EP0417752B1 - Presse mécanique ou hydraulique avec dispositif d'étirage ou d'emboutissage pour presse à plusieurs étapes - Google Patents

Presse mécanique ou hydraulique avec dispositif d'étirage ou d'emboutissage pour presse à plusieurs étapes Download PDF

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Publication number
EP0417752B1
EP0417752B1 EP90117535A EP90117535A EP0417752B1 EP 0417752 B1 EP0417752 B1 EP 0417752B1 EP 90117535 A EP90117535 A EP 90117535A EP 90117535 A EP90117535 A EP 90117535A EP 0417752 B1 EP0417752 B1 EP 0417752B1
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EP
European Patent Office
Prior art keywords
piston
sheet metal
pressure
metal holder
cylinder unit
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
EP90117535A
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German (de)
English (en)
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EP0417752A2 (fr
EP0417752A3 (en
Inventor
Erich Harsch
Hans Engelhardt
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.)
Maschinenfabrik Mueller Weingarten AG
Mueller Weingarten AG
Original Assignee
Maschinenfabrik Mueller Weingarten AG
Mueller Weingarten 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 Maschinenfabrik Mueller Weingarten AG, Mueller Weingarten AG filed Critical Maschinenfabrik Mueller Weingarten AG
Publication of EP0417752A2 publication Critical patent/EP0417752A2/fr
Publication of EP0417752A3 publication Critical patent/EP0417752A3/de
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Publication of EP0417752B1 publication Critical patent/EP0417752B1/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
    • B21D24/10—Devices controlling or operating blank holders independently, or in conjunction with dies
    • 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 mechanical or hydraulic press with a pulling device or drawing step of a step press according to the preamble of claim 1.
  • sheet metal holder a special sheet metal counterholder - hereinafter referred to as "sheet metal holder” - and the descending upper tool.
  • the force exerted by the plunger during the decline must counteract a counterforce via a yielding cushion.
  • the counterforce is applied to the sheet metal holder by an underlying pressure cheek - also known as a pressure cushion or die cushion.
  • the amount of work required which is applied as a counterforce to the sheet metal holder by means of a die cushion loaded with air or hydraulic medium, is measured from the product counterforce times the way. Due to the tappet force acting on the sheet metal holder from above, part of the energy becomes one Counter force for the sheet metal holder supply stored and can relieve the drive as a restoring force on the ram after the pulling process, when the die cushion and the plunger rises again. If the die cushion is held back in its lower position and raised again under pressure control, the entire energy generated when the ram and the sheet metal holder are lowered is converted into heat. Large presses are very large amounts of energy. For example, with a sheet metal holder force of 4,000 kN, a stroke of 200 mm occurs at a stroke rate of 15 per minute. a power loss of 196 kW.
  • the central piston-cylinder unit must, on the one hand, carry out large strokes with the press ram movement due to the rigid connection via the tie rods. On the other hand, it must exert high opposing forces during the actual sheet metal holding process. This requires complicated control systems that have to control large amounts of hydraulic medium at both low and high pressures. At the same time, the central piston-cylinder unit on the sheet metal holder frame must set the respective initial position of the sheet metal holder, which is not readily possible with the large lifting movements taking place.
  • the piston-cylinder units connected to the tie rods therefore serve the direct hydraulic bracing between the press ram and the sheet metal holder. This is through the direct direct mechanical coupling between the lower cross member, and the sheet holder.
  • the central or central piston-cylinder unit is designed as a pneumatic cylinder unit and serves only as an ejector mechanism after the pulling process has taken place.
  • the pulling device according to the invention which is defined by the combination of features of claim 1, has the advantage that a pulling device is created, the energy losses of which are greatly reduced.
