EP0635320B1 - Serre-flan pour presses à simple effet en particulier pour presses mécaniques et presses de transfert - Google Patents

Serre-flan pour presses à simple effet en particulier pour presses mécaniques et presses de transfert Download PDF

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Publication number
EP0635320B1
EP0635320B1 EP94111292A EP94111292A EP0635320B1 EP 0635320 B1 EP0635320 B1 EP 0635320B1 EP 94111292 A EP94111292 A EP 94111292A EP 94111292 A EP94111292 A EP 94111292A EP 0635320 B1 EP0635320 B1 EP 0635320B1
Authority
EP
European Patent Office
Prior art keywords
press
gear unit
blank
holder
working
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.)
Expired - Lifetime
Application number
EP94111292A
Other languages
German (de)
English (en)
Other versions
EP0635320A1 (fr
Inventor
Eckhard Menger
Gregor Geist
Uwe Dr. Hoyer
Wieland Dr. Petter
Markus Dr. Müller
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.)
Umformtechnik Erfurt GmbH
Original Assignee
Umformtechnik Erfurt 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 Umformtechnik Erfurt GmbH filed Critical Umformtechnik Erfurt GmbH
Publication of EP0635320A1 publication Critical patent/EP0635320A1/fr
Application granted granted Critical
Publication of EP0635320B1 publication Critical patent/EP0635320B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • B21D24/00—Special deep-drawing arrangements in, or in connection with, presses
    • B21D24/04—Blank holders; Mounting means therefor
    • B21D24/08—Pneumatically or hydraulically loaded blank holders
    • 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
    • B21D24/00—Special deep-drawing arrangements in, or in connection with, presses
    • B21D24/10—Devices controlling or operating blank holders independently, or in conjunction with dies
    • B21D24/14—Devices controlling or operating blank holders independently, or in conjunction with dies pneumatically or hydraulically

