen Exzenterantrieb, insbesondere für eine Exzenterpresse
AR027371A1 (es) 2000-02-10 2003-03-26 Envases Uk Ltd Deformacion de cuerpos de pared delgada
CA2396657C (en) * 2001-08-16 2007-11-06 The Minster Machine Company Adjustable stroke mechanism
DE10261534A1 (de) * 2002-12-23 2004-07-15 Alexander Christ Spraydose
ITMI20031783A1 (it) * 2003-09-18 2005-03-19 Donato Manera Dispositivo per regolare la corsa di una pressa meccanica e metodo per regolare detta corsa mediante detto dispositivo
JP4587752B2 (ja) * 2004-09-15 2010-11-24 株式会社小松製作所 ハイブリッド制御サーボプレスの制御装置およびその制御方法
US7555927B2 (en) 2004-10-20 2009-07-07 Universal Can Corporation Bottle-shaped can manufacturing method and bottle-shaped can
US7434442B2 (en) * 2006-08-16 2008-10-14 Werth Advanced Packaging Innovations, Ltd. Container bodymaker
EP2123373A4 (en) * 2007-03-09 2015-10-14 Mitsubishi Materials Corp DOSE MANUFACTURER AND CAN MANUFACTURING METHOD

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Publication number Publication date
US20110214473A1 (en) 2011-09-08
US8997544B2 (en) 2015-04-07
ES2398642T3 (es) 2013-03-20
EP2363215A1 (de) 2011-09-07

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