EP3938196B1 - Presse à estamper - Google Patents

Presse à estamper Download PDF

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Publication number
EP3938196B1
EP3938196B1 EP19718349.4A EP19718349A EP3938196B1 EP 3938196 B1 EP3938196 B1 EP 3938196B1 EP 19718349 A EP19718349 A EP 19718349A EP 3938196 B1 EP3938196 B1 EP 3938196B1
Authority
EP
European Patent Office
Prior art keywords
connecting rods
punch press
eccentric shaft
crankshaft
balancing
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
EP19718349.4A
Other languages
German (de)
English (en)
Other versions
EP3938196A1 (fr
Inventor
Ugo De Santis
Josef Thomas Hafner
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.)
Bruderer AG
Original Assignee
Bruderer AG
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 Bruderer AG filed Critical Bruderer AG
Publication of EP3938196A1 publication Critical patent/EP3938196A1/fr
Application granted granted Critical
Publication of EP3938196B1 publication Critical patent/EP3938196B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/0064—Counterbalancing means for movable press elements
    • 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
    • B30B1/02—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 lever mechanism
    • B30B1/06—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 lever mechanism operated by cams, eccentrics, or cranks

Definitions

  • the present invention relates to a punching press according to the preamble of claim 1.
  • a punching press with a top drive in which the active connecting rods move counter to the punching direction and the horizontal drive movements required for horizontal mass balancing are picked up on the active connecting rods directly above the eccentric shaft.
  • the drive movements required for vertical mass balancing are picked up at the end of the active connecting rods facing away from the eccentric shaft.
  • US 3,422,688 A discloses a punching press according to the preamble of claim 1.
  • the task is therefore to provide a technical solution which does not have the previously mentioned disadvantage of the prior art or at least partially avoids it.
  • This relates to a punching press with a crank or eccentric drive, which has a crank or eccentric shaft and associated active connecting rods according to the claims for generating the lifting movement of the press ram. Furthermore, the punching press has balancing weights to balance the vertical and horizontal inertial forces that are generated during operation by the movements of the ram drive and the ram.
  • the punching press according to the invention is designed in such a way that it is used for horizontal mass balancing
  • the required horizontal drive movements can be picked up directly on the crankshaft or eccentric shaft, namely on the side of the crankshaft or eccentric shaft.
  • “Side on the crankshaft or eccentric shaft” means that the horizontal movements of a crank pin or an eccentric of the crankshaft or eccentric shaft directly in the area between two horizontal planes, which adjoin the crankshaft or eccentric shaft from below and from above, on the crank pin or Eccentric is picked up.
  • the punching press according to the invention is designed in such a way that the drive movements required for vertical mass balancing are picked up directly on the crankshaft or eccentric shaft, preferably above the crankshaft or eccentric shaft.
  • “Above the crankshaft or eccentric shaft” means that the vertical movements of a crank pin or an eccentric of the crankshaft or eccentric shaft directly in the area between two vertical planes, which adjoin the crankshaft or eccentric shaft from both sides, above the crankshaft or eccentric shaft is picked up on the crank pin or eccentric.
  • the press according to the invention is also designed in such a way that each of the balancing weights serves to balance both horizontal and vertical mass forces.
  • the construction method according to the invention can prevent any vibrations that arise during operation of the components used for horizontal mass balancing from being transferred to the press ram and thereby negatively influencing the cutting or embossing process.
  • a compact design with as few components as possible is also encouraged.
  • the punching press is preferably designed in such a way that the drive movements required for horizontal mass balancing are picked up via components on the crankshaft or eccentric shaft and applied to them Balancing weights are transferred, which are designed separately from the components that serve the ram drive. This makes it possible to achieve maximum decoupling of any vibrations that occur during operation of the components used for horizontal mass balancing from the press ram and thus from the cutting or embossing process.
  • all of the drive movements required for mass balancing are picked up via components on the crankshaft or eccentric shaft and transferred to the balancing weights, which are designed separately from the components , which serve the ram drive.
  • This allows a maximum Achieve decoupling of any vibrations that occur during operation of the components used for mass balancing from the press ram and thus from the cutting or embossing process.
