EP0616882B1 - Méthode de commande hydraulique d'une presse à levier articulée ou à genoullière et presse à levier articulée ou à genoullière avec un système de commande adapté à la mise en oeuvre de la méthode - Google Patents

Méthode de commande hydraulique d'une presse à levier articulée ou à genoullière et presse à levier articulée ou à genoullière avec un système de commande adapté à la mise en oeuvre de la méthode Download PDF

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Publication number
EP0616882B1
EP0616882B1 EP19940104561 EP94104561A EP0616882B1 EP 0616882 B1 EP0616882 B1 EP 0616882B1 EP 19940104561 EP19940104561 EP 19940104561 EP 94104561 A EP94104561 A EP 94104561A EP 0616882 B1 EP0616882 B1 EP 0616882B1
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EP
European Patent Office
Prior art keywords
press
cylinder
line
valve
ram
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
EP19940104561
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German (de)
English (en)
Other versions
EP0616882A1 (fr
Inventor
Jürgen Hennig
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.)
Leinhaas Umformtechnik GmbH
Original Assignee
Leinhaas Umformtechnik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Leinhaas Umformtechnik GmbH filed Critical Leinhaas Umformtechnik GmbH
Publication of EP0616882A1 publication Critical patent/EP0616882A1/fr
Application granted granted Critical
Publication of EP0616882B1 publication Critical patent/EP0616882B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • B30B1/10—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 toggle mechanism
    • B30B1/106—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 toggle mechanism operated by another toggle mechanism
    • 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
    • B30B1/10—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 toggle mechanism
    • 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
    • B30B1/10—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 toggle mechanism
    • B30B1/16—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 toggle mechanism operated by fluid-pressure means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/14—Control arrangements for mechanically-driven presses
    • 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
    • Y10T83/04—Processes
    • 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
    • Y10T83/8821—With simple rectilinear reciprocating motion only
    • Y10T83/8858—Fluid pressure actuated