Definitions

  • the invention relates to a sheet holder in combination with a single-acting press according to the preamble of claim 1 or 2, in particular with a mechanical press and transfer press for sheet metal forming, for holding back during the forming process, for ejecting the sheet metal parts after the forming process with the main function of the low-energy Sheet metal holding for large forces.
  • connection of the coupling rods is complex with this solution. Furthermore, the space required by the coupling rods in the area of the tool room increases the column width of the press, the free area of the tool room environment is influenced and the ram's guideways are moved to the outside. Additional guides are required below the table for the sheet metal crossbeam.
  • the problem of the invention is also during the drawing process of a single-acting press or one single-acting drawing stage of a transfer press to clamp the workpiece against the plunger and thus the sheet metal holder without the plunger having to work against this force and without the connection between the press plunger and the pressure pin plate in order to reduce the stand width of the press and at the same time the position of the Do not influence the ram guide and the free area between the side stand and sliding table or side stand and mounting rail. According to the invention this is achieved by the features described in claims 1 and 2, respectively. Further advantageous refinements of the invention are described in claims 3 to 7.
  • FIG. 1 shows the basic press structure consisting of the press frame 3, the press drive 1 with the drive shaft 27 and the press ram 2 with the upper tool 4.
  • the sliding table 19, which carries the lower tool 7, is mounted on the press table 18 .
  • the sheet metal holder frame 6, on which a circuit board 5 lies, is arranged in this lower tool 7.
  • the sheet metal holder frame 6 is connected to the pressure pin plate 17 via intermediate pins 8 and pressure pins 9.
  • a gearbox is arranged below the press table 18 for converting rotary to translatory motion and is operatively connected to the drive shaft 27 of the press drive 1 via a coupling gearbox 22, here designed as a bevel gearbox.
  • the translation of the coupling gear 22 is chosen so that the torque is minimized.
  • Two or four working cylinders 14, each with piston rods on both sides, are arranged between the transmission and the pressure pin plate 17, thereby ensuring mutual support.
  • the working piston 15 of each working cylinder 14 can be pressurized on the transmission side.
  • a control circuit consisting of a pressure relief valve 13 and an electrical pressure transducer 21, a control and regulating unit 10, a hydraulic control block 16, a hydraulic pressure generator 11, a hydraulic control and damping device 24, which if necessary can be configured with a retraction device, and a pneumatic pressure vessel 25, in operative connection.
  • the pressure pin plate 17 is connected via a piston rod 41 to the cushion assembly 23 in a pneumatic design for generating the die cushion upward movement and the ejection force.
  • the piston rod 41 is at the same time as an electrical displacement transducer 20 in operative connection, which in turn is connected to the control and regulating unit 10.
  • the gear for converting rotary into translatory movement is preferably designed as a lever gear.
  • the rotary movement is transmitted from the coupling gear 22 to the drive shaft 30.
  • a crank 31 is fixedly arranged on the drive shaft 30, the other end of which is operatively connected via a coupling rod 32 to a rocker arm 34 mounted in the pivot point 33.
  • the free end of the rocker arm 34 is connected via a tab 35 to a lever arm 36a of an angle lever 36 which is mounted in a pivot point 29.
  • the other lever arm 36b is connected via a tab 37 to the free end of a rocker arm 38 rotatably mounted on the drive shaft 30.
  • a connecting rod 39 is arranged, which is articulated at its other end to the pressure point 28.
  • the piston rod 12 of each working cylinder 14 is connected directly to a pressure point 28 of the transmission.
  • the gear can be connected upstream in a known manner and therefore gear wheels, not shown.
  • the connection of a pressure point 28 to the piston rods 12 of the working cylinders 14 can alternatively also be made via a guided plate 26, as shown in FIG. 2.
  • the working cylinders 14 are in a rest position, as can be seen from FIG. 4.
  • the pressure point 28 of the transmission passes through a rest phase.
  • the working pistons 15 are in a central position. Before the upper tool 4 is placed on the board 5, the pre-acceleration of the moving elements of the sheet metal holder begins. The pre-acceleration is realized by the kinematics in the transmission.
  • the start of the pre-acceleration is selected so that after approx. 30 mm of travel the moving parts of the sheet metal holder have been accelerated to approx. 80% of the ram speed.
  • the pressure build-up begins in the working cylinders 14 in accordance with predetermined target values.
  • the transmission is designed so that it has approximately the same path-time curve as the press ram 2 in this crank angle range from the beginning of the build-up of force to the bottom dead center.
  • the pressure in the working cylinder 14 is regulated via the control loop in accordance with the path-time profile and the workpiece conditions.
  • the working cylinders 14 are depressurized and the cushion unit takes over the upward movement of the pressure pin plate 17.
  • the pressure pin plate 17 is again in its initial position according to FIG. 1.
  • the pressure pin plate 17 With the function "stop in the lowest position", the pressure pin plate 17 remains in its lowest position after passing through the press ram 2 through the bottom dead center. If necessary, withdrawal is carried out in this phase in a known manner.
  • the pressure pin plate 17 While the pressure pin plate 17 is held in its lowest position by the cushion unit 23, the working cylinder 14 is raised by the gear mechanism. The valves in the control blocks 16 are switched so that an unpressurized oil circulation can take place.
  • the pressure pin plate 17 is moved upward by the cushion unit 23.
  • the damping phase also takes place 50-60 mm before the upper working position of the pressure pin gap 17. During this process, oil is sucked back into the working cylinder 14 until the working piston 15 has reached its approximate middle position. Then the pressure pin plate 17 is again in its initial position.
  • the difference in structure to the first embodiment is as follows:
  • the working pistons 15 of each working cylinder 14 can be pressurized on both sides.
  • both cylinder spaces of the working cylinder 14 are operatively connected to the control loop.
  • the cushion unit 23 from the first exemplary embodiment is thereby replaced and the upward movement of the pressure pin plate 17 is realized by the working piston 15.
  • the displacement transducer 20 is connected to an encoder 42 which is arranged on the pressure pin plate 17.
  • the mode of operation of the sheet metal holder is identical to the aforementioned solution.
  • the pressure build-up during the pre-acceleration takes place simultaneously in the upper and lower cylinder spaces of the working cylinders 14 in accordance with the desired values.
  • the upward movement of the pressure pin plate 17 also takes place according to the 2 known functions. In the "uncontrolled" function, the pressure pin plate 17 follows the press ram 2 after passing through the bottom dead center, likewise after its path-time curve.
  • the pressure pin plate 17 is driven by inflowing pressure oil into the lower cylinder space of the working cylinder 14 and the consequent run-up of the working piston 15.
  • the pressure plate 17 is braked in a controlled manner by pressurization of the working piston 15 on both sides, but differently.
  • the working cylinders 14 subsequently move from the transmission into their upper position by the upward movement of the pressure point 28.
  • the working piston 15 moves relative to the working cylinder 14.
  • the two cylinder spaces of the working cylinder 14 are pressurized in such a way that the pressure pin plate 17 is held in its upper position. With the function "stop in the lowest position", the pressure pin plate 17 remains in its lowest position after passing through the press ram 2 through the bottom dead center.
  • the withdrawal takes place in this phase.
  • the working cylinder 14 is raised.
  • the valves in the control blocks 16 are switched so that an unpressurized oil circulation can take place, and a relative movement between the working cylinder 14 and the working piston 15 takes place.
  • the pressure pin plate 17 is actively moved upwards by the pressure oil below the working piston 15.
  • the moving system is braked in a controlled manner by pressurization of the working piston 15 on both sides, but differently.
  • the stroke within the working cylinder 14 is used to compensate for the ram adjustment and the relative position of the workpiece to the table.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Presses And Accessory Devices Thereof (AREA)

