EP0216776B1 - Systeme de reglage de pression pour un embrayage et/ou un frein a commande hydraulique pour l'arbre d'entrainement d'une presse - Google Patents

Systeme de reglage de pression pour un embrayage et/ou un frein a commande hydraulique pour l'arbre d'entrainement d'une presse Download PDF

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Publication number
EP0216776B1
EP0216776B1 EP19850903265 EP85903265A EP0216776B1 EP 0216776 B1 EP0216776 B1 EP 0216776B1 EP 19850903265 EP19850903265 EP 19850903265 EP 85903265 A EP85903265 A EP 85903265A EP 0216776 B1 EP0216776 B1 EP 0216776B1
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EP
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Prior art keywords
pressure
press
valve
line
safety valve
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Expired
Application number
EP19850903265
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German (de)
English (en)
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EP0216776A1 (fr
Inventor
Lothar GRÖTZINGER
Alfred Hyrenbach
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Herion Systemtechnik GmbH
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ZF Herion Systemtechnik GmbH
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Application filed by ZF Herion Systemtechnik GmbH filed Critical ZF Herion Systemtechnik GmbH
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    • 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
    • B30B15/142—Control arrangements for mechanically-driven presses controlling the brake or the clutch

Definitions

  • the invention relates to Druckbeein kgungsein- T ichtungen for hydraulically actuated clutch-brake combination or separately arranged clutches and brakes for the drive shaft of a press.
  • a pressure damper for a hydraulic application, which consists of a pressure-dependent locking slide in a pressure relief line branching off the line carrying the hydraulic fluid, in which throttle channel cross sections, which are variable as a function of the differential pressure, differ by a locking member provided with a preselectable cone Pressure relief effects should cause automatically depending on the position of the press ram.
  • This variant also makes it difficult to fill up the actuating cylinder quickly and makes it impossible to make major changes to the setting without dismantling the damper locking element, e.g. B. for the purpose of using a truncated cone with other slopes.
  • the viscosity influences are also of particular importance here.
  • temporal extensions of the entire press stroke due to the expansion of the travel path due to the slower inflowing oil cannot be ruled out, so that the partial output of the press can also decrease.
  • a separate influencing of the emptying or braking phase after passing through the working area of the press is also not provided here or is not possible.
  • the object of the invention is seen in further developing the pressure influencing devices for hydraulic actuation in such a way that, while avoiding damping valves in the feed line downstream of the press safety valve and also highly viscosity-dependent, only pressure medium-actuated switching elements, both for coupling or the pressure build-up as well as for braking or pressure reduction shock-absorbing and quickly functioning pressure modulation is achieved, which, however, z. B. for adjustment work, quickly cancel or change without internal intervention and then repeats easily identically.
  • the solution is achieved with the characterizing features of claim 1 essentially by using a directional control valve that can be electrically adjusted to a blocking position and a plurality of pressure relief stages with return to the tank, each with differently throttling pressure relief conditions between the press safety valve linked to it and the actuating cylinder in exact association with the respective
  • the press ram position is driven and can be adjusted sensitively, without interference from flow obstacles in the main path to or from the actuating cylinder having to be accepted. Due to the adjustability of different pressure levels in parallel branches of the pressure relief line when it can be activated via a single common directional valve and its electrical function linkage with the press safety valve, the movement of the locking elements is so reliable that the selected operating conditions can be maintained exactly and can be easily found again after changes in operation are.
  • valve e.g. by using a plug with a different inclination
  • both pressure and quantity values as well as activation times can be varied within wide limits or adapted to requirements without the individual work cycles the press strokes are more necessary wise to stretch in time.
  • the device which can preferably be implemented in the cartridge principle, is free of space problems, since the control elements can be inexpensively installed outside the area of the actuating cylinder.