Definitions

  • the invention relates to a method for controlling a and an articulated or toggle press controlled after the Method according to the preamble of claim 1 and According to claim 5.
  • Such processes are mainly used for Cutting and forming presses of modern design with hydromechanical Articulated lever drives applied.
  • the applicant has for example under the name differential travel press (DWP) successfully launched a toggle plate cutting press in the Market introduced, for example in DE-C 2925416 or EP-A1 250610.
  • DWP differential travel press
  • Such a press has two - with their knee joints buckling towards the middle of the press - toggle lever systems, that of a piston rod one symmetrical to the toggle levers arranged cylinder piston assembly during a Lift cycle in the forward and then reverse direction be charged.
  • DDP Differential printing press
  • the toggle levers also provide precision in the cutting direction (depth of cut) for sure what is under also for toggle presses with hydraulic piston drives took advantage of, such as shown in GB-A 707815.
  • the present invention is therefore based on the object of providing a press and a simple method for driving the same, which, without losing the respective advantages and properties of the known presses, should enable a higher stroke rate and therefore greater profitability.
  • the additional components required for the control effort should be kept as low as possible - not least to avoid inertia and control errors -.
  • a conventional DWP or DDP should be improved in such a way that a desired forming speed can be set which remains essentially constant over the entire forming process, as a result of which the optimum forming speed is achieved per workpiece. This task should also be made possible without significant additional control expenditure (by a large number of additional components for regulators or the like).
  • the tasks are solved for the first time by adding the Features of the characterizing part of claim 1 or by Press with the features of claim 5.
  • U.S. Patent 3,926,033 shows a "series connection" of Cylinder piston arrangements (telescopic cylinders) with different effective areas, which in turn disadvantageously with correspondingly large, powerful pressure medium drives must be applied.
  • a targeted one Switch from one piston to another inside a movement phase is not possible
  • the invention solves the stated problems in a simple manner Art.
  • the invention can with any conventional Pressurized articulated or toggle press be applied.
  • the only requirement is that the drive the piston rod is speed controllable.
  • the ram speed is reduced by the method according to the invention not as before (e.g. with the DWP or DDP) reduced to the UT (bottom dead center), but rather almost constant at the expense of the driving force of the piston rod held.
  • the effect according to the invention comes to that Workpiece in the opposite direction: only during first contact of the cutting tool with the workpiece are high forces second hand; these generally decrease in the flow area.
  • the invention advantageously changes other desired ones Properties of a DWP or DDP not, e.g. Stop times under 50ms, practically no cutting bang due to under high Pressure of clamped oil quantities, long tool life, possibility any reprint settings in the range from UT, no need for shock absorption, etc.
  • the invention is by the simplest hydraulic Circuits possible. Compared to the known circuit according to DE-A1 4036564, it can according to the exemplary embodiments shown with a minimal mechanical-hydraulic Regular effort to find enough.
  • a preferred embodiment of a press according to the invention is however with at least one stepped piston cylinder or Differential cylinder with integrated plunger cylinder as Main working power source equipped.
  • this structure offers the advantage great compactness and a reduction of sealing problems compared to arrangements of multiple drive cylinders with different ones working parallel to each other Printing areas.
  • this offers preferred Solution that one in the sense of a high hydraulic efficiency with high pressures but low oil flows can work.
  • the method according to the invention deals with the basic principle forth with the control of a press ram one hydromechanical toggle press in its working area.
  • the basic idea is the speed of work of the ram there as constant as possible on the as optimal recognized speed that he was at the time of first cut contact (at the beginning of the work area) has reached.
  • the piston rod speed after reaching the To increase the intersection point so that after redirection of this Speed through the toggle or even one Increase in ram speed results if for the workpiece in question, for example, from deformation technology Reasons is desirable.