  • This is achieved in particular by decoupling a pneumatic cylinder provided for lifting the die cushion with a sheet metal holder and several separate piston-cylinder units.
  • this corresponds initially to the solution according to DE-A-38 35 376.
  • the die cushion is only supported via a central central rod, which at the same time serves as a piston rod for the central piston-cylinder unit.
  • Different pressurization of the piston-cylinder units arranged on the side must be compensated for by a swinging cross-beam.
  • four hydraulic piston-cylinder units arranged in the corner points of a die cushion or a pressure cheek are provided in the present invention, which can act separately controlled on the die cushion and thus on the sheet metal holder.
  • the pressurization of these piston-cylinder units takes place in order to produce a specific bracing of the sheet metal holder.
  • the invention provides various options for controlling these piston-cylinder units.
  • the piston of the piston-cylinder units acting on the corners of the die cushion is designed as a piston which can be acted upon from both sides, the piston rod being guided out of the cylinder housing at the top and bottom with the same pressure gauge.
  • the printing medium can be moved very easily when the Pistons inside the cylinder housing are guided from top to bottom via a proportional valve.
  • the piston is held in place locally in the cylinder housing by closing the proportional valve, which causes the overall tensioning of the sheet metal holder.
  • An additional targeted and, if necessary, program-controlled pressurization of the lower piston surface by an additional control can compensate for leakage losses and / or lead to the targeted force application of the sheet metal holder.
  • the flow between the upper and the lower cylinder space of the piston-cylinder units supporting the pressure cheek is initially shut off by means of a separate piston-cylinder unit and subsequently the upper pressure chamber of the piston-cylinder units supporting the die cushion is shifted by a further displacement of the additional piston-cylinder unit can be pressurized.
  • the piston of the additional piston-cylinder unit can have a predetermined curve shape for a desired acceleration characteristic in its upper region. The time of triggering the acceleration can also be set.
  • An alternative embodiment is also advantageous in that further pressure is applied to the lower pressure chamber of the piston-cylinder units supporting the die cushion by a piston-cylinder unit connected to it, the displacement of the piston of this piston-cylinder unit by an adjustable stop taking place when the additional piston-cylinder unit arranged in the sheet metal holder frame and thus the associated piston are moved downward.
  • the drawing devices or presses 1 in FIGS. 1, 2 and 4 consist of a stationary press table 2 with a table support 3 for receiving the lower tool 4 for producing a workpiece, represented by the board 5 which has not yet been machined.
  • the board 5 is on a sheet metal holder 6 hung up, which is guided in the lower tool 4 with stamp 4 '.
  • the upper tool 7 is connected to the press ram 8.
  • the sheet metal holder 6 is supported by pressure bolts 9 on a pressure cheek 10 - also called pressure cushion or die cushion.
  • tension rods or connecting rods 12 are articulated on the press ram 8 via bolts 11, which in their lower region are in turn connected to a lower sheet metal holder frame 13 via bolts 11.
  • the sheet metal holder frame 13 is accordingly rigidly guided with the press ram 8 within the press table 2.
  • Four piston-cylinder units 14 to 16 are fixedly connected to the sheet metal holder frame 13, the cylinder being designated by reference number 14 and the piston rod numbering 15.
  • the piston 16 running in the cylinder 14 divides the inner pressure chamber 17 into an upper pressure chamber 18 and into a lower pressure chamber 19.
  • the piston rods 15 are firmly connected in their upper region to the underside of the die cushion 10 via a holder 20.
  • the die cushion 10 is thereby supported by four piston-cylinder units 14 to 16 in its corner regions, so that a targeted influence on the sheet metal holder of the sheet metal holder 6 is possible.
  • the pressure cheek 10 is guided in the press table 2 and is moved upwards by a central piston-cylinder unit 21 to 23, the cylinder stationary in the press table with reference number 21 and that in the cylinder housing Movable piston rod acting on the die cushion 10 is designated by reference number 22.