  • the drive movements required for the horizontal mass balancing are preferably picked up via auxiliary connecting rods acting on a crank pin or eccentric of the crankshaft or eccentric shaft, which can be designed completely independently or together with the active connecting rods or any connecting rods for picking up the drive movements for the vertical mass balancing ( demanding passive connecting rods).
  • auxiliary connecting rods extend from the crankshaft or eccentric shaft in a direction transverse to the intended direction of movement of the press ram, i.e. in a substantially horizontal direction pointing away from the crankshaft or eccentric shaft.
  • auxiliary connecting rods facing away from the crankshaft or eccentric shaft are advantageously each coupled to one end of a pivotably mounted double lever, and are preferably articulated thereon.
  • the second end of this double lever is coupled directly or via further coupling elements to a balancing weight for horizontal mass balancing, and is advantageously articulated to it.
  • auxiliary connecting rods facing away from the crankshaft or eccentric shaft are each coupled via a tab to the end of the respective pivotally mounted double lever.
  • the second end of this double lever is preferably coupled via a tab to the respective balancing weight for horizontal mass balancing.
  • auxiliary connecting rods acting on a crank pin or eccentric of the crank or eccentric shaft these auxiliary connecting rods are designed separately from the claimed active connecting rods, which are used to generate the lifting movement of the Press ram serve.
  • these auxiliary connecting rods are each designed together with the active connecting rods, which serve to generate the lifting movement of the press ram.
  • This can expediently be done by forming an active connecting rod and an auxiliary connecting rod in one piece, for example in such a way that the eye of the active connecting rod on the crank or eccentric shaft side also forms the eye of the auxiliary connecting rod on the crank or eccentric shaft side, and that an auxiliary eye is formed on the side of this eye , which forms the eye of the auxiliary connecting rod facing away from the crankshaft or eccentric shaft.
  • the punching press according to the invention is designed in such a way that the drive movements required for vertical mass balancing are applied via acting on a crank pin or eccentric of the crank or eccentric shaft Claimed passive connecting rods are picked up, which can be designed completely independently or together with the active connecting rods or any connecting rods for picking up the drive movements for horizontal mass balancing (claimed auxiliary connecting rods).
  • the passive connecting rods extend from the crankshaft or eccentric shaft in a substantially vertical direction pointing away from the press ram.
  • the ends of the passive connecting rods facing away from the crankshaft or eccentric shaft are advantageously each articulated to one end of a pivotally mounted double lever, the second end of which is articulated directly or via further coupling elements to a balancing weight for vertical mass balancing.
  • the respective balancing weight for vertical mass balancing is carried by the respective end of the respective double lever.
  • auxiliary connecting rods and the passive connecting rods are formed by separate components. This makes it possible to achieve maximum decoupling of any vibrations that arise during operation of the components used for horizontal mass balancing and the components used for vertical mass balancing.
  • the balancing weights for horizontal mass balancing are advantageously on both sides of the crankshaft or eccentric shaft in the punching press according to the invention arranged. This concept has proven to be particularly suitable.
  • the punching press according to the invention is designed in such a way that the active connecting rods extend from the crankshaft or eccentric shaft in the direction of the press ram, the ends of the active connecting rods facing away from the crankshaft or eccentric shaft each being at one end of a one-sided lever are articulated.
  • the other end of the respective one-sided lever is mounted in an articulated manner on the housing of the punching press directly or via additional coupling elements.
  • a pressure tab which is connected to the press ram, is articulated on the one-sided levers in an area between their two ends.
  • Fig. 1 shows a vertical section through a punching press according to the invention, in which, in normal operation, the press ram 13, which is driven by an eccentric drive arranged in the upper part of the press structure 11, works from above against the clamping plate 14 of the press.
  • Fig. 2 is a horizontal section through the press along the line XX in Fig. 1 shows, the plunger 13 is driven via an eccentric shaft 1a, which has an eccentric bushing 1b for the purpose of adjusting the eccentricity.
  • eccentric bushing 1b Arranged on the eccentric bushing 1b are two pairs of active connecting rods 9a, 9b, which extend from the eccentric shaft 1a, 1b in the direction of the press ram 13.
  • the ends of the active connecting rods 9a, 9b facing away from the eccentric shaft 1a, 1b are each articulated in pairs at one end of a substantially horizontally extending one-sided lever 10a, 10b, the other end of which is articulated on the housing 11 of the punching press.
