EP0417754B1 - 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
EP0417754B1
EP0417754B1 EP90117537A EP90117537A EP0417754B1 EP 0417754 B1 EP0417754 B1 EP 0417754B1 EP 90117537 A EP90117537 A EP 90117537A EP 90117537 A EP90117537 A EP 90117537A EP 0417754 B1 EP0417754 B1 EP 0417754B1
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EP
European Patent Office
Prior art keywords
piston
pressure
cylinder
press
die cushion
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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
EP90117537A
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German (de)
English (en)
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EP0417754A3 (en
EP0417754A2 (fr
Inventor
Erich Harsch
Walter Klenk
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
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Maschinenfabrik Mueller Weingarten AG
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Publication of EP0417754A3 publication Critical patent/EP0417754A3/de
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    • 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
    • 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

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, as is known from the document DD-A-242 355.
  • the amount of work required is measured as a counterforce to the Sheet metal counterholder is applied via a pressure cushion or pressure cheek to which air or hydraulic medium is applied, from the product counterforce times the way. Due to the tappet force acting on the sheet metal counterholder from above, some of the energy is stored in a storage device that provides the counterforce for the sheet metal counterholder and can be used as a restoring force on the tappet after the pulling process, when the pressure cushion or the pressure cheek and the tappet rises again Relieve the drive. If the pressure cushion is held back in its lower position and raised again under pressure control, then the entire energy generated when the ram and the sheet metal counter-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 min. a power loss of 196 kW.
  • drawing presses have been proposed that work with mechanically operated sheet metal counterholders.
  • Such mechanical sheet metal supports work via lever drives, which are associated with great mechanical and therefore also financial expenditure.
  • the machine body would in principle have to absorb the full pressing force of both the ram and the sheet metal counterhold.
  • Hydraulic drawing presses have become known from DE-PS 883 736 or from DE 38 35 376 A1, the press rams of which are connected via connecting rods directly or indirectly via a piston-cylinder unit to a lower sheet metal holder frame for supporting the drawing cushion are.
  • the die cushion is supported via the outer piston-cylinder units coupled to the connecting rods, the pressure medium of which is supplied to these units in a controllable manner.
  • the pressure pad for the sheet metal counterholder is rigidly connected to these piston-cylinder units via a central connecting rod. This device therefore only serves to clamp the workpiece against the ram force.
  • a disadvantage of such drawing presses is the fact that the press ram with the upper tool strikes the lower tool with sheet metal counterholder with great force and is at least associated with a high level of noise pollution. At the same time, the sheet metal counterholder has to be accelerated suddenly to the speed of the press ram, which generates a high energy requirement.
  • a device for pre-accelerating the movable cushion masses in drawing presses has become known.
  • a gradual acceleration of the die cushion from zero to almost ram speed is achieved. This is done by means of a complicated telescopic cylinder in a control line system, with a telescopic ring piston which can be actuated by means of a special stamp.
  • the ring pistons are acted upon one after the other and thus gradually displace pressure medium for the die cushion movement.
  • the number of telescopic pistons determines the degree of pre-acceleration of the movable cushion masses.
  • a targeted hydraulic control of a compliant sheet metal counterholder via the ram is still out DE-PS 877 590 known.
  • compensating cylinders are provided, which perform a defined pressure transfer to the die cushion when the press ram moves.
  • a targeted acceleration of the sheet metal counter-holder is not provided here.