  • the piston itself is identified by reference number 23.
  • the piston-cylinder unit 21 to 23 is designed as a prestressed compressed air cylinder and is closed in the lower region by a flange 24.
  • the piston rod 22 is extended downward by the piston 23 through a further piston rod 25 with a smaller cross section, which projects downward through the flange 24 and is provided at its end with a further piston 26 in a cylinder housing 27.
  • the pressure chamber 28 arranged above the piston 26 is closed via a check valve 29 as a pressure chamber with a damping function and is used via a throttle circuit (not shown in more detail) to dampen the upward movement of the upper piston 23 before its upper end stop.
  • the pressure chamber 30 of the piston-cylinder unit 21 to 23 located below the piston 23 is prestressed with compressed air via the pressure line 31 and a proportional valve 32 with accumulator 33.
  • the further valve 34 serves to equalize the pressure.
  • the upper piston rod 15 is passed through the piston 16 in the piston-cylinder unit 14 to 16 and continued in the lower region in the pressure chamber 19 as a piston rod 15 '.
  • this piston rod region 15 ' is passed through the sheet metal holder frame 13 and attached to a cross member 35 at the lower end.
  • the 1 furthermore has a control piston 36, 37 integrated in the cylinder housing 14, the upper cylinder bore 36 in the cylinder housing 14 is arranged parallel to the cylinder space or pressure space 17 and extends downward through the sheet metal holder frame 13.
  • the continued in the sheet metal holder frame is designated 36 '.
  • the cylinder bore 36, 36 ' is penetrated from below by a piston rod 37 which is articulated to an actuator 38 for adjusting the starting position of the piston rod 37.
  • the height adjustment motor 38 is itself attached to the crossbar 35.
  • the press ram 8 moves with the upper tool 7 including the four tie rods 12 with the sheet metal holder frame 13 fastened thereon downward in the direction of the lower tool 4.
  • the four cylinder housings 14 connected to the sheet metal holder frame 13 likewise move downward, the hydraulic oil contained in the upper pressure chamber 18 of the piston-cylinder units 14 to 16 having to escape.
  • the upper pressure chamber 18 and the lower pressure chamber 19 of each piston-cylinder unit 14 to 16 are connected to one another via a pressure line 39 and a proportional valve 40, so that the pressure medium from the pressure chamber 18 into the pressure chamber 19 during the downward movement of the Cylinder housing 14 can flow without pressure.
  • the die cushion 10 itself is held in its upper position by the piston-cylinder unit 21 to 23, which is designed as a pneumatic cylinder unit, the pressure being applied via the proportional valve 32.
  • the upper stop is formed by the stop of the lower piston 26 of the lower hydraulic piston-cylinder unit 26, 27 serves as a damping unit. To maintain this position, only a slight pressure of the reservoir 33 is required.
  • the proportional valve 40 is closed shortly before the upper tool 7 is placed on the board 5 and thus on the sheet metal holder 6.
  • a pressure accumulator 42, 42 ' is opened by means of the proportional valve 41, which suddenly applies pressure to the lower pressure chamber 19, as a result of which the piston 16 and thus the die cushion 10 are pressed upwards.
  • the proportional valve 41 then also takes over, if necessary, a program-controlled regulation of the pressure curve of each individual piston-cylinder unit 14 to 16.
  • the components, which are also shown in FIG. 3a, are required as measurement and control variables.
  • FIG. 3b In the representation of the invention according to FIG. 1, in contrast to that according to FIG. 2, an additional acceleration device for the sheet metal holder 6 is provided.
  • the circuit diagram for this is shown in Fig. 3b.
  • the control piston 37 already described in FIG. 1 moves in one Cylinder bore 36 or 36 'upwards.
  • this upward movement of the control piston 37 represents a downward movement of the cylinder housing 14, connected to the downward movement of the press ram 8 and the sheet metal holder frame 13 in connection with the cylinder housings 14.
  • the control piston 37 is rigidly connected via the cross member 35 to the piston rods 15, 15 ' .