  • valves depending on the path of the piston rod, because highest stroke rates can be achieved.
  • the principle of the step piston shown in the drawing can course within the scope of the invention to increase the Use the number of stages several times, provided the cylinder piston arrangement is chosen accordingly.
  • Another variant could be between the piston rod and a suitable lever ratio at the articulation points on the toggle levers or a gear or the like. be arranged that way is designed so that it corresponds to the inventive Procedure with constant piston speed Articulation points accelerated in the forward direction.
  • Fig. 1 shows a toggle press, the construction of which is shown in US-A-707815 (Corresponding parts of the description are deemed to be herein disclosed) is described in more detail.
  • the press stamp 1 is driven by the toggle assembly 18, which by a cylinder-piston arrangement 10, 11 is driven. This arrangement is via pressure lines 2 from a hydraulic Control 3 controlled. the control works the principle according to the invention. In the area of the UT the Increased oil flow rate and the piston 10 accelerated accordingly, so that the press ram or ram 1 in the work area has a constant working speed.
  • Fig. 2 shows a press with two counter-acting toggle lever systems 10, 12, 16 by a cylinder-piston arrangement 10,11 are driven. The latter becomes corresponding the press of Figure 1 with a control line 21 Compressed air or another pressure medium.
  • the press ram 20 of this press works from the bottom up. The meaning of the UT area according to the invention is here thus understandable for the OT.
  • the press according to Figure 3 is the one according to Figures 1 and 2 to the extent that the working cylinder 1 is not on Housing G, but is supported on the plunger 3, it corresponds thus a DWP.
  • the detailed structure of such Press is described for example in EP-A1 250610.
  • a pump delivers pressure oil through a pressure line 30 a cam-operated 3-position valve 14a, which in its Position b promotes the oil in a line 31.
  • the cam control is coupled to the piston position and symbolic indicated at 15.
  • Line 31 becomes the pressure oil via the 3-position valve 16a in its position a via the 2-position valve 21 in its position b in the innermost Cylinder chamber 11 promoted. Because this is a relatively small volume has resulted in a relatively rapid downward movement of the piston 2 and thus via the pressure piece 4 and Toggle lever 5,6,7 a rapid downward movement of the ram 3.
  • the cylinder chamber 13 is simultaneously via the line 36 emptied, this via the valve 14a (position b) in the reservoir 25 is emptied.
  • valve 16a By switching the valve 16a to its position 0 (phase 2A) starting with phase 2 (see Fig. 7), pressure oil is now used conveyed from line 31 into both cylinder chambers 11 and 12, whereby the nominal working pressure for the plunger 3 is applied becomes.
  • the feed speed of the piston rod 2 is the least now, your strength is the greatest.
  • valve 16a By switching the valve 16a into its position b (phase 2B), pressure oil is only delivered into the cylinder space 12. Unpressurized oil enters the cylinder chamber 11 from the reservoir 18. The speed of the piston rod 2 is thereby accelerated again, the speed of the ram 3 not delayed.
  • valve 16a After reaching the UT, valve 16a switches to position a and valve 14a in its position a, whereby the pressure oil out the line 30 is promoted to line 36 to from there to apply pressure to the annular cylinder space 13, which moves the piston 2 quickly upwards. In the beginning is the the pressure required for this is still low since the toggle lever ratio helps. At the same time, valve 16a switches on its position a, whereby the oil from the room 12 in the Pressure accumulator 18 and the oil from space 11 via the valve 14a can flow into the line 42 or the container 25.
  • the container 18 shown as a pressure accumulator reduces the Pressure oil relaxation problems during the transition from unpressurized in the printing state. As a rule, however, it will only a low compared to the working pressure in the cylinder Have pressure and - as in other examples (e.g. Fig. 4) represented - even with a pure refill container Ambient pressure can be replaced.
  • the variant according to Fig.4 dispenses with the differential circuit option.
  • Pressure oil flows from pump 24 via line 30, valve 19 (b), Line 31, valve 14b (a), line 32, valve 16b (b), line 33 and 35 in rooms 11 and 12.
  • Pressure oil flows from pump 24 via line 30, valve 19 (b), Line 31, valve 14b (a), line 32, valve 16b (c). management 33 in the cylinder space 11.
