EP0696960B1 - Module porte-outils entraine par une presse, notamment unite de decoupage transversal ou de pliage entrainee par une presse - Google Patents

Module porte-outils entraine par une presse, notamment unite de decoupage transversal ou de pliage entrainee par une presse Download PDF

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Publication number
EP0696960B1
EP0696960B1 EP19930908821 EP93908821A EP0696960B1 EP 0696960 B1 EP0696960 B1 EP 0696960B1 EP 19930908821 EP19930908821 EP 19930908821 EP 93908821 A EP93908821 A EP 93908821A EP 0696960 B1 EP0696960 B1 EP 0696960B1
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EP
European Patent Office
Prior art keywords
working
cylinder
tool module
module according
tool
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
EP19930908821
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German (de)
English (en)
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EP0696960A1 (fr
Inventor
Wolfgang Katz
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Danly Corp
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Danly Corp
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Filing date
Publication date
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Publication of EP0696960A1 publication Critical patent/EP0696960A1/fr
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Publication of EP0696960B1 publication Critical patent/EP0696960B1/fr
Anticipated expiration legal-status Critical
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • 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
    • B21D28/00—Shaping by press-cutting; Perforating
    • B21D28/002—Drive of the 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
    • B30B1/007—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 using a fluid connection between the drive means and the press ram
    • 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
    • B30B1/32—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 plungers under fluid pressure
    • 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
    • Y10T83/00—Cutting
    • Y10T83/869—Means to drive or to guide tool
    • Y10T83/8776—Constantly urged tool or tool support [e.g., spring biased]
    • Y10T83/8785—Through return [noncutting] stroke