  • the upper part of the cylinder bore 36 is connected to the upper pressure chamber 18 via a pressure line 43 and to the lower pressure chamber 19 of the pressure chamber or cylinder chamber 17 via a lower line 44.
  • the flow of the pressure line 43 to the upper pressure chamber 18 can be controlled via a proportional valve 45 and a corresponding control valve 46.
  • Fig. 1 in the left piston-cylinder unit 14 to 16.
  • the right piston-cylinder unit 14 to 16 contains only a bare through hole 43 '.
  • the accelerator is used as follows: As already described in relation to FIG. 3a, when the press ram 8 and thus the cylinder housing 14 move downward, the pressure medium flows from the upper 18 into the lower pressure space 19 via the pressure line 39. Instead of the proportional valve 40 in FIG. 3a, the valve occurs in FIG. 3b 45, ie there is an inevitable piston control in the piston-cylinder unit 14 to 16.
  • the control piston 37 moves as a control rod synchronously and in the same direction as that Piston rod 15.
  • the basic setting, ie the height starting position of the control piston 37 is carried out by the servomotor 38.
  • the control piston 37 has a certain curve shape 47 at its upper end, which is designed as a control curve 47. In the figure, this control curve is only shown as a simple slope.
  • this acceleration process is shown again as a curve.
  • the X axis shows the angle of rotation of the rotating plunger drive, the Y axis the plunger stroke.
  • Curve 48 shows the tappet path. The bottom dead center is marked with UT.
  • the path of the die cushion 10 is shown at 49.
  • the inlet bore 44 to the lower pressure chamber 19 is closed by the control curve 47 of the control piston 37 and the die cushion 10 is accelerated by the amount a ⁇ 30 mm before the upper tool 7 touches the sheet holder 6 at point 51 at the angle of rotation X2.
  • the path of the die cushion 10 according to curve 49 is the same as the path of the sheet metal holder 6. This pre-acceleration dampens the impact of the upper tool on the sheet metal holder. From point 51 to point 52 then the sheet metal holder and the press ram moves over the same curve path 48 '.
  • the design of the piston-cylinder unit 14 to 16 is configured somewhat differently.
  • the lower piston rod 15 ', d. H. the control schemes shown in FIGS. 3a and 3b do not apply here.
  • the pressure medium therefore not only swings from the upper pressure chamber 18 into the lower pressure chamber 19, but is controlled from the outside.
  • the lower pressure chamber 19 ' is connected via a bore 55 to a further piston-cylinder unit 56 to 58, 56 representing the cylinder housing and 57 the piston rod.
  • the piston 58 runs in the cylinder housing 56.
  • the piston-cylinder unit 56 to 58 is firmly integrated in the sheet metal holding frame and moves with it.
  • the piston rod 57 hits a lower stop 59, the height position "h" of which can be adjusted via the servomotor 60.
  • the stop 59 with the servomotor 60 is arranged in a stationary manner in the press table 2.
  • the piston 58 is now pushed upward within the cylinder housing 56, which leads to an increase in pressure in the lower pressure chamber 19 'and thus to the actual sheet metal holder pressure.
  • the proportional valve 61 regulates the pressure in the lower pressure chamber 19 according to predetermined values. A path-dependent program-controlled pressurization of the sheet metal holder 6 is thus possible.
  • the clamped between the sheet metal holder 6 and the lower tool 7 5 initially moves during the distance s to the punch 4 'of the lower tool 4 before the actual drawing process begins. During this distance, the pressure in the piston-cylinder units 14 to 16 is increased by the piston-cylinder unit 56 to 58 built up, which forms the holding pressure for the sheet metal holder. Thereafter, no further energy is required on the sheet metal holder, except that which is required by the piston-cylinder unit 56 to 58 to compensate for any pressure losses.
  • the system is tense.
  • the pressure cheek 10 is moved upwards by the pneumatic piston-cylinder unit 21 to 23, the damping device of the hydraulic piston-cylinder unit 26, 27 damping the upper impact.
  • the oil column under the pressure piston 16 can then flow back into the accumulator 52 via the valve 53. This takes place during the upward movement of the press ram 8 and thus of the sheet metal holder frame 13 with the cylinder housing 14.
  • the pressure medium flows from the lower pressure chamber 19 into the upper pressure chamber 18 in this case.