  • the control electronics also enable various automatic safety checks for each individual operating phase and rapid error detection. Thanks to flow obstacles such. B. throttle valves, free main feed line of the actuating cylinder, a very fast filling of the cylinder, i.e. short cycle times with soft starting, clutching and braking, and thus a reduction in noise and wear in all engagement and disengagement processes of the entire press stroke is achieved without wasting time.
  • the device can be used almost identically for any type of press, since neither, e.g. B. in the clutch or brake of the press, special spring or surface adjustments made even valve inserts in special damper valves for different operating conditions must be replaced. Once set values have been changed even after interim changes, e.g. B. for single stroke, identifiable quickly, and changing a pressure phase of the partial strokes does not necessarily result in a change in the following partial strokes. In clutch-brake combinations, neither springs nor piston surfaces need to be different, so that simple manufacturing conditions also arise in this regard.
  • an advantageous for 2 partial pressure levels and a maximum pressure embodiment with a refill option from a parallel to the feed line of the actuating cylinder pressure line from the pump of the system or from a memory is proposed, which contributes with a special automatic shutoff valve that both pressure build-up and Depressurization takes place quickly and always under the same preselected conditions.
  • a special automatic shutoff valve that both pressure build-up and Depressurization takes place quickly and always under the same preselected conditions.
  • the automatic refill option for the memory is also provided for situations in which the shut-off valve is closed and at the same time the shut-off valve is kept free of differential pressure influences.
  • the two line branches of the pressure limitation stage are protected by a separate pressure damping device against interference from the feed line.
  • the starting phase is started with a reduced pressure by a predetermined amount in a branch of the pressure relief line of the pressure fluid in the feed line can first be discharged into the tank via the pressure relief line or the directional control valve.
  • a further damping phase is initiated towards the end of a press stroke in that the braking torque for the press ram is reduced to a level that is just required by a further relief position of the directional valve.
  • the press stroke is ended quickly and clearly after the previous braking by opening the drain opening of the press safety valve and closing the pressure relief line via the directional valve.
  • the invention also offers the possibility of connecting the electrical connection between the press safety valve and the directional control valve to a safety circuit (not shown), which reports any deviation from the desired state and also the source of the fault, or switches off the press when or as soon as the damping does not work according to the setting.
  • a safety circuit not shown
  • appropriate signal transmitters and further directional valves can be used to arrange any number of pressure stages in the same way without having to provide any flow regulators in the actual feed line from the press safety valve to the actuating cylinder.
  • Fig. 1 the most important elements of the hydraulic system and the most important electrical connections with the signal or position sensors on the press or on its plunger or drive shaft are shown in the position which they are at top dead center (zero position) of the press ram Take home position 0.
  • the pump 2 takes hydraulic fluid into the feed line 3, which finally opens via the press safety valve 4 into the actuating cylinder 5 of the brake 6 or the clutch 7 of the clutch-brake combination.
  • an actuating piston 8 is supported against a clutch-side return spring 9.
  • the piston rod 10 can rest on the brake 6 or clutch 7.
  • the brake 6 is activated because the press safety valve 4 is relieved of pressure to the tank 1, so that the return spring 9 can press the piston 8 and its rod 10 against the brake 6, whereby the press ram, not shown, is locked.
  • a pressure cut-off valve 16 is connected via line 12, which uses a check valve 51 to control the feed pressure in front of the press safety valve 4, irrespective of its position and any previous withdrawals, and, with the appropriate setting, allow excess fluid to flow back into the tank 1.
  • the line 13 has a check valve 17 that prevents backflow and is a pressure compensation line for a further pressure-maintaining system.
  • This directional control valve 23 is the termination of the pressure relief line 15, which branches off the current after the press safety valve 4 and whose outputs, depending on the position, either turn to the tank 1 or into the aforementioned connection line 22.
  • the pressure relief line 15 located upstream of the directional control valve 23 there is initially a damping valve 24, seen downstream, in whose spring-loaded floating piston an internal throttle is arranged downstream and which can release an outlet to the tank 1 if the pressure is too sudden or too high.
  • the pressure relief line 15 then branches into two branches 25, 26, each of which has its own adjustable and pressure-dependent pressure relief valve 27, 28.