Definitions

  • the invention relates to a press-driven tool module, in particular a press-driven transverse punching or bending unit according to the preamble of claim 1.
  • Comparable tool modules are known, for example, from the "MILFAB” brochure from Danly Deutschland GmbH. They have a plunger to which a tool, for example a punching or bending tool, can be attached.
  • the tappet is slidably mounted in a guide bush of a base body. The direction of movement is through the The arrangement of the guide bush is predetermined and runs horizontally.
  • a helical spring is attached either inside or outside of the base body and coupled to the plunger in such a way that it counteracts the displacement of the plunger and serves as a return spring.
  • the plunger is actuated by a rocker arm on its end facing away from the tool. This is pivotally mounted in the base body and is acted upon vertically by a press ram.
  • the rocker arm Due to the downward movement of the press ram during the working stroke, the rocker arm swivels about its axis and presses the ram carrying the tool forward in the horizontal direction. After the punching or bending process has ended, the return stroke of the press ram and the return movement of the ram carrying the tool take place as a result of the action of the return spring.
  • the return spring is necessary because the press ram is not firmly connected to the rocker arm. Rather, the press ram generally has no contact with the rocker arm in the area of its top dead center position.
  • Such tool modules have been widely used because they can be used universally in all common presses. They will be fixed there at the desired location. For this purpose, various mounting options, such as. B. holes, feather keys or shoulders arranged.
  • the rocker arm which acts as a force-deflecting element, is subject to very heavy wear, because the pivot axis has to absorb the transmitted high forces.
  • This further relates to the sliding surfaces of the rocker arm which are in contact with the press ram and the ram carrying the tool.
  • Such tool modules also offer in terms of Their arrangement possibility in the case of a required multiple arrangement little flexibility, since usually only one rocker arm can be actuated by the press ram. Therefore, complex designs are often required in order to operate several tools simultaneously using a central rocker arm. Once a geometric configuration has been preselected, it must generally be retained; even minor modifications in the geometry require the special production of a new tool module.
  • the invention was therefore based on the problem of further developing a press-driven tool module, in particular a press-driven transverse punching or bending unit of the type mentioned at the outset, in such a way that the problems described no longer occur.
  • the energy introduced by the press should be optimally implemented with the least possible technical outlay and adapted to the deformation process.
  • the invention is based on the idea of using the kinetic energy of the press ram to put the hydraulic medium under high pressure only briefly in each case, so that the desired punching and bending process can be carried out. Otherwise, the hydraulic medium is essentially depressurized.
  • a reservoir for the hydraulic medium is provided in the power cylinder, which has a connection to the displacement chamber in the top dead center position of the piston, but otherwise, d. H. at a position of the piston which deviates from the top dead center position, is sealed against high pressure with respect to the displacement space.
  • the tool module according to the invention offers the possibility of attaching the work unit carrying the tool and the force unit that pressurizes the hydraulic medium in a spatial separation from one another, the two subunits being connected by a high-pressure line. In this way it is possible to actuate several work units simultaneously by a single common force unit.
  • the position of each work unit can be changed without any significant effort.
  • the direction of machining can also be realized not only purely horizontally, but deviating therefrom in any angular position.
  • a gas spring element is integrated in the working unit as a return spring, which is integrated within the cylinder space as well as optionally within the piston and the piston rod without taking up additional space.
  • a coil spring can also be provided as an inexpensive alternative will.
  • the tool module consists of two sub-units, namely a working cylinder A and a power cylinder K.
  • the working cylinder A has a base body 33 with a cylindrical bore.
  • a working piston 10 is slidably disposed in the cylindrical bore.
  • a piston rod 9 is attached, which carries a tool 18 in the form of a stamp on the end face.
  • the piston rod 9 is also slidably guided in a bearing bush 11 which closes off the base body 33.
  • the guide bush 11 is screwed to the base body 33.
  • the guide bush 11 projects with a shoulder web 34 into the interior of the cylinder bore of the base body 33.
  • a sealing ring 35 is attached, the function of which is explained in more detail below.
  • the displacement of the working piston 10 is limited, on the one hand, by the abutment against the base 33 and, on the other hand, by the abutment on the shoulder 34 of the bearing bush 11.
  • the distance between these two end positions is the stroke H A of the working piston 10 and thus corresponds to the amount of the maximum displacement of the Tool 18.
  • the working space 22 is hereby defined as the axial section of the cylinder bore of the base body 33.
  • the working piston 10 is provided with a high-pressure seal 5, so that the working space 22 is sealed at a high pressure at this point between the working piston 10 and the cylinder bore of the base body 33.
  • the power cylinder K has a base block 1, on which a guide block 2 is placed and screwed tightly to it.
  • the guide block 2 has a through hole into which the slide bush 27 is inserted.
  • the sliding bush 27 takes over the guidance of a piston rod 3, which is attached to a plunger 23.
  • the bore receiving the piston rod 3 merges in the interior of the guide block 2 into a cylindrical bore of larger diameter, which is provided with an internal thread 36.
  • the internal thread 36 is in engagement with an external thread 37 which an upwardly facing heel ring 38 of the base block 1 is attached.
  • a cylinder bore is provided in the base block, which essentially represents the displacement space 24 and merges upwards into the cylinder bore of the guide block 2.
  • the diameter of the cylinder bore of the guide block 2 is larger than the outer diameter of the plunger 23, so that an annular space 26 remains between the plunger 23 and the guide block 2.