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

Claims (9)

  1. Presse mécanique ou hydraulique, comportant un dispositif d'emboutissage (1) pour des travaux d'emboutissage ou un étage d'emboutissage d'une presse à étages, dans laquelle un serre-flan (6) est commandé et serré hydrauliquement, un coulisseau de presse (8) étant relié de façon commandée par une force, par l'intermédiaire d'au moins deux, en particulier quatre tirants (12), à un cadre de serre-flan (13) agencé au-dessous d'une face de pression (10), un vérin (21 à 23), relié à la face de pression (10) et agencé de façon centrale dans une table de presse (2), étant prévu, et l'alimentation en pression de la face de pression (10) et, ainsi, l'appui du serre-flan (6) après la mise en place du coulisseau de presse (8) étant réglables pendant le processus d'emboutissage,
    caractérisée en ce que la face de pression (10) peut être déplacée dans la position initiale supérieure, avant le processus d'emboutissage proprement dit, au moyen d'un vérin pneumatique (21 à 23), en ce que, sur le cadre de serre-flan (13), sont agencés quatre autres vérins hydrauliques (14 à 16), dont les tiges de piston supérieures (15) s'appuient aux quatre coins de la face de pression (10), pendant la descente commune du coulisseau de presse (8), des tirants (12), du cadre de serre-flan (13) et des cylindres (14), l'espace de pression (19) se trouvant au-dessous du piston (16) du vérin (14 à 16) se remplissant de fluide sous pression provenant de l'espace de pression supérieur (18) ou d'un accumulateur de pression séparé (52), et en ce qu'un serrage programmé, dépendant de la course, du serre-flan (6) est effectué, après la mise en place du coulisseau de presse (8) sur le serre-flan (6), par l'intermédiaire d'une alimentation en pression séparée du vérin (14 à 16) au moyen d'une commande à soupape proportionnelle (41,61).
  2. Presse selon la revendication 1,
    caractérisée en ce que le piston (16) du vérin (14 à 16) est réalisé en tant que piston pouvant être alimenté des deux côtés, en ce que le fluide hydraulique sous pression, avant le serrage du serre-flan (6), est amené de l'espace de pression supérieur (18) dans l'espace de pression inférieur (19) par l'intermédiaire d'une soupape proportionnelle (40), laquelle, lors de la mise en place d'un outil supérieur (7) fixé au coulisseau de presse (8) sur le serre-flan (6), est fermée, et en ce que le serrage du serre-flan (6) est effectué par une alimentation en pression réglable de l'espace de pression inférieur (19) au moyen d'un accumulateur (42, 42'), par l'intermédiaire d'une autre soupape proportionnelle (41).
  3. Presse selon la revendication 2,
    caractérisée en ce que l'alimentation en pression de l'espace de pression inférieur (19) et, ainsi, la force agissant sur le serre-flan sont commandées de façon programmée.
  4. Presse selon une des revendications précédentes,
    caractérisée en ce que la tige de piston supérieure (15) du vérin (14 à 16) est reliée à la face de pression (10) de façon mécanique ou commandée par une force.
  5. Presse selon une des revendications 1 à 4,
    caractérisée en ce que, pour engendrer une pré-accélération orientée vers le bas du serre-flan (6) avant que l'outil supérieur (7) entre au contact du serre-flan (6), un autre vérin (36,37), de préférence intégré dans le cylindre (14), est associé au vérin (14 à 16), vérin qui présente un piston de commande (37), l'espace de pression (36) reliant l'espace de pression supérieur (18) et l'espace de pression inférieur (19) du vérin (14 à 16) par l'intermédiaire de perçages ou de conduits de pression (43,44), et le piston de commande correspondant (37) étant solidaire de la tige de piston (15,15') et déplaçable dans le cylindre (36), et en ce que, peu avant que l'outil supérieur (7) entre au contact du serre-flan (6), le canal de liaison inférieur (44) vers l'espace de pression inférieur (19) peut être obturé au moyen d'une came de commande (47) et, lorsque la montée du piston de commande (37) à l'intérieur du perçage (36) se poursuit, une augmentation de pression se produit dans l'espace de pression supérieur (18) dans le sens d'une accélération en descente du serre-flan (6).
  6. Presse selon la revendication 5,
    caractérisée en ce que le piston de commande (37) présente, à son extrémité supérieure, une forme de came (47) correspondant à la caractéristique d'accélération souhaitée.
  7. Presse selon la revendication 5 ou 6,
    caractérisée en ce que la hauteur initiale du piston de commande (37) peut être réglée par l'intermédiaire d'un moteur (38) commandé de façon programmée.
  8. Presse selon une des revendications précédentes 1,3,4,
    caractérisée en ce qu'un autre vérin (56 à 58) est associé à l'espace de pression inférieur (19) du vérin (14 à 16), autre vérin qui se déplace, dans le même sens, avec le cadre de serre-flan (13) et dont le piston (57), lorsque l'outil supérieur (7) est mis en place sur le serre-flan (6), entre en contact avec une butée fixe (59) pour augmenter la pression dans l'espace de pression inférieur (19), et en ce qu'une alimentation en pression supplémentaire, dépendant de la course et commandée de façon programmée, du vérin (14 à 16) est effectuée au moyen du vérin (56 à 58) par l'intermédiaire d'une soupape proportionnelle (61).
  9. Presse selon la revendication 8,
    caractérisée en ce que le vérin (56 à 58) est agencé à l'intérieur du cadre mobile de serre-flan (13), et en ce que la tige de piston (57) entre en contact avec une butée (59) réglable en hauteur de façon motorisée au moment du serrage souhaité du serre-flan (6).
EP90117535A 1989-09-12 1990-09-12 Presse mécanique ou hydraulique avec dispositif d'étirage ou d'emboutissage pour presse à plusieurs étapes Expired - Lifetime EP0417752B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3930348 1989-09-12
DE3930348 1989-09-12