  • a pressure tab 12a, 12b is articulated on the one-sided levers 10a, 10b in the area between the two ends, which is connected to the press ram 13 and moves it up and down during normal operation.
  • the press has two balancing weights 2a, 2b arranged on both sides of the eccentric shaft 1a, 1b, which are mounted within the housing structure 11 of the press and rotate in opposite directions to the press ram during operation 13 and to the components of the plunger drive 9a, 9b; 10a, 10b; 12a, 12b are moved so that they compensate for the vertical and horizontal mass forces generated by them to a large extent within the press.
  • Fig. 3 which has an essentially horizontal cut along the line YY in Fig. 1 shows, the drive of the balancing weights 2a, 2b is designed such that the drive movements required for the horizontal and vertical mass balancing are picked up directly on the eccentric shaft 1a, 1b.
  • the drive movements required for horizontal mass balancing are picked up on both sides laterally on the eccentric shaft 1a, 1b via auxiliary connecting rods 5a, 5b arranged on the eccentric bushing 1b, which, starting from the eccentric shaft 1a, 1b, extend in a direction transverse to the intended direction of movement S of the press ram 13 extend.
  • the auxiliary connecting rods 5a, 5b and the passive connecting rods 3a, 3b are formed by common components, that is to say a passive connecting rod 3a or 3b and an auxiliary connecting rod 5a or 5b are combined to form a common one-piece component.
  • This is implemented in such a way that the eccentric shaft-side eye 16a, 16b of the respective passive connecting rod 3a, 3b also simultaneously forms the eccentric shaft-side eye of the associated auxiliary connecting rod 5a, 5b, and that an auxiliary eye 15a, 15b is formed on the side of this eye 16a, 16b, which the eye of the respective auxiliary connecting rod 5a, 5b facing away from the eccentric shaft.
  • the active connecting rods 9a, 9b are designed separately from the auxiliary connecting rods 5a, 5b and the passive connecting rods 3a, 3b.
  • auxiliary connecting rods 5a, 5b facing away from the eccentric shaft 1a, 1b, which are formed by the auxiliary eyes 15a, 15b, are each coupled via a tab 8a, 8b to one end of a pivotably mounted double lever 6a, 6b, the second end of which via another Tab 7a, 7b is coupled to the lower end of one of the balancing weights 2a, 2b.
  • the arrangement of the tabs and levers 7a, 8a, 6a, or 7b, 8b, 6b is selected such that a horizontal movement of the auxiliary eye 15a, 15b of the respective auxiliary connecting rod 5a, 5b causes an opposite horizontal movement of the respectively assigned balance weight 2a or 2b causes.
  • the punching press is therefore designed in such a way that the drive movements required for horizontal mass balancing are carried out via components 5a, 5b; 6a, 6b; 7a, 7b; 8a, 8b are picked up on the eccentric shaft 1a, 1b and transferred to the balancing weights 2a, 2b, which are designed separately from the components 9a, 9b; 10a, 10b; 12a, 12b, which serve the plunger drive.
  • the ends of the passive connecting rods 3a, 3b facing away from the eccentric shaft 1a, 1b, which are each formed by an eye 17a, 17b, are each articulated at one end of a pivotally mounted double lever 4a, 4b, the second, fork-shaped end of which is at the upper end of one of the Balancing weights 2a, 2b are articulated and carry them.
  • the arrangement is chosen such that a vertical movement of the eye 17a, 17b of the respective passive connecting rod 3a, 3b causes an opposite vertical movement of the respectively assigned balance weight 2a or 2b.
  • the punching press is also designed in such a way that the drive movements required for vertical mass balancing are carried out via components 3a, 3b; 4a, 4b are picked up on the eccentric shaft 1a, 1b and transferred to the balancing weights 2a, 2b, which are formed separately from the components 9a, 9b; 10a, 10b; 12a, 12b, which serve the plunger drive.
  • Fig. 4 shows a section along line XX in Fig. 1 in a variant of the punching press according to the invention.
  • This variant differs from the variant according to Figures 2 and 3 in that the auxiliary connecting rods 5c, 5d and the passive connecting rods 3a, 3b are formed by separate components.
  • auxiliary connecting rods 5c, 5d and the active connecting rods 9a, 9b are formed by common components, i.e. an active connecting rod 9a or 9b and an auxiliary connecting rod 5c or 5d are combined to form a common, one-piece component.
  • This is implemented in such a way that the eccentric shaft-side eye 16 of the respective passive connecting rod 9a, 9b also forms the eccentric shaft-side eye of the associated auxiliary connecting rod 5c, 5d, and that an auxiliary eye 15c, 15d is formed on the side of this eye 16, which is that of the eccentric shaft 1a, 1b forms the eye of the respective auxiliary connecting rod 5c, 5d.
  • the active connecting rods 9a, 9b and also the auxiliary connecting rods 5c, 5d are each designed here as pairs of connecting rods.
  • the passive connecting rods 3a, 3b are designed separately from the active connecting rods 9a, 9b.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Presses And Accessory Devices Thereof (AREA)