  • One branch 25 then opens into a first press-side connection 29 of the 4/3-way valve 23, while the second branch 26 opens into a second press-side connection 30 there.
  • Both connections 29, 30 are in the initial position shown in FIG Zero position 0 of the press in locked position, d. that is, there is no pressure relief.
  • the accumulator 19 releases volume via the check valve 53 when engaging.
  • the directional control valve 23 is switched again after a start phase 41, 42, as a result of which the accumulator 19 can then only be filled via the throttle 54. After the shut-off valve 18 is closed, the accumulator 19 is only connected to the feed line 14 via the throttle 52.
  • the press safety valve 4 is shown here in a simplified manner so that it is provided on one side with magnetic actuators 31 for opening a passage position, which work against return springs 32 on the other side.
  • the directional valve 23 has magnetic actuators and return - springs 33, 34 and 35, 36, which are opposite each other and separately operable are an electrical control system 37 which is coupled together via a switch box 38 to the solenoid actuator 31 of the press safety valve 4 and its switching commands both from Hand as well as one or more signal generator (s) 39 can receive the z. B. from path, time or angle encoders on the press, in the press ram or the drive shaft, etc., may exist.
  • a first changeover position is generally arranged at approximately 10 to 20 ° after the initial position 0.
  • there is only then an increase in pressure for the clutch which leads to the working area 43A of the tappet being reached at approximately 120 to 150 °.
  • the actuating piston 8 is then pushed back into its initial position in the region 44 and the braking is carried out in the region 45 until the valves 4 and 23 are brought back to the initial position, that is to say in the pressure relief position, at the third switchover point at approximately 340 to 350 ° . Valves 4 and 23 are located in area 46 back to the starting position.
  • Fig. 3 the positions of the magnetic actuators 31, 33, 35 or the valves 4 and 23 corresponding to the above sequence are shown in a table.
  • the full points mean excitation of the respective magnetic actuator, the open circles the rest position and the crossings the blocking of the valve passage in question.
  • all actuators are in the initial position, that is, the magnetic actuators 31, 33 and 35 are not energized, and the press safety valve 4 in the pressure relief position and the directional control valve 23 in the blocking position.
  • the magnetic actuator 31 is energized, so that the press safety valve 4 releases inlet to the actuating cylinder 5.
  • the first pressure relief position of the directional control valve 23 is activated by excitation of the first magnetic actuator 33, that is to say a filling pressure deviating from the pump pressure is driven.
  • press safety valve 4 or magnetic actuator 31 remains activated, however directional control valve 23 or its magnetic actuator 33 returns to the blocking position and thus causes the full pump pressure to be available as filling pressure on actuating cylinder 5 for work area 43.
  • the press safety valve 4 or the magnetic actuator 31 remains activated, however, the magnetic actuator 35 or its directional control valve 23 now opens via another pressure relief outlet and thus brings about a pressure reduction which does justice to the reduced torque in the braking phase 45 .
  • the press stroke ends with the deactivation of the press safety valve 4 by the return of the magnetic actuator 31 to the pressure relief position and the magnetic actuator 35 to the blocking position.
  • the various pressures in the actuating cylinder 8 are shown schematically with continuous lines 47, the torque curve at the clutch M K with dashed lines 48 and the speed curve n with dash-dotted lines 49 over the time t of a press stroke.
  • the response pressure PA that is, for. B. overcome the spring resistance and static friction before the pressure PK sufficient to close the clutch is reached.
  • the pressure increases up to the value of the so-called switch-on pressure P E , at which the clutch retains torque M K until the clutch engagement is complete and then the actual press work area 43A with the pressure rising to the nominal pressure P N begins.
  • the pressure runs out after a pressure reduction area 44, in which the pressure fluid is pushed out of the brake cylinder 8, with a brake area 45 reduced by the hydraulic counter pressure P H.
  • the speed change is initiated smoothly by the braking effect of the braking pressure APg r .
  • a braking torque M B can be switched until the speed n has completely dropped to 0.
  • the filling pressure in the brake cylinder 8 is thus reduced to low pressure before the end of the phase in order to avoid shock, and in the region 46 the valves 4 and 23 are again in the starting position.
  • the press speed n only begins at the point of engagement of the clutch at the end of the start phase 41, reaches its maximum before the end of the pressure build-up area 42, remains at this value during the work area 43A and the constant area 43B.