  • the diameter of the cylinder bore is matched to the diameter of the plunger 23.
  • the diameter of the cylinder bore in the base block 1 increases slightly in the manner of a recess. From here a bore 25 goes off, which connects the displacement space 24 with the working space 22 of the working cylinder A.
  • the displacement space 24, the bore 25, the working space 22 and parts of the annular space 23 are filled with hydraulic medium M. It is a medium viscosity oil.
  • the annular space 26 has a connection with the displacement space 24, so that a continuous liquid column is created from the displacement space 24 to the annular space 26.
  • hydraulic medium M can be supplemented via the filler valve 10, which is not shown here.
  • a vent hole 30 opening into the working space 22 is provided, which can be sealed with a vent screw 12.
  • the liquid level in the power cylinder rises until finally the entire annular space 26 is filled and thus the function of a storage space for the hydraulic medium M.
  • the storage space 26 is separated from the displacer space 24. This is ensured by a high-pressure ring seal 4, which is mounted in the heel ring 38 of the base block 1 and tightly encloses the plunger 23.
  • a gas spring element is integrated in the working cylinder A.
  • the annular space is used, which lies in the radial direction between the piston rod 9 and the cylinder bore of the working cylinder A and in the axial direction between the working piston 10 and the bearing bush 11.
  • This area is made gas-tight in that the working piston 10 is provided with a gas seal 6 and the bearing bush 11 with the gas seal 7, which seals the transition from the piston rod 9 to the bearing bush 11.
  • the seal 35 mentioned above seals the transition from the base body 33 to the bearing bush 11.
  • the annular space 31 is filled with nitrogen gas under high pressure. Moving the working cylinder 10 out of the starting position shown in FIG. 1 to the right reduces the volume of the annular space 31, and the gas therein is compressed.
  • the gas relaxes and presses the working piston 10 back into its starting position.
  • the interior of the piston 10 and the piston rod 9 are largely drilled out, so that a common cavity 32 results which has a connection 16 to the annular space 31.
  • the cavity 32 and the bore 16 are also filled with gas.
  • the desired spring characteristic can be achieved by appropriate dimensioning of the cavity. This enables an extremely compact design, since the gas spring element is completely inside the working cylinder A is integrated.
  • the gas filling can be introduced through a gas valve 8 (not shown in detail) or can be supplemented if necessary.
  • FIG. 1 The starting point as the start of a machining cycle is shown in FIG. 1. This is a punching process in which a hole is to be punched in a workpiece 20.
  • the workpiece 20 is held by a die 21, which in turn is attached to a support plate 19.
  • a press ram 17 of a press is in its top dead center position.
  • the tool 18 is in the retracted position, the working piston 10 abutting on the end face inside the cylinder bore of the base body 33 due to the action of the gas spring element.
  • the displacer 23 is held against the shoulder of the guide block 2 via the hydraulic medium M.
  • the displacement piston 23 has no contact with the high-pressure ring seal 4, so that a continuous liquid column has formed in the displacement space 24 and in the storage space 26.
  • the press ram 17 begins its downward movement and hits the piston rod 3. Due to the further downward movement of the press ram 17, the displacer 23 is forced vertically downward via the piston rod 3. It comes into contact with the high-pressure ring seal 4 after a short distance, so that from then on the displacement space 24 is sealed off from the storage space 26. Through the further downward movement of the plunger 23 increases the pressure of the hydraulic medium M, which is located in the displacement chamber 24 and in the bore 25. When the pressure rises further, the working piston 10 is first shifted to the right against the action of the gas suspension element (in the illustration according to FIGS. 1 and 2). The pressure build-up in the hydraulic medium M initially moves in the low-pressure range, since only the working piston 10 carries out a displacement movement and the tool 18 is thus delivered.
  • the press ram 17 has reached its lowest position, bottom dead center (UT) and is about to reverse its direction of movement and move upward. This enables the displacement piston 23 to return to its starting position. Since the piston rod 3 is not connected to the press ram 17, the return stroke of the plunger 23 is effected by the return stroke of the working piston 10. This is ensured by the integrated gas spring element, which was compressed as a result of the displacement of the working cylinder 10 and can now expand again. As a result of the expansion, the working piston 10 becomes contact with the cylinder bore in the base body 33 on the end face brought so that the position indicated in Figure 1 is reached again.
  • a height-adjustable mechanical stop 15 is attached to the end of the guide block 2 and serves as a stroke limitation for the press ram 17 and thus for the displacement piston 23. It is intended to prevent the plunger 23 from accidentally penetrating too deeply into the displacement chamber 24 and thereby causing the pressure in the hydraulic medium M to rise to an impermissibly high value. This virtually eliminates operating errors.
  • a burst protection device can be provided in areas leading hydraulic medium (M), for example in the area of the bore 25.
  • the low-pressure valve 13 ensures pressure equalization if the overpressure or underpressure generated as a result of the displacement movement of the plunger 23 exceeds predetermined limits. It also prevents overfilling with hydraulic medium M.
  • a spatially separate arrangement of the power cylinder K and the working cylinder A is also possible without loss of function, the bore 25 being replaced by a high-pressure line.
  • a plurality of working cylinders A can also be connected to the power cylinder K, the high pressure lines of which are coupled to the power cylinder either individually or via a multiple coupling. Especially when using a flexible line as a high-pressure line, a completely variable and freely configurable configuration can be realized.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Presses And Accessory Devices Thereof (AREA)
  • Press Drives And Press Lines (AREA)
  • Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)
  • Actuator (AREA)

