EP0216776A1 - 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.

Info

Publication number
EP0216776A1
EP0216776A1 EP19850903265 EP85903265A EP0216776A1 EP 0216776 A1 EP0216776 A