Claims (7)

  1. Serre-flan en combinaison avec une presse à simple effet, en particulier avec une presse mécanique et une presse transfert, dans lequel des vérins (14) possédant des tiges de piston (12) bilatérales sont agencées dans la table (18) de la presse, vérins qui prennent appui l'un sur l'autre pendant l'opération d'emboutissage, un côté des tiges de piston (12) étant relié, par des éléments de transmission (8, 9, 17) au cadre (6) du serre-flan, auquel est agencé, au-dessous, simultanément, un groupe amortisseur (23) destinés à la production de mouvement d'élévation du coussin d'emboutissage et pour la production de la force d'éjection,
    caractérisé
    en ce que l'autre tige de piston (12) des vérins (14) est reliée à un mécanisme servant à la transformation d'un mouvement de rotation en un mouvement de translation,
    le mécanisme est en liaison fonctionnelle, côté entrée, avec l'arbre d'entraînement (27) de l'entraînement (1) de la presse et le piston de travail (15) de chaque vérin (14) peut être chargé par une pression sur le côté mécanisme.
  2. Serre-flan en combinaison avec une presse à simple effet, en particulier avec une presse mécanique et une presse transfert, dans lequel des vérins (14) possédant des tiges de piston (12) bilatérales sont agencées dans la table (18) de la presse, vérins qui prennent appui l'un sur l'autre pendant l'opération d'emboutissage, un côté des tiges de piston (12) étant relié, par des éléments de transmission (8, 9, 17) au cadre (6) du serre-flan,
    caractérisé
    en ce que l'autre tige de piston (12) des vérins (14) est reliée à un mécanisme servant à la transformation d'un mouvement de rotation en un mouvement de translation,
    le mécanisme est en liaison fonctionnelle, côté entrée, avec l'arbre d'entraînement (27) de l'entraînement (1) de la presse et le piston de travail (15) de chaque vérin (14) peut être chargé par une pression sur les deux côtés.
  3. Serre-flan en combinaison avec une presse à simple effet selon les revendications 1 et 2,
    caractérisé
    en ce que la liaison fonctionnelle entre l'arbre d'entraînement (27) de l'entraînement (1) de la presse et le mécanisme peut être réalisé par un mécanisme de transmission (22) tel qu'un mécanisme à roues dentées ou à courroie crantée.
  4. Serre-flan en combinaison avec une presse à simple effet selon les revendications 1 et 3,
    caractérisé
    en ce que le mécanisme est constitué de telle manière que, sur l'arbre d'entraînement (30) soit agencée une manivelle (31) dont l'autre extrémité est en liaison fonctionnelle, par l'intermédiaire d'une bielle (32), avec un levier oscillant (34) monté rotatif sur un point de rotation (33), et l'extrémité libre du levier oscillant (34) est reliée par l'intermédiaire d'une biellette (35) à un bras de levier (36a) appartenant à un levier coudé (36) monté rotatif sur un point de rotation (29), l'autre bras de levier (36b) étant relié, par l'intermédiaire d'une biellette (37), à l'extrémité libre d'un-deuxième levier oscillant (38) monté rotatif sur l'arbre d'entraînement (30) et, dans la région centrale du deuxième levier oscillant (38) est agencée une bielle (39) qui est articulée sur le point de pression (28) par son autre extrémité.
  5. Serre-flan en combinaison avec une presse à simple effet selon les revendication 1 à 3,
    caractérisé
    en ce que la tige de piston (12) des vérins (14) est reliée au point de pression (28) du mécanisme par l'intermédiaire d'une plaque guidée (26).
  6. Serre-flan en combinaison avec une presse à simple effet selon les revendications 1 à 3,
    caractérisé
    en ce que la tige de piston (12) de chaque vérin (14) est reliée directement à un point de pression (28) du mécanisme.
  7. Serre-flan en combinaison avec une presse à simple effet selon les revendications 1 à 3,
    caractérisé
    en ce que des roues de mécanismes peuvent être agencées en amont du mécanisme pour la réduction et/ou en fonction du nombre des vérins (14) du serre-flan.
EP94111292A 1993-07-24 1994-07-20 Serre-flan pour presses à simple effet en particulier pour presses mécaniques et presses de transfert Expired - Lifetime EP0635320B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4324963 1993-07-24
DE4324963A DE4324963A1 (de) 1993-07-24 1993-07-24 Blechhalter für einfachwirkende Pressen, insbesondere für mechanische Pressen und Transferpressen