Abstract

Dans un module porte-outils entraîné par une presse, notamment une unité de découpage transversal ou de pliage entraîné par une presse, un outil (18) montable sur un coulisseau (9) est monté mobile dans n'importe quelle direction voulue à l'encontre de l'action d'un ressort pneumatique intégré de rappel, et le coulisseau (9) qui porte l'outil peut être actionné par le coulisseau (17) d'une presse mobile dans le sens vertical. A cet effet, un piston plongeur (23) verticalement guidé dans un cylindre de force (K) peut être actionné par le coulisseau (17) de la presse au moyen d'une tige de piston (3) et agit sur un fluide hydraulique (M) dans une chambre de refoulement sous-jacente (24). La chambre de déplacement (24) est reliée par une conduite haute pression (25) à la chambre de travail (22) d'un cylindre de travail (A) dont la tige de piston (9) porte l'outil. Dans un mode préféré de réalisation, le cylindre de force (K) et le cylindre de travail (A) peuvent être montés à des endroits séparés et reliés l'un à l'autre par une conduite flexible haute pression.

Claims (16)

  1. Module porte-outil entraîné par une presse, notamment élément d'estampage ou de cintrage, comportant un outil (18) susceptible d'être fixé à un poussoir (9), notamment à un outil d'estampage ou de cintrage, monté dans un corps de base (33), coulissant contre l'action d'un élément à ressort de rappel, dans une direction différente de la direction verticale, notamment dans une direction horizontale,
    - le poussoir portant l'outil (18) est constitué par un poussoir (9) d'un piston de travail (10) sollicité par un liquide hydraulique (M), ce piston coulissant dans la chambre de travail (22) d'un vérin de travail (A),
    - le liquide hydraulique (M) de la chambre de refoulement (24) d'un vérin de force (K) étant sollicité par un piston (23) guidé verticalement dans le vérin de force (K), ce piston étant actionné lui-même par le poussoir de presse (17) à partir d'une tige de piston (3), et
    - entre la chambre de refoulement (24) du vérin de force (K) et la chambre de travail (22) du vérin de travail (A), il est prévu une liaison hydraulique sous la forme d'une conduite haute pression (25) pour le liquide hydraulique (M),
    caractérisé en ce que
    le vérin de force (K) comporte une chambre d'alimentation (26) pour le liquide hydraulique (M) qui, lorsque le piston (23) occupe son point mort haut (O.T.), communique avec la chambre de refoulement (24) du vérin de force (K) alors que pour toute autre position il est fermé de manière étanche à la haute pression par rapport à la chambre de refoulement (24).
  2. Module porte-outil selon la revendication 1,
    caractérisé en ce que
    le piston (23) est un piston plongeur et le vérin de force (K) comporte un bloc de base (1) et un bloc de guidage (2) relié au bloc de base (1), un alésage cylindrique étant prévu dans le bloc de base (1) qui forme pour l'essentiel la chambre de refoulement (24) et porte dans sa zone supérieure un joint annulaire haute pression (4) mis en appui radial contre le piston plongeur (23) dans la mesure où celui-ci se trouve dans une position différente de sa position de point mort haut (O.T.) et en outre le bloc de guidage (2) comporte un alésage cylindrique dont le diamètre est supérieur à celui de l'alésage cylindrique du bloc de base (1) pour former la chambre d'alimentation (26) du liquide hydraulique (M) au-dessus de la chambre de refoulement (24) et rejoignant celle-ci.
  3. Module porte-outil selon la revendication 2,
    caractérisé en ce que
    le bloc de guidage (2) est une douille de glissement (27) pour guider la tige de piston (3).
  4. Module porte-outil selon la revendication précédente,
    caractérisé en ce que
    le vérin de force (K) comporte, à sa surface frontale (28) tournée vers le coulisseau de presse (17), une butée (15) mécanique, ajustable en hauteur, pour limiter la course du coulisseau de presse (17).
  5. Module porte-outil selon l'une des revendications précédentes,
    caractérisé en ce qu'
    un perçage d'équilibrage de pression (29), muni d'une soupape basse pression (13), débouche par le haut dans la chambre d'alimentation (26).
  6. Module porte-outil selon l'une des revendications précédentes,
    caractérisé en ce qu'
    un perçage de purge (30) débouche par le haut dans la chambre de travail (22), ce perçage pouvant être fermé de manière étanche par une vis de purge (12).
  7. Module porte-outil selon l'une des revendications précédentes,
    caractérisé en ce que
    l'alésage du vérin de travail (A) est fermé du côté de l'outil par une douille de palier (11) guidant la tige de piston (9).
  8. Module porte-outil selon l'une des revendications précédentes,
    caractérisé en ce que
    l'élément à ressort de rappel est un ressort hélicoïdal.
  9. Module porte-outil selon l'une des revendications 1 à 7,
    caractérisé en ce que
    l'élément à ressort de rappel est un élément à ressort à gaz.
  10. Module porte-outil selon la revendication 9,
    caractérisé en ce que
    l'élément à ressort à gaz est constitué par au moins une chambre annulaire (31) remplie de gaz (G) qui se situe dans la direction radiale, entre la tige de piston (9) et l'alésage du vérin de travail (A) et dans la direction axiale, entre le piston de travail (10) et la douille de palier (11).
  11. Module porte-outil selon la revendication 10,
    caractérisé en ce que
    la chambre annulaire (31) est reliée par un perçage (16) du piston de travail (10) ou de la tige de piston (9) avec une cavité (32), commune, à l'intérieur du piston de travail (10) et de la tige de piston (9).
  12. Module porte-outil selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le vérin de force (K) et le vérin de travail (A) forment un ensemble indissociable.
  13. Module porte-outil selon l'une des revendications 1 à 11,
    caractérisé en ce que
    le vérin de force (K) et le vérin de travail (A) constituent chacun une unité manipulée indépendamment et qui sont reliés par une conduite haute pression, distincte.
  14. Module porte-outil selon la revendication 13,
    caractérisé en ce que
    la conduite haute pression distincte est un tuyau souple.
  15. Module porte-outil selon l'une des revendications 12 à 14,
    caractérisé par
    un grand nombre de vérins de travail (A) couplés simultanément sur le vérin de force (K).
  16. Module porte-outil selon l'une des revendications précédentes,
    caractérisé en ce que
    la tige de piston (9) est munie d'une installation de montage rapide pour recevoir l'outil (18).
EP19930908821 1993-04-26 1993-04-26 Module porte-outils entraine par une presse, notamment unite de decoupage transversal ou de pliage entrainee par une presse Expired - Lifetime EP0696960B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/DE1993/000370 WO1994025260A1 (fr) 1993-04-26 1993-04-26 Module porte-outils entraine par une presse, notamment unite de decoupage transversal ou de pliage entrainee par une presse