Claims (19)

  1. Presse à poinçonner avec une manivelle ou un excentrique, comprenant un vilebrequin ou un arbre excentrique (1a, 1b) et des bielles actives (9a, 9b) pour générer le mouvement de course du coulisseau de presse (13), et avec des poids d'équilibrage (2a, 2b) pour équilibrer les forces de masse verticales et horizontales,
    la presse à poinçonner étant conçue de telle sorte que les mouvements d'entraînement horizontaux nécessaires à l'équilibrage des masses horizontales sont prélevés directement sur le vilebrequin ou l'arbre excentrique (1a, 1b),
    la presse à poinçonner étant conçue de manière à ce que chacun des poids d'équilibrage (2a, 2b) serve à équilibrer les forces de masse horizontales ainsi que les forces de masse verticales,
    caractérisée en ce que la presse à poinçonner est adaptée de manière à ce que les mouvements d'entraînement nécessaires à l'équilibrage vertical des masses soient prélevés directement sur le vilebrequin ou l'arbre excentrique (1a, 1b), en particulier au-dessus du vilebrequin ou de l'arbre excentrique (1a, 1b).
  2. Presse à poinçonner selon l'une des revendications précédentes, dans laquelle la presse à poinçonner est adaptée de telle sorte que les mouvements d'entraînement nécessaires à l'équilibrage horizontal des masses sont prélevés par l'intermédiaire de composants (5a, 5b ; 6a, 6b ; 7a, 7b ; 8a, 8b) sur le vilebrequin ou l'arbre excentrique (1a, 1b) et sont transmis aux masses d'équilibrage (2a, 2b), qui sont formées séparément à partir de composants (9a, 9b ; 10a, 10b ; 12a, 12b) servant à l'entraînement du coulisseau.
  3. Presse à poinçonner selon l'une des revendications précédentes, dans laquelle la presse à poinçonner est adaptée de manière à ce que tous les mouvements d'entraînement nécessaires à l'équilibrage des masses soient prélevés par l'intermédiaire de composants (3a, 3b, 4a, 4b, 5a, 5b ; 6a, 6b ; 7a, 7b ; 8a, 8b) sur le vilebrequin ou l'arbre excentrique (1a, 1b) et sont transmis aux masses d'équilibrage (2a, 2b), qui sont formées séparément à partir des composants (9a, 9b ; 10a, 10b ; 12a, 12b) servant à l'entraînement du coulisseau.
  4. Presse à poinçonner selon l'une des revendications précédentes, dans laquelle la presse à poinçonner est adaptée de manière à ce que les mouvements d'entraînement nécessaires à l'équilibrage horizontal des masses soient prélevés par l'intermédiaire de bielles auxiliaires (5a, 5b, 5c, 5d) s'engageant sur le vilebrequin ou l'arbre excentrique.
  5. Presse à poinçonner selon la revendication 4, dans laquelle la presse à poinçonner est adaptée de telle sorte que les bielles auxiliaires (5a, 5b, 5c, 5d) s'étendent à partir du vilebrequin ou de l'arbre excentrique (1a, 1b) dans une direction transversale à la direction de mouvement prévue (S) du coulisseau de presse (13) .
  6. Presse à poinçonner selon la revendication 5, dans laquelle les extrémités des bielles auxiliaires (5a, 5b, 5c, 5d) tournées vers l'extérieur du vilebrequin ou de l'arbre excentrique (1a, 1b) sont chacune couplées, en particulier articulées, à une extrémité d'un double levier monté pivotant (6a, 6b), dont la seconde extrémité est couplée, en particulier articulée, directement ou par l'intermédiaire d'autres éléments de couplage (7a, 7b) à un poids d'équilibrage (2a, 2b) pour l'équilibrage horizontal de la masse.
  7. Presse à poinçonner selon la revendication 6, dans laquelle les extrémités des bielles auxiliaires (5a, 5b, 5c, 5d) tournées vers l'extérieur du vilebrequin ou de l'arbre excentrique (1a, 1b) sont chacune couplées par une liaison (8a, 8b) à l'extrémité du double levier respectif monté pivotant (6a, 6b).
  8. Presse à poinçonner selon l'une des revendications 6 à 7, dans laquelle la deuxième extrémité du double levier respectif monté pivotant (6a, 6b) est couplée dans chaque cas par une liaison (7a, 7b) au poids d'équilibrage respectif (2a, 2b) pour l'équilibrage horizontal de la masse.