  • the press according to the invention with the characterizing features of claim 1 has the advantage that it contains a pulling device, by means of which the impact noise that occurs when the upper tool hits the sheet metal counterholder can be considerably reduced by a pre-acceleration of the die cushion masses and subsequent hydraulic tensioning of the sheet metal counterholder can take place .
  • the process runs largely without complicated and delayed valve controls, i. H. these valve controls are kept to a minimum. This ensures a high reproducibility of the machining process due to the lack of control mechanisms.
  • the device according to the invention therefore runs in the manner of a positive control.
  • the invention makes use of the individual movements to perform the individual movements and, in particular, to generate the bracing of the sheet metal counter-holder.
  • the kinetic energy of the press ram is not converted into heat by means of throttle valves during its downward movement, but is stored in corresponding pressure accumulators. The energy stored in this way can be reused for the ram return stroke.
  • the press 1 with a pulling device in FIGS. 1 and 2 consists of a stationary press table 2 with a table support 3 for receiving a lower tool 4 for producing a workpiece, represented by a board 5 which has not yet been machined.
  • the board 5 is placed on a sheet metal counterholder 6. which is guided in the lower tool 4 with a stamp 4 '.
  • the upper tool 7 is connected to a press ram 8.
  • the sheet metal counter-holder 6 is generally supported by pressure bolts 9 on a pressure cheek 10, or also known as die cushion 10.
  • the die cushion 10 lies on a die cushion holder 10 '. Both parts together form the die cushion unit 10, 10 '.
  • the press ram 8 is connected via at least two laterally arranged connecting rods 11 or four connecting rods 11 arranged in its corner regions connected to the lower part of the pulling device.
  • the connecting rods 11 serve as piston rods 11 for a first piston-cylinder unit 12 with piston 13 and, in FIG. 1, the cylinder space 14 underneath for the pressure medium.
  • This first piston-cylinder unit 11, 12, 13, 14 is referred to below as the pump cylinder 12.
  • the die cushion unit 10, 10 'and in particular the die cushion holder 10' are supported downwards by at least two lateral and in particular four second piston-cylinder units 15 arranged in the corner regions of the die cushion, which are referred to below as pressure cylinders 15.
  • the pressure cylinders 15 consist of a piston rod 16 connected to the die cushion rest 10 ', a piston 17 arranged at the end thereof and a cylinder space 18 for pressure medium which completely surrounds the piston.
  • the cylinder space located above the piston 17 is denoted by 18 ', the cylinder space arranged below the piston 17 by 18' '.
  • the pressure chamber 14 of each pump cylinder 12 is connected to the upper pressure chamber 18 'of the pressure cylinder 15 via a pressure line 19.
  • the lower pressure chamber 18 ′′ is connected to a pressure accumulator 21 via a pressure line 20.
  • the pressure line 19 is connected via a further pressure line 22 to a further pressure accumulator 23 via a check valve 24.
  • the pressure line 22 is also assigned a further pressure accumulator 25 via a pressure line 26, which is controlled in a controllable manner by means of a hydraulic valve 27.
  • Another line 28 connects the pressure line 22 to a pressure relief valve 29 which is connected to a pressure oil outlet device 31 via a further pressure valve 30.
  • the first piston-cylinder unit or the pump cylinder 12 is connected with its pressure chamber 14 via a line 32 to a metering reservoir 33, a further piston-cylinder unit 34 with piston 35 and cylinder chamber 36 being connected in between.
  • the piston 35 is guided in the cylinder chamber 36 over a defined distance s 1 to an upper stop 37, an adjusting device 38 accomplishing the path specification.
  • the embodiment of the pulling device according to FIG. 2 differs from that according to FIG. 1 only in that the first piston-cylinder unit 12, i. H. the pump cylinder 12, not in the lower part of the pulling device via the connecting rods 11, as in FIG. 1, but in the upper part of the pulling device, i. H. is arranged above the press ram 8.
  • the connecting line 19 between this upper pump cylinder 12 and the lower pressure cylinder 15 is drawn from top to bottom in the pulling device. 2
  • the piston rod 11 of the pump cylinder 12 is in turn connected to a piston 13, the pressure chamber 14 being now integrated in the upper housing of the pulling device 1.
  • the effective cross-sectional area of the pressure chamber 14 is reduced by the piston rod 11, which must be taken into account when adjusting the pressure.