  • Pressure oil flows from pump 24 via line 30, valve 19 (b), Line 31, valve 14b (c), line 37, valve 19 (b), line 36 into the cylinder space 13. That from the cylinder space 11 displaced oil flows via line 33, valve 16b (c), line 32, valve 14b (c), line 38 into the container 25. Das Oil displaced from the cylinder chamber 12 flows via the line 35, valve 16b (c), line 34 into container 15.
  • the valve 14b can be used as a 4-edge regulator (FIGS. 4 and 6) or are designed as a 2-edge controller 14c (FIG. 5).
  • the valve 16b in an embodiment according to FIGS. 4 and 5 individual valves 20, 21, 22, 23 (corresponding to Fig. 6) replaced will.
  • the electrohydraulic Actuation by mechanical actuation in Depending on the piston 2 take place via cams.
  • the hydraulically effective piston surface in the cylinder chamber 11 is larger than the effective piston area in the cylinder space 13.
  • Pressure oil flows from pump 24 via line 30, valve 19 (b), Line 31, valve 14c (a), line 32, valve 16b (c), Line 33 into the cylinder chamber 11.
  • the oil displaced from the cylinders 44 flows through the lines 39, 40, valve 19 (b), line 41, valve 17 (b), Line 42 into the tank 25.
  • Pressure oil flows from pump 24 via line 30, valve 19 (b), Line 31, valve 14c (a), line 32, valve 16 (b), lines 33, 35 into the cylinder spaces 12, 11. From the cylinder space 13 oil flows through line 36, valve 18 (b), line 38 back into the tank 25. That from cylinders 44 displaced oil flows via lines 39, 40, valve 19 (b) line 41, valve 17 (b), line 42 into tank 25.
  • the oil displaced from the cylinders 44 flows through the lines 39, 40, valve 19 (b), line 41, valve 17 (b), Line 42 into the tank 25.
  • Pressure oil flows from pump 24 via line 30, valve 19 (b), Line 31, valve 18 (a), line 36 into the cylinder space 13. At the same time, pressure oil flows from pump 24 via valve 17 (a), line 41, valve 19 (b), lines 39, 40 to the Cylinders 44.
  • the oil displaced from the cylinder chamber 11 flows through the line 33, valve 16b (c), line 32, valve 14 (c), line 38 into the tank 25.
  • the oil displaced from the cylinder space 12 flows via line 35, valve 16b (c), line 34 into the Container 15.
  • the upper chambers of the auxiliary cylinders 44 are with their upper hydraulic room with ambient air connected.
  • the effective piston ring area of the annular space 13 is smaller than that of the effective cylinder space 11.
  • the space 13 stands constantly under pump pressure. But there is a forward movement nevertheless possible due to the above area ratio.
  • the Auxiliary cylinders therefore support the backward movement, to the small force of the small effective area in the Make up for space 13. At the beginning of the backward movement the performance of 13 is still completely sufficient, since there the Lever translation of the toggle lever still helps. First against This support is needed at the end of the backward movement.
  • the hydraulically effective piston surface in the cylinder chamber 11 is smaller than the piston area in the cylinder chamber 13.
  • Parenthetical expressions mean the position of the respective valve.
  • Valve 21 is in Position b. Oil from the container becomes in the cylinder chamber 12 15 sucked in via line 34, valve 23, line 35 or refilled. Oil flows from the cylinder space 13 via a line 36, valve 19 (b), line 37, valve 14b (a), line 38 in the tank 25 back.
  • Pressure oil flows from pump 24 via line 30, valve 19 (b), Line 31, valve 14b (a), line 32, valves 20 (a), 21 (a), Lines 33, 35 into the cylinder spaces 11, 12. From the cylinder space 13 oil flows through line 36, valve 19 (b), line 37, valve 14b (a), line 38 back into tank 25.
  • Valve 20 is in Position b. In the cylinder chamber 11 oil from the container 15 sucked in via line 34, valve 22, line 33 or refilled. Oil flows from the cylinder space 13 via a line 36, valve 19 (b), line 37, valve 14b (a), line 38 in the tank 25 back.
  • Valve 21 is in Position b. Oil from the container becomes in the cylinder chamber 12 15 sucked in via line 34, valve 23, line 35 or refilled. Oil flows from the cylinder space 13 via a line 36, valve 19 (b), line 37, valve 14b (a), line 38 in the tank 25 back.
  • Valve 20 is in Position b.
  • Valve 18 is in Position a.
  • valves and lines shown can be functional Similar components can be replaced without the frame to leave the invention, provided that the invention Procedure apply.
  • the outer structure of the press preferably includes one Partially closed two-stand frame on the front and front according to the well-known DWP.
  • a multi-joint lever construction according to WO 87/07870 A1 is also possible be realized constructively within the scope of the invention. On the relevant parts of the description in the cited Publication is referenced.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Control Of Presses (AREA)