  9. Presse à poinçonner selon l'une des revendications 4 à 8, dans laquelle les bielles auxiliaires (5a, 5b) et les bielles actives (9a, 9b) sont constituées de composants séparés.
  10. Presse à poinçonner selon l'une des revendications 4 à 8, dans laquelle les bielles auxiliaires (5c, 5d) et les bielles actives (9a, 9b) sont formées par des composants communs.
  11. Presse à poinçonner selon l'une des revendications précédentes, dans laquelle la presse à poinçonner est adaptée de manière à ce que les mouvements d'entraînement nécessaires à l'équilibrage vertical de la masse soient pris par des bielles passives (3a, 3b) s'engageant sur le vilebrequin ou l'arbre excentrique (1a, 1b) .
  12. Presse à poinçonner selon la revendication 11, dans laquelle la presse à poinçonner est adaptée de telle sorte que les bielles passives (3a, 3b) s'étendent à partir du vilebrequin ou de l'arbre excentrique (1a, 1b) dans une direction s'éloignant du coulisseau de presse (13).
  13. Presse à poinçonner selon la revendication 12, dans laquelle les extrémités des bielles passives (3a, 3b) s'éloignant du vilebrequin ou de l'arbre excentrique (1a, 1b) sont chacune articulées à une extrémité d'un double levier monté pivotant (4a, 4b), dont la seconde extrémité est articulée directement ou par l'intermédiaire d'autres éléments d'accouplement à un poids d'équilibrage (2a, 2b) pour l'équilibrage vertical de la masse.
  14. Presse à poinçonner selon la revendication 13, dans laquelle le poids d'équilibrage respectif (2a, 2b) pour l'équilibrage vertical de la masse est supporté par l'extrémité respective du double levier respectif (4a, 4b).
  15. Presse à poinçonner selon l'une des revendications 4 à 9 et selon l'une des revendications 11 à 14, dans laquelle les bielles auxiliaires (5a, 5b) et les bielles passives (3a, 3b) sont formées par des composants communs.
  16. Presse à poinçonner selon l'une des revendications 4 à 10 et selon l'une des revendications 11 à 14, dans laquelle les bielles auxiliaires (5c, 5d) et les bielles passives (3a, 3b) sont formées par des composants séparés.
  17. Presse à poinçonner selon l'une des revendications 4 à 10 et selon l'une des revendications 11 à 16, dans laquelle les bielles auxiliaires (5a, 5b, 5c, 5d), les bielles passives (3a, 3b) et/ou les bielles actives (9a, 9b) sont montées sur un maneton commun du vilebrequin ou sur un excentrique commun de l'arbre excentrique (1a, 1b).
  18. Presse à poinçonner selon l'une des revendications précédentes, dans laquelle les masses d'équilibrage (2a, 2b) sont disposées de part et d'autre du vilebrequin ou de l'arbre excentrique (1a, 1b) pour l'équilibrage horizontal des masses.
  19. Presse à poinçonner selon l'une des revendications précédentes, dans laquelle la presse à poinçonner est adaptée de telle sorte que les bielles actives (9a, 9b) s'étendent à partir du vilebrequin ou de l'arbre excentrique (1a, 1b) en direction du coulisseau de presse (13), les extrémités des bielles actives (9a, 9b) opposées au vilebrequin ou à l'arbre excentrique (1a, 1b) sont chacune articulées à une extrémité d'un levier unilatéral (10a, 10b), dont l'autre extrémité est montée de manière articulée sur la carcasse (11) de la presse à poinçonner, soit directement, soit par l'intermédiaire d'autres éléments de couplage, et dans lequel une manille de poussée (12a, 12b), qui est reliée au coulisseau de la presse (13), est articulée à chacun des leviers unilatéraux (10a, 10b) dans une zone située entre leurs deux extrémités.
EP19718349.4A 2019-04-16 2019-04-16 Presse à estamper Active EP3938196B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2019/059833 WO2020211931A1 (fr) 2019-04-16 2019-04-16 Presse à estamper