Publications (2)

Publication Number Publication Date
EP0696960A1 EP0696960A1 (fr) 1996-02-21
EP0696960B1 true EP0696960B1 (fr) 1997-03-26

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19930908821 Expired - Lifetime EP0696960B1 (fr) 1993-04-26 1993-04-26 Module porte-outils entraine par une presse, notamment unite de decoupage transversal ou de pliage entrainee par une presse

Country Status (8)

Country Link
US (1) US5606910A (fr)
EP (1) EP0696960B1 (fr)
JP (1) JPH08508681A (fr)
KR (1) KR960701740A (fr)
DE (2) DE59306000D1 (fr)
ES (1) ES2100530T3 (fr)
FR (1) FR2704478B3 (fr)
WO (1) WO1994025260A1 (fr)

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AT505160B1 (de) * 2007-05-30 2008-11-15 Bogner Fritz Mag Hydrauliksystem
AT505440B1 (de) * 2007-05-30 2009-03-15 Bogner Fritz Mag Hydrauliksystem

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US10532481B2 (en) * 2015-11-25 2020-01-14 Ridge Tool Company Punch tool system
ES2686989T3 (es) * 2015-12-14 2018-10-23 Nitrogas, S.A.U. Dispositivo hidráulico de actuación para una prensa
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DE102020000238B4 (de) 2020-01-16 2022-08-04 Fritz Stepper GmbH & Co. KG. Kernstation
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AT505160B1 (de) * 2007-05-30 2008-11-15 Bogner Fritz Mag Hydrauliksystem
AT505440B1 (de) * 2007-05-30 2009-03-15 Bogner Fritz Mag Hydrauliksystem

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Publication number Publication date
WO1994025260A1 (fr) 1994-11-10
ES2100530T3 (es) 1997-06-16
KR960701740A (ko) 1996-03-28
FR2704478B3 (fr) 1995-03-24
DE9405764U1 (de) 1994-06-01
JPH08508681A (ja) 1996-09-17
EP0696960A1 (fr) 1996-02-21
US5606910A (en) 1997-03-04
FR2704478A3 (fr) 1994-11-04
DE59306000D1 (de) 1997-04-30

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