  • the pressure reduction area 44 With the beginning of the pressure reduction area 44, it drops to a low pressure and towards the end of the press stroke with a reduced braking area 45 quickly returns to 0 in the starting position 46.
  • the continuously increasing or decreasing gradual acceleration and deceleration in the shortest possible time cause shocks when tearing loose in the starting phase just as avoided or greatly reduced as when braking after the end of the pressing work.
  • the difference compared to a previously customary type of pressure influencing by means of a throttle section after the press safety valve 4 according to the prior art mentioned at the beginning of the description is indicated by the pressure curve 50, which is also shown in FIG. 4 with a dotted line.
  • the functional sequence begins at top dead center in zero position 0 with the press ram stationary, in the start phase 41, 42 with the downward stroke and the excitation of the magnetic actuator 31 of the press safety valve 4 and of the first magnetic actuator 33 on the directional control valve 23, which has a pressure compensation preselected on the pressure limiting valve 27 brings about the first branch 25 of the pressure relief line 15.
  • the accumulator 19 delivers oil via the check valve 53 or line 14 into the main feed line 3, as long as the shut-off valve 18 is relieved on the spring side via line 14A and line 22 via directional valve 23 to tank 1.
  • the throttle 21 prevents oil from flowing back into the line 14A from there, and that the shut-off valve 18 would thereby close again too soon.
  • the pressure in the actuating cylinder 5 initially rises in accordance with the spring characteristic at maximum delivery rate (without throttling effect in FIG. 3) Line quickly up to the spring pressure P F , then further due to the spring characteristic of the clutch 7 up to the clutch closing pressure P K. Only now that no more compression volume is needed, the pressure corresponding to the total delivery rate from pump 2 and accumulator 19 increases rapidly to a value preselected at pressure relief valve 27, which is above the closing pressure P K of the clutch and which acts as switch-on pressure P E. With the same, the damper valve 24 is relieved on the spring side and can release excess pressure to the tank 1, so that the pressure in the actuating cylinder 5 remains constant at a reduced value during this phase.
  • the acceleration of the drive shaft of the press is thus controlled with the differential pressure which results from the value set on the pressure relief valve 27 and the closing pressure P K of the clutch.
  • This relatively low acceleration pressure dP ae he therefore follows the speed change on the shaft from 0 to operating speed with a much lower pressure surge than at full pump pressure, that is to say in a short time period.
  • the oil from the pump 2 can flow via the lines 13, 14 and 20 only via the throttle 54 to the accumulator 19, so that it is automatically refilled until the next starting process , and the nominal pressure in the feed line 3 is immediately available while there is no pressure relief via the directional valve 23.
  • the magnetic actuator 35 is then energized and the line branch 30 is thus switched to pressure relief in the direction of tank 1.
  • the nominal pressure present before and after the damper valve 24 thus opens the pressure limiting valve 28, which is adjusted to a value set below the spring pressure P F.
  • the relevant stop point of the signal transmitter 39 is placed so that the excitation of the magnetic actuator 35 is adjusted electrically so that the press ram comes to exactly at top dead center, in the starting position 0.
  • the damper valve 24 can open on the spring side, relieve the pressure on the actuating cylinder 5, so that the piston rod 10 is pressed back under spring force away from the clutch 7 to the brake 6. This is then effective under spring pressure.
  • a preselectable hydraulic back pressure is generated via the pressure relief valve 28, the brake does not stop hard, but rather with shock absorption.
  • the pressure drop in the valves 24 and 28 and the directional control valve 23 is maintained via the press safety valve 4 from the supply quantity of the accumulator 19 via the throttle 52, so that the effective braking pressure ⁇ P Br is derived from the spring pressure P F minus the hydraulic counter pressure at the pressure relief valve 26 corresponds.
  • Both the magnetic actuator 31 on the press safety valve 4 and the magnetic actuator 35 on the directional control valve 23 are switched off shortly before reaching the starting position 0 at top dead center at about 340 to 350 ° of the press stroke, so that the actuating cylinder 5 of the press is neither via the main feed line 3 nor via the parallel lines 22, 15 can be pressurized. This guarantees a safe total shutdown. - Thanks to the parallel connection of the pressure compensation system to the feed line, the entire process takes place almost as quickly as without damping when coupling and braking.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Presses (AREA)