  • the pressure accumulator 23 with check valve 24 via line 22 and the pressure relief valve 29 with pressure valve 30 via line 28 are further connected to line 19 in the upper region of the pulling device in the head part of the pulling device. Furthermore, the piston-cylinder unit 34 with the metering reservoir 33 as well as the piston 35, cylinder space 36 and adjusting device 38 is in the upper head part of the Pulling device integrated.
  • the pressure accumulator 25 with a controllable hydraulic valve 27 and a connecting line 26 to the pressure line 19 also remains in the lower region of the drawing device in the exemplary embodiment according to FIG. 2.
  • auxiliary cylinder 39 consists of a piston 41 which is arranged in a cylinder space 40 and can be acted upon by pressure from the pressure line 20 on its upper side via a pressure line 42; H. the upper pressure chamber 40 'is connected via the pressure line 42 to the lower pressure chamber 18' of the pressure cylinder 15 and to the pressure accumulator 21 in the same way.
  • the cylinder space 40 has a defined height h, the piston 41 being able to move down a defined distance s 2 before it moves against a stop 43 formed by the wall of the cylinder space.
  • the directional control valve 30, which is designed as a solenoid valve, is actuated and the flow through the check valve 29 is thus blocked.
  • the pressure medium cannot flow from the pressure chamber 14 of the pump cylinder 12 via the lines 19, 22, 28 into an outlet 44. Rather, the pressure medium displaced by the piston 13 during the downward movement of the press ram 8 is pressed out of the pressure chamber 14 via the line 32 into the lower cylinder chamber 36 ', so that the piston 35 of the piston-cylinder unit 34 is pressed upward.
  • the starting position of this piston 35 is adjusted by the adjusting device or adjusting screw 38, so that the distance s 1 of the piston 35 that can be covered is adjustable.
  • the pressure medium located above the piston 35 is hereby pressed into the metering reservoir 33, which is prestressed with a prestressing pressure of approximately 8 bar.
  • the upper stop surface 37 limits the upward stroke of the piston 35 to the adjustable distance s 1. A pressure increase thus takes place in the metering reservoir 33.
  • the pressure in the upper cylinder space 18 ' is opposed by the pressure in the lower cylinder space 18''. This is first determined from the pressure of the pressure accumulator 21, which with a maximum pressure, for. B. about 200 bar, is biased according to the maximum die cushion force.
  • the pressure accumulator 21 is connected via the line 42 to the upper pressure surface 41 'of the piston 41.
  • the effective lower pressure surface 17 ′′ of the piston 17 is approximately 10% larger than the upper effective pressure surface 41 ′ of the piston 41.
  • the stroke of the piston 41 of the auxiliary cylinder 39 is, for example, s2 ⁇ 20 mm before the piston 41st moves against the lower housing stop during the downward movement of the die cushion unit. Thereafter, the pressure line 42 is meaningless with regard to the movement sequence of the die cushion unit. During this stroke by the amount s2 during the downward movement of the die cushion, the die cushion force is only about 10% of the maximum pretensioning force.
  • the upper effective piston area 17 'of the piston 17 is approximately 20% larger than the lower effective piston area 13' of the piston 13.
  • the die cushion speed is therefore 0.8 times the ram speed. This state applies to the pre-acceleration of the plate counter-holder 6, i. H. before the upper tool hits the sheet metal counterholder. Then the upper tool 7 or the press ram 8 and the sheet metal counter-holder 6 and thus the die cushion unit 10 move downward at the same speed.
  • the start of the pre-acceleration of the sheet metal counterholder is set by the adjusting device 38, ie the piston 35 first runs through the set path s 1 until it stops; the pressure medium of the pump cylinder 12 is then deflected from the pressure chamber 14 into the upper pressure chamber 18 '.
  • the pre-acceleration movement of the die cushion starts at a distance from the upper tool 7 to the board 5 of approximately 4 mm when the upper tool touches the board after a 16 mm counter-stroke. This route is taken into account, as is the route for oil compression by the adjusting device 38, ie the route s 1.