Publications (2)

Publication Number Publication Date
EP3938196A1 EP3938196A1 (fr) 2022-01-19
EP3938196B1 true EP3938196B1 (fr) 2023-12-13

Family

ID=66223738

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19718349.4A Active EP3938196B1 (fr) 2019-04-16 2019-04-16 Presse à estamper

Country Status (5)

Country Link
US (1) US20220212431A1 (fr)
EP (1) EP3938196B1 (fr)
JP (1) JP7377889B2 (fr)
ES (1) ES2970790T3 (fr)
WO (1) WO2020211931A1 (fr)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0455988B1 (fr) * 1990-05-09 1993-10-06 Bruderer Ag Dispositif pour l'équilibrage des forces inertielles dans une machine à poinçonner
JPH07121474B2 (ja) * 1987-09-14 1995-12-25 京利工業株式会社 プレス機

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH427442A (de) * 1965-12-02 1966-12-31 Bruderer Ag Vorrichtung für den Massenausgleich bei durch Kurbeltrieb angetriebenen Maschinen
CH543375A (de) * 1971-10-01 1973-10-31 Bruderer Ag Einrichtung zur Führung des Bärs einer Stanzmaschine
CH543376A (de) * 1971-10-01 1973-10-31 Bruderer Ag Vorrichtung für den Massenausgleich an einer Stanzmaschine
DE2434266A1 (de) * 1974-07-17 1976-01-29 Haulick Fa Hermann Vorrichtung fuer den massenausgleich bei pressen
CH581281A5 (fr) 1974-09-03 1976-10-29 Bruderer Ag
JPH02258200A (ja) * 1989-03-30 1990-10-18 Sankyo Seisakusho:Kk 動的釣り合い機構を有するプレス機械
CH679471A5 (fr) * 1989-05-03 1992-02-28 Bruderer Ag
DE59303264D1 (de) * 1993-06-04 1996-08-22 Bruderer Ag Einwellen-Vierpunkt-Stanzpresse
DE59700425D1 (de) * 1997-12-12 1999-10-14 Bruderer Ag Presse, insbesondere Stanzpresse

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07121474B2 (ja) * 1987-09-14 1995-12-25 京利工業株式会社 プレス機
EP0455988B1 (fr) * 1990-05-09 1993-10-06 Bruderer Ag Dispositif pour l'équilibrage des forces inertielles dans une machine à poinçonner

Also Published As

Publication number Publication date
WO2020211931A1 (fr) 2020-10-22
JP2022532481A (ja) 2022-07-15
EP3938196A1 (fr) 2022-01-19
US20220212431A1 (en) 2022-07-07
ES2970790T3 (es) 2024-05-30
JP7377889B2 (ja) 2023-11-10

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