Publications (2)

Publication Number Publication Date
EP0635320A1 EP0635320A1 (fr) 1995-01-25
EP0635320B1 true EP0635320B1 (fr) 1997-11-19

Family

ID=6493675

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94111292A Expired - Lifetime EP0635320B1 (fr) 1993-07-24 1994-07-20 Serre-flan pour presses à simple effet en particulier pour presses mécaniques et presses de transfert

Country Status (3)

Country Link
EP (1) EP0635320B1 (fr)
DE (2) DE4324963A1 (fr)
ES (1) ES2109559T3 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19538316A1 (de) * 1995-10-14 1997-04-17 Schuler Pressen Gmbh & Co Ziehvorrichtung für eine Presse
DE19756911A1 (de) * 1997-12-19 1999-06-24 Erfurt Umformtechnik Gmbh Pneumatische Zieheinrichtung
JP4722558B2 (ja) * 2004-06-01 2011-07-13 株式会社小松製作所 ダイクッション装置
JP5129731B2 (ja) * 2005-03-07 2013-01-30 ミューラー ワインガルテン アーゲー Ｎｃ駆動装置と液圧パッドを装備したダイクッション
DE102006034201A1 (de) * 2006-07-24 2008-02-07 Siemens Ag Presse

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1778358A (en) * 1930-07-18 1930-10-14 Rudolph W Glasner Drawing press
DE3476524D1 (en) * 1984-06-29 1989-03-09 Schuler Gmbh L Drawing device in a press
DD267205A1 (de) * 1987-12-24 1989-04-26 Warnke Umformtech Veb K Hydraulischer blechhalter fuer einfachwirkende pressen
EP0417752B1 (fr) * 1989-09-12 1994-03-02 Maschinenfabrik Müller-Weingarten AG Presse mécanique ou hydraulique avec dispositif d'étirage ou d'emboutissage pour presse à plusieurs étapes
DE4112943A1 (de) * 1991-04-20 1992-10-22 Schuler Gmbh L Zieheinrichtung im pressentisch einer presse
DE4117102A1 (de) * 1991-05-25 1992-11-26 Schuler Gmbh L Presse mit zieheinrichtung

Also Published As

Publication number Publication date
ES2109559T3 (es) 1998-01-16
EP0635320A1 (fr) 1995-01-25
DE59404610D1 (de) 1998-01-02
DE4324963A1 (de) 1995-01-26

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