  • the pre-acceleration of the die cushion unit 10, 10 'and thus the sheet metal counter-holder 6 takes place without substantial counterpressure of the pressure accumulator 21. This takes place due to the downward movement of the piston 41 by the amount of s 2. During this path, the pressure force of the pressure accumulator 21 acts both on the somewhat larger lower pressure surface 17 ′′ and on the upper pressure surface 41 ′. As a result, the die cushion unit 10, 10 'is virtually in equilibrium. The pre-acceleration of the sheet metal counterholder 6 continues until the upper tool 7 has caught up with the sheet metal counterholder 6 and is seated thereon.
  • the pressure of the pressure medium from the pump cylinder 12 is therefore used in the cylinder space 18 of the pressure cylinder 15 to pre-accelerate the die cushion unit and thus the sheet metal counter-holder.
  • This pressure is composed of a static working pressure and a required acceleration pressure.
  • the static working pressure results from the area difference of the pressure cylinder surface 17 '' of the piston 17 minus the auxiliary cylinder surface 41 'of the piston 41 divided by the upper ring surface 17' of the piston 17.
  • the dynamic downward pressure on the surface 17 'required for the acceleration is dependent on the stroke rate. This pressure is added to the static pressure and additionally compresses the hydraulic oil.
  • the die cushion When the upper tool 7 strikes the sheet metal counterholder 6, the die cushion is suddenly accelerated from 80% to 100% ram speed against approximately 10% die cushion force. After a 20 mm die cushion stroke, the piston 41 of the auxiliary cylinder 39 runs against its stop 43. The die cushion force then suddenly increases to approximately 90% of that determined by the pressure accumulator 21 Strength increased. The remaining portion of the force of 10% is still effective on the annular surface 17 ′ of the piston 17 due to the compressed pressure medium required for the pre-acceleration. During the further downward movement of the die cushion unit, the force acting on the die cushion can be changed by pressure change in the line 19 or 22 by means of the hydraulic valve 27 by pressure medium from the pressure accumulator 25.
  • the pressure accumulator 25 is preloaded so high that the cushion force can be canceled by counter pressure in the pressure cylinder 15.
  • the hydraulic valve 27 connects the hydraulic line 22 either to the pressure accumulator 25 or to an unpressurized hydraulic tank 46. In the basic position (starting position), both stops are blocked.
  • the pressure relief valve 29 pretensions the hydraulic line 22 with approximately 5 bar.
  • the die cushion 10 moves upward at approximately 80% of the speed of the press ram 8. This is done in the pressure accumulator 21 energy stored during the downward movement of the press ram 8 is now used in addition to the ram upward movement. Approx. 20 mm before the upper end of the stroke, the die cushion rest 10 'hits the lower plunger 45 of the auxiliary cylinder 39. As a result, the die cushion upward force is suddenly reduced to approximately 10% of the maximum force, since in turn the balance between the upper piston surface 41' and the lower one Set piston surface 17 ′′ via the connecting line 20, 42.
  • the press ram 8 is accordingly connected to a plurality of pump cylinders 12, which are arranged in particular in the four corner regions. These pump cylinders 12 interact with pressure cylinders 15 in the sense of a pre-acceleration of the pressure cheek 10 and a subsequent bracing.
  • the dosing memory 33 with the adjusting device 38 Hydraulic tensioning of the die cushion during the downward stroke of the press ram, so to speak, unlocked and tensioned again only shortly before the upper tool 7 strikes the sheet metal counterholder 6, thus initiating a preliminary movement.
  • the difference in speed between the press ram 8 and the pressure cheek 10 and thus the speed at which the upper tool 7 strikes the sheet metal counterholder 6 can be determined by the area difference between the effective piston area 13 'of the pump cylinder 12 and the effective areas in the pressure cylinder 17.
  • the pressure in the hydraulic line 22 and thus in the connecting line 19 and thus in the effective pressure space between the pump cylinder 12 and pressure cylinder 15 can be controlled by means of the hydraulic valve 27 and / or program-controlled.
  • the majority of the pressure energy required for the die cushion force during the downward movement is not converted into heat, but can be stored in the pressure accumulator 21 and 33 and reused for the upward movement of the press ram 8.
  • the auxiliary cylinder 39 reduces the force on the pressure cheek 10 during its preliminary differential movement downwards until the time when the piston 41 is seated.