Publications (3)

Publication Number Publication Date
EP0417752A2 EP0417752A2 (fr) 1991-03-20
EP0417752A3 EP0417752A3 (en) 1991-06-05
EP0417752B1 true EP0417752B1 (fr) 1994-03-02

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ID=6389201

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90117535A Expired - Lifetime EP0417752B1 (fr) 1989-09-12 1990-09-12 Presse mécanique ou hydraulique avec dispositif d'étirage ou d'emboutissage pour presse à plusieurs étapes

Country Status (3)

Country Link
EP (1) EP0417752B1 (fr)
DE (1) DE59004758D1 (fr)
ES (1) ES2049378T3 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6729173B2 (en) 2001-04-27 2004-05-04 Schuler Pressen Gmbh & Co. Hydraulic draw press arrangement
DE10125078B4 (de) * 2001-04-27 2007-04-05 Schuler Pressen Gmbh & Co. Kg Hydraulische Zieheinrichtung

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4324963A1 (de) * 1993-07-24 1995-01-26 Erfurt Umformtechnik Gmbh Blechhalter für einfachwirkende Pressen, insbesondere für mechanische Pressen und Transferpressen
DE19538316A1 (de) * 1995-10-14 1997-04-17 Schuler Pressen Gmbh & Co Ziehvorrichtung für eine Presse
WO2006094485A1 (fr) * 2005-03-07 2006-09-14 Müller Weingarten AG Ensemble coussin d'emboutissage a entrainement par commande numerique et a coussin hydraulique
DE102011016669B4 (de) * 2011-04-12 2016-03-24 Schuler Pressen Gmbh Verfahren zum Betreiben einer Presse mit Unterantrieb und danach betriebene Presse
ES2853743T3 (es) * 2012-09-28 2021-09-17 Siemens Ag Accionamiento de cojín de tracción y procedimiento para operar un accionamiento de cojín de tracción

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3406526C2 (de) * 1984-02-23 1987-01-15 Maschinenfabrik Müller-Weingarten AG, 7987 Weingarten Einfachwirkende Presse mit einem Ziehkissen im Pressentisch und einem Schiebetisch
DE3717768A1 (de) * 1987-05-26 1988-12-08 Schuler Gmbh L Zieheinrichtung im pressentisch einer presse
DD272963A3 (de) * 1987-08-26 1989-11-01 Warnke Umformtech Veb K Pneumo-hydraulisches kissen fuer pressen zum abstreifen der blechteile aus dem werkzeug nach dem umformprozess bzw. zum gegenhalten waehrend des ziehvorganges
DD267205A1 (de) * 1987-12-24 1989-04-26 Warnke Umformtech Veb K Hydraulischer blechhalter fuer einfachwirkende pressen

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6729173B2 (en) 2001-04-27 2004-05-04 Schuler Pressen Gmbh & Co. Hydraulic draw press arrangement
DE10125078B4 (de) * 2001-04-27 2007-04-05 Schuler Pressen Gmbh & Co. Kg Hydraulische Zieheinrichtung

Also Published As

Publication number Publication date
EP0417752A2 (fr) 1991-03-20
DE59004758D1 (de) 1994-04-07
EP0417752A3 (en) 1991-06-05
ES2049378T3 (es) 1994-04-16

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