Abstract

Le système de réglage de pression pour limiter et atténuer les opérations de démarrage et de freinage, qui est adapté aux exigences du fonctionnement d'une presse au moyen d'un système de commande électrique (37, 38, 39) suivant la course, le temps ou l'angle, empêche à chaque cycle des restrictions dans la ligne d'alimentation (3) entre la valve de sécurité (4) de la presse et le cylindre d'actionnement (5), et permet d'obtenir un comportement optimum de la pression par une ligne parallèle (15) qui y est introduite, à travers laquelle, selon la position de consigne d'une valve de distribution (23) montée à l'intérieur, on peut diminuer ou augmenter la pression dans une mesure prédéterminée sans une perte considérable de temps. Un système de maintien de la pression, qui lui-même est indépendant de la position de la valve de sécurité de la presse, avec un ensemble de stockage (19) et un système d'appoint, permet non seulement la détente de la pression vers le réservoir (1), mais également l'entrée ou l'élimination d'une pression supplémentaire de la ligne d'alimentation (3) directement après la commutation des éléments de réglage (31, 33, 35) qui commandent les valves (4, 23) et sont déclenchés par des émetteurs de signaux (39) marquant les differents coups partiels de la presse.

Claims (9)

1. Dispositif de réglage de pression pour un embrayage et/ou un frein à commande hydraulique pour l'arbre d'entraînement d'une presse,
a) dans lequel une soupape (4) de sécurité de la presse, montée sur une conduite d'alimentation (3) débouchant dans un cylindre d'actionnement (5), et une soupape à plusieurs voies (23), commandée de manière à décharger la pression ou à la bloquer, coopèrent par des combinaisons de phases de pression partielle et de pression complète dans le sens d'un amortissement des à- coups, caractérisé en ce que :
b) la soupape à plusieurs voies (23) est disposée, sur une conduite de décharge (15) dérivée de la conduite d'alimentation (3), en aval d'un étage (27, 28) de limitation ou de réduction proportionnelle de la pression, lequel est ajustable de l'extérieur,
c) aussi bien la soupape de sécurité (4) que la soupape à plusieurs voies (23) disposent d'organes de commande électromagnétiques (31, 33, 35) qui sont reliés les uns aux autres par un dispositif de commande électrique programmée (37, 38) raccordé, sur la presse, à des capteurs (39) d'angle de rotation, de course ou de durée,
d) le dispositif de commande électrique (37, 38) et/ou les organes de commande électromagnétiques (31, 33, 35) sont pourvus d'un moyen de présélection pour régler la pression de travail dans le cylindre (5) tant lorsqu'elle augmente (embrayage) que lorsqu'elle diminue (freinage).
2. Dispositif selon la revendication 1, caractérisé :
a) en ce que la soupape à plusieurs voies (23) est une soupape à 4/3 voies,
b) dont les deux raccords (29, 30) du côté de la presse sont précédés de soupapes (27, 28) de limitation ou de réduction proportionnelle de pression, montées sur deux branches parallèles (25, 26) de la conduite de décharge (15),
c) et dont les raccords (22, 1) du côté opposé sont reliés respectivement à un réservoir (1) et, par une conduite particulière d'équilibrage de pression (22), à une soupape d'arrêt (18) d'un accumulateur hydraulique (19), cette soupape étant commandée automatiquement en fonction de la pression.
3. Dispositif selon la revendication 2, caractérisé :
a) en ce que la soupape d'arrêt (18) est raccordée d'un côté à la conduite d'alimentation (3) en amont de la soupape de sécurité (4), et de l'autre côté à l'accumulateur (19),
b) et en ce que son organe de fermeture présente des rapports de surfaces qui assurent le . maintien de la soupape d'arrêt (18) en position fermée sous l'effet des différences de pression résultant de la position initiale de la soupape à plusieurs voies (23).
4. Dispositif selon la revendication 2 ou 3, caractérisé en ce que l'accumulateur (19) est agencé pour un équilibrage de sa pression au moyen d'une conduite d'équilibrage (13) comportant un clapet anti-retour (17) qui la ferme en direction de la conduite d'alimentation (3).
5. Dispositif selon l'une des revendications 1 à 4, caractérisé en ce que, dans la conduite de décharge (15), une soupape d'amortissement (24), ayant sa propre commande de vidange en fonction de la pression, est prévue en amont de l'étage de limitation de pression (27, 28).
6. Dispositif selon l'une des revendications 1 à 5, caractérisé en ce que, au départ de la course de la presse à partir d'une position neutre (point zéro), la soupape de sécurité (4) est en position de passage et la soupape à plusieurs voies (23) est en position de vidange vers le réservoir (1) pour son premier raccord (29) du côté de la presse.
7. Dispositif selon la revendication 6, caractérisé en ce que la position de vidange du premier raccord (29) de la soupape à plusieurs voies (23) est supprimée à un stade se trouvant entre environ 10° et 20° au-delà du point zéro, tandis que la soupape de sécurité (4) reste en position de passage.
8. Dispositif selon la revendication 6 ou 7, caractérisé en ce que la soupape à plusieurs voies (23) est mise en position de vidange vers le réservoir (1) pour son second raccord (30) du côté de la presse à un stade se trouvant entre environ 270° et 320° au-delà du point zéro, tandis que la soupape de sécurité (4) reste en position de passage.
9. Dispositif selon l'une des revendications 6 à 8, caractérisé en ce que, à un stade se trouvant entre environ 340° et 350° au-delà du point zéro, la soupape de sécurité (4) revient en position de décharge de la pression et la soupape à plusieurs voies (23) revient en position de blocage.
EP19850903265 1984-07-19 1985-06-28 Systeme de reglage de pression pour un embrayage et/ou un frein a commande hydraulique pour l'arbre d'entrainement d'une presse Expired EP0216776B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP8400225 1984-07-19
WOPCT/EP84/00225 1984-07-19