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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)

Claims (14)

  1. Presse mécanique ou hydraulique à dispositif d'emboutissage ou étage d'emboutissage d'une presse à étages, dans laquelle un dispositif de maintien des tôles (6) est commandé et serré hydrauliquement au moyen d'un coussin de serre-flan (10), le mouvement d'un coulisseau de presse (8) pouvant être transmis, par l'intermédiaire d'une tige de piston (11), à un premier vérin stationnaire (12) (vérin de pompe 12), dont le fluide de pression agit sur un second vérin (15) relié au coussin de serre-flan (10) (vérin de pression 15), dans le sens d'une descente préaccélérante du coussin de serre-flan (10),
    caractérisée en ce que, pour obtenir une préaccélération, apparaissant initialement, du dispositif de maintien des tôles (6), le fluide de pression du vérin de pompe (12) ne peut être amené au vérin de pression (15) relié au coussin de serre-flan (10), dans le sens d'une descente définie du coussin de serre-flan (10), que peu avant le contact de l'outil supérieur (7) avec le dispositif de maintien des tôles (6), et en ce que, après achèvement de la préaccélération du dispositif de maintien des tôles (6), un réservoir de précontrainte (21) exerce une force de précontrainte dirigée vers le haut et, ainsi, sur le coussin de serre-flan (10), en tant que force de maintien des tôles.
  2. Presse selon la revendication 1,
    caractérisée en ce que le fluide de pression dans le vérin de pompe (12), lors de la descente du coulisseau de presse (8), est tout d'abord amené dans un réservoir de dosage (33), la force de précontrainte du réservoir de dosage (33) étant en particulier plus faible que la force de précontrainte du réservoir de pression (21).
  3. Presse selon la revendication 2,
    caractérisée en ce que la charge du réservoir de dosage (33) est effectuée par un vérin intermédiaire (34) à piston de dosage (35) à course commandée, la course réglable s₁ du piston de dosage (35) limitant la charge du réservoir de dosage (33).
  4. Presse selon la revendication 1,
    caractérisée en ce que la tige de piston ou la tige de liaison (11) entre le coulisseau de presse (8) et le vérin de pompe (12) est réalisée en tant que tige de piston pour un piston (13) d'un vérin (12) intégré dans le carter de la presse (vérin de pompe 12), et en ce que la surface inférieure efficace (13') du piston (13) agit tout d'abord sur le piston de dosage (35) du vérin (34) et, après sa limitation de course, sur le piston (17) du second vérin (15) (vérin de pression 15).
  5. Presse selon une des revendications précédentes,
    caractérisée en ce que, pour engendrer des vitesses de marche différentes entre le piston (13) et le piston (17), la surface efficace (13') du piston (13) du vérin de pompe (12) est plus petite que la surface de piston supérieure (17'), disponible pour la descente du coussin de serre-flan (10), du second vérin (15) (vérin de pression 15), de sorte que la vitesse de descente du coulisseau de presse (8), après l'arrêt du piston de dosage (35) jusqu'au contact avec l'outil supérieur (7) sur le dispositif de maintien des tôles (6), est plus grande que la vitesse de descente du coussin de serre-flan (10), l'outil supérieur (7) rejoignant le dispositif de maintien des tôles (6) après une course donnée.
  6. Presse selon la revendication 5,
    caractérisée en ce que la descente commune, d'étendue réglable, de l'outil supérieur (7) ou du coulisseau de presse (8) et de la face de pression (10) après le contact de l'outil supérieur (7) sur le dispositif de maintien des tôles (6) a lieu sur une étendue déterminée avec une force diminuée du coussin de serre-flan sur le dispositif de maintien des tôles.
  7. Presse selon la revendication 6,
    caractérisée en ce que la dépression existant dans l'espace de pression entre les premier et second vérins (12,15), pour une vitesse identique des pistons (13,17), peut être compensée au moyen d'un dispositif de compensation de dépression (23,24,22).
  8. Presse selon une des revendications précédentes,
    caractérisée en ce que le cylindre inférieur (18''), relié au réservoir de pression (21), du vérin de pression (15) est relié, par l'intermédiaire d'un autre conduit de pression (42), à un troisième vérin (39) agencé entre la table de presse (2) et le coussin de serre-flan (10), vérin dont le piston (41) effectue un mouvement orienté vers le bas sur le coussin de serre-flan (10) sur une étendue définie s₂.
  9. Presse selon la revendication 8,
    caractérisée en ce que le vérin (39) est agencé au-dessus du coussin de serre-flan (10) ou d'un récepteur (10') du coussin de serre-flan, avec une surface supérieure (41'), qui peut être sollicitée par de la pression, du piston (41), qui est reliée au réservoir de pression (21), et avec un coulisseau inférieur (45) qui s'appuie sur le coussin de serre-flan (10) ou le récepteur (10') du coussin de serre-flan, la course du piston dans le cylindre (40) correspondant étant limitée, vers le bas, par l'étendue s₂.
  10. Presse selon une des revendications précédentes,
    caractérisée en ce que la surface de piston inférieure (17'') du vérin de pression (15) est plus grande que la surface de piston supérieure (41'), reliée hydrauliquement à celle-ci, du troisième vérin (39).
  11. Presse selon une des revendications précédentes,
    caractérisée en ce que l'espace de pression efficace entre le vérin de pompe (12) et le vérin de pression (15) peut être alimenté en pression, de façon réglable, par l'intermédiaire d'un conduit de pression (22), au moyen d'un réservoir de pression supplémentaire (25), une commande à soupape proportionnelle (27) étant prévue dans le sens d'un réglage de la force de maintien des tôles pendant le processus d'emboutissage.
  12. Presse selon une des revendications précédentes,
    caractérisée en ce que l'espace de pression efficace (14, 18') entre le vérin de pompe (12) et le vérin de pression (15) est relié, par l'intermédiaire d'un conduit de pression (22,28), à un distributeur (30) qui peut être actionné magnétiquement, pour une compensation de pression.
  13. Presse selon une des revendications précédentes,
    caractérisée en ce que, pour chaque dispositif d'emboutissage (4), sont prévus des vérins de pression (15) et des vérins de pompe (12) agencés dans les zones de coin.
  14. Presse selon une des revendications précédentes,
    caractérisée en ce que la plus grand partie de l'énergie de pression nécessaire pendant la descente du coulisseau de presse (8) pour la force du coussin de serre-flan n'est pas transformée en chaleur, mais stockée dans le réservoir de pression (21,33) et réutilisée pour la montée du coulisseau de presse (8).
EP90117537A 1989-09-12 1990-09-12 Presse mécanique ou hydraulique avec dispositif d'étirage ou d'emboutissage pour presse à plusieurs étapes Expired - Lifetime EP0417754B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3930349 1989-09-12
DE3930349 1989-09-12