Claims (10)

  1. Méthode de commande hydraulique d'une tige de piston (2) d'un cylindre de travail (1) d'un système de levier articulé ou de genouillère d'une presse à levier articulé ou à genouillère dans laquelle avant d'arriver a la phase d'intersection (contact de l'outil avec la pièce), la vitesse du coulisseau de la presse est réduite et la force de compression du coulisseau (3) est augmentée, caractérisée en ce que la vitesse du mouvement en avant de la tige de piston (2) est augmentée au moins une fois après que le point d'intersection a été atteint et avant le déclenchement du mouvement en arrière.
  2. Méthode selon la revendication 1, caractérisée en ce que la vitesse du mouvement en avant et du mouvement en arrière de la tige de piston (2) est commandée - de préférence par l'intermédiaire d'organes de commande mécaniques - en fonction du parcours du coulisseau de presse (3), cette dernière étant également déplacée le cas échéant à différentes vitesses d'entraínement lors du mouvement en arrière de la tige de piston (2).
  3. Méthode selon la revendication 1 ou la revendication 2, caractérisée en ce que la vitesse de la tige de piston (2) est augmentée au moins deux fois vers l'avant après que le point d'intersection a été atteint.
  4. Méthode selon l'une quelconque des revendications précédentes, caractérisée en ce que la variation de vitesse a lieu par la mise en service ou hors service - le cas échéant progressive - de surfaces de piston (8-10) actives par voie hydraulique.
  5. Presse à levier articulé ou à genouillère comportant un groupement de pistons de cylindre commandé par voie hydraulique dans laquelle avant que la phase d'intersection (contact de l'outil avec la pièce) ne soit atteinte, la vitesse du coulisseau de presse est réduite et la force de compression du coulisseau (3) est augmentée, caractérisée en ce que pour la commande, on prévoit des soupapes hydrauliques qui sont directement ou indirectement reliées par un organe de réaction (14 ; 115) dépendant du parcours et ajustant la course de la tige de piston (2) ou du coulisseau (3) de presse, la vitesse du mouvement en avant de la tige de piston (2) étant au moins augmentée une fois après que le point d'intersection a été atteint et avant le déclenchement du mouvement en arrière.
  6. Presse selon la revendication 5, caractérisée en ce qu'il est prévu, en tant que groupement de pistons de cylindre, au moins un cylindre différentiel comportant au moins un cylindre plongeur (11) intégré.
  7. Presse selon la revendication 5, caractérisée en ce que la variation de vitesse a lieu par la mise en service ou hors service - le cas échéant progressive - de surfaces de piston (8-10) actives par voie hydraulique.
  8. Presse selon l'une quelconque des revendications 5 à 7, caractérisée en ce qu'au moins un cylindre du groupement de pistons de cylindre (1) est disposé de manière fixe avec le coulisseau.
  9. Presse selon l'une quelconque des revendications 5 à 8, caractérisée en ce qu'au moins un cylindre de travail (en particulier pour le mouvement en arrière du coulisseau de presse (3) - assiste un cylindre différentiel comportant au moins un cylindre plongeur (11) intégré.
  10. Presse selon l'une quelconque des revendications 5 à 9, caractérisée en ce qu'au moins un cylindre de travail auxiliaire (44) fixé dans le bâti de la presse assiste au moins un cylindre de travail principal (13) fixé avec le coulisseau - de préférence un cylindre différentiel comportant un cylindre plongeur intégré (11) - dont la tige de piston (2) est assemblée avec les genouillères (5-7), la tige de piston dudit cylindre de travail auxiliaire (44) étant assemblée avec le coulisseau de la presse (3).
EP19940104561 1993-03-23 1994-03-23 Méthode de commande hydraulique d'une presse à levier articulée ou à genoullière et presse à levier articulée ou à genoullière avec un système de commande adapté à la mise en oeuvre de la méthode Expired - Lifetime EP0616882B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CH87093 1993-03-23
CH870/93 1993-03-23
CH2277/93 1993-07-28
CH227793 1993-07-28

Publications (2)

Publication Number Publication Date
EP0616882A1 EP0616882A1 (fr) 1994-09-28
EP0616882B1 true EP0616882B1 (fr) 1998-01-14

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Application Number Title Priority Date Filing Date
EP19940104561 Expired - Lifetime EP0616882B1 (fr) 1993-03-23 1994-03-23 Méthode de commande hydraulique d'une presse à levier articulée ou à genoullière et presse à levier articulée ou à genoullière avec un système de commande adapté à la mise en oeuvre de la méthode

Country Status (5)