Publications (2)

Publication Number Publication Date
EP0216776A1 EP0216776A1 (fr) 1987-04-08
EP0216776B1 true EP0216776B1 (fr) 1988-10-19

Family

ID=8164954

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Application Number Title Priority Date Filing Date
EP19850903265 Expired EP0216776B1 (fr) 1984-07-19 1985-06-28 Systeme de reglage de pression pour un embrayage et/ou un frein a commande hydraulique pour l'arbre d'entrainement d'une presse

Country Status (4)

Country Link
EP (1) EP0216776B1 (fr)
JP (1) JPS61502735A (fr)
DE (2) DE3565651D1 (fr)
WO (1) WO1986000849A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4416194A1 (de) * 1994-05-06 1995-11-09 Rexroth Mannesmann Gmbh Regelsystem für einen hydraulisch betätigten Verbraucher eines Nutzfahrzeugs
GB2374392B (en) * 1997-07-14 2002-11-27 Luk Getriebe Systeme Gmbh Transmission
DE19831144A1 (de) * 1998-07-11 2000-01-13 Mannesmann Rexroth Ag Hydraulische Steuerung für eine hydraulisch betätigbare Kupplungsbremskombination für die Antriebswelle einer mechanischen Presse
US6260357B1 (en) * 1998-11-30 2001-07-17 Caterpillar Inc. Quick coupler control system
WO2001012997A2 (fr) * 1999-08-13 2001-02-22 Herion Systemtechnik Gmbh Soupape de securite de presse
EP1211059B1 (fr) * 2000-12-02 2006-08-16 Bosch Rexroth AG Commande hydraulique pour combinaison embrayage-frein à actionnement hydraulique en particulier pour l'arbre excentrique d'une presse mécanique
DE10062229A1 (de) * 2000-12-02 2002-06-13 Mannesmann Rexroth Ag Hydraulische Steuerung für eine hydraulisch betätigbare Kupplungsbremskombination insbesondere an der Exzenterwelle einer mechanischen Presse
EP1275854A1 (fr) * 2001-07-09 2003-01-15 Herion Systemtechnik GmbH Méthode et dispositif hydraulique de commande pour la protection contre les surcharges d'une presse mécanique actionnée par une combinaison embrayage-frein
JP2005530618A (ja) * 2002-05-24 2005-10-13 メッツォ・リンデマン・ゲゼルシャフト・ミット・ベシュレンクテル・ハフツング スクラップシャー駆動用油圧システム等のための油圧制御装置
DE102006050300B4 (de) * 2006-10-23 2013-05-08 Ortlinghaus-Werke Gmbh Druckmittelbetätigte Schaltung

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1053255B (de) * 1955-12-05 1959-03-19 Eumuco Ag Fuer Maschb Reibungskupplung mit oelhydraulischer Betaetigung des Kupplungsgliedes, insbesonderefuer Pressen, Scheren u. dgl.
DE1502319A1 (de) * 1965-01-05 1969-04-10 Schuler Gmbh L Pressenkupplung
DE2935702A1 (de) * 1979-09-04 1981-03-12 Herion-Werke Kg, 7012 Fellbach Schaltungsanordnung.
ATE6231T1 (de) * 1980-10-31 1984-03-15 L. Schuler Gmbh Steuerung fuer die kupplung und/oder bremse einer presse.

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Publication number Publication date
JPS61502735A (ja) 1986-11-27
WO1986000849A1 (fr) 1986-02-13
DE3523163A1 (de) 1986-02-13
EP0216776A1 (fr) 1987-04-08
DE3565651D1 (fr) 1988-11-24

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