Publications (3)

Publication Number Publication Date
EP0417754A2 EP0417754A2 (fr) 1991-03-20
EP0417754A3 EP0417754A3 (en) 1991-06-12
EP0417754B1 true EP0417754B1 (fr) 1993-09-08

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EP90117537A Expired - Lifetime EP0417754B1 (fr) 1989-09-12 1990-09-12 Presse mécanique ou hydraulique avec dispositif d'étirage ou d'emboutissage pour presse à plusieurs étapes

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EP (1) EP0417754B1 (fr)
DE (1) DE59002628D1 (fr)
ES (1) ES2045702T3 (fr)

Cited By (3)

* 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
WO2008064619A1 (fr) * 2006-11-30 2008-06-05 Müller Weingarten AG Presse de formage présentant une fonction de coussin pneumatique intégrée au plateau coulissant

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2084558B1 (es) * 1993-11-25 1998-05-01 Fagor S Coop Sistema de preceleracion para un cojin hidraulico de prensa.
JP2812201B2 (ja) * 1994-07-15 1998-10-22 トヨタ自動車株式会社 プレス装置
JP2856107B2 (ja) * 1995-05-22 1999-02-10 トヨタ自動車株式会社 プレス加工方法およびプレス加工装置
ES2190833B1 (es) * 2000-03-30 2004-07-01 Fagor, S. Coop Prensa con cojin hidraulico con sistema de control de fuerza y posicion.
DE102004049149A1 (de) * 2004-10-07 2006-04-13 Feintool International Management Ag Verfahren und Vorrichtung zum Herstellen und/oder Bearbeitung von Teilen

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD242355A1 (de) * 1985-10-30 1987-01-28 Warnke Umformtech Veb K Einrichtung zur auftreffstossdaempfung fuer ziehkissen an pressen
DD267926B5 (de) * 1987-12-14 1994-03-10 Erfurt Umformtechnik Gmbh Rueckzugssteuerung fuer ziehkissen an pressen

Cited By (4)

* 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
WO2008064619A1 (fr) * 2006-11-30 2008-06-05 Müller Weingarten AG Presse de formage présentant une fonction de coussin pneumatique intégrée au plateau coulissant
DE102006057051A1 (de) 2006-11-30 2008-07-03 Müller Weingarten AG Umformpresse mit im Schiebetisch integrierter Ziehkissenfunktionalität

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ES2045702T3 (es) 1994-01-16
DE59002628D1 (de) 1993-10-14
EP0417754A3 (en) 1991-06-12
EP0417754A2 (fr) 1991-03-20

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