Country Link
US (1) US5562026A (fr)
EP (1) EP0616882B1 (fr)
JP (1) JPH0775900A (fr)
AT (1) ATE162134T1 (fr)
DE (1) DE59404987D1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004046493A1 (de) * 2004-08-18 2006-03-02 Müller Weingarten AG Presse insbesondere zur Herstellung von Formteilen aus Kunststoff
DE202013003622U1 (de) 2013-04-18 2014-07-21 Bümach Engineering International B.V. Abschnittsgedämpfter Plungerzylinder
DE202013003623U1 (de) 2013-04-18 2014-07-21 Bümach Engineering International B.V. Abschnittsgedämpfter Plungerzylinder

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19918700A1 (de) 1999-04-26 2000-11-02 Mueller Weingarten Maschf Hydromechanischer Pressenantrieb
DE10028147B4 (de) * 2000-06-07 2004-12-02 Schuler Pressen Gmbh & Co. Kg Verfahren und Vorrichtung zum Betreiben einer Werkstücktransportvorrichtung für eine Pressenanlage
JP2006334660A (ja) * 2005-06-06 2006-12-14 Toyota Motor Corp プレス成形方法
JP5708463B2 (ja) * 2011-12-08 2015-04-30 トヨタ自動車株式会社 油圧プレス装置の制御方法
CN105729998B (zh) * 2016-04-19 2018-10-26 唐山瑞可达科技有限公司 平压平烫金模切机运动平台调整装置

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US1007792A (en) * 1910-10-17 1911-11-07 Bliss E W Co Press.
FR953349A (fr) * 1947-09-04 1949-12-05 A Hubert M Juy Ets Embiellage pour machines à comprimer et autres machines analogues à grande course
CH273192A (de) * 1948-08-24 1951-01-31 May Otto Ing Dr Kniehebelpresse.
US2780117A (en) * 1952-11-25 1957-02-05 Nat Lead Co Press for forging metal
CH498701A (it) * 1969-07-16 1970-11-15 Internat Press Dev Establishme Dispositivo di chiusura per presse, in particolare per iniezione o per pressofusione
DE2357824B2 (de) * 1973-11-20 1976-01-08 Maschinenfabrik Weingarten Ag, 7987 Weingarten Antrieb für den Stössel mechanischer Pressen
CA1127450A (fr) * 1978-08-26 1982-07-13 Gordon L. Mcglennon Mecanismes multiplicateurs d'efforts
DE2925416C2 (de) * 1979-06-23 1983-02-24 Werner Ing.(Grad.) 6460 Gelnhausen Leinhaas Kniehebel-Blechschneidepresse
WO1988004990A1 (fr) * 1986-12-29 1988-07-14 Mitoshi Ishii Procede de commande d'une presse et servocommande utilisee a cet effet
DE4036564A1 (de) * 1990-11-16 1992-05-21 Bosch Gmbh Robert Hydraulische einrichtung zur steuerung eines arbeitszylinders einer presse

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004046493A1 (de) * 2004-08-18 2006-03-02 Müller Weingarten AG Presse insbesondere zur Herstellung von Formteilen aus Kunststoff
DE102004046493B4 (de) * 2004-08-18 2013-02-28 Schuler Pressen Gmbh Presse insbesondere zur Herstellung von Formteilen aus Kunststoff
DE202013003622U1 (de) 2013-04-18 2014-07-21 Bümach Engineering International B.V. Abschnittsgedämpfter Plungerzylinder
DE202013003623U1 (de) 2013-04-18 2014-07-21 Bümach Engineering International B.V. Abschnittsgedämpfter Plungerzylinder
EP2792890A1 (fr) 2013-04-18 2014-10-22 Bümach Engineering International B.V. Vérin à piston plongeur amorti par sections
EP2799726A1 (fr) 2013-04-18 2014-11-05 Bümach Engineering International B.V. Vérin à piston plongeur amorti par sections

Also Published As

Publication number Publication date
ATE162134T1 (de) 1998-01-15
US5562026A (en) 1996-10-08
JPH0775900A (ja) 1995-03-20
EP0616882A1 (fr) 1994-09-28
DE59404987D1 (de) 1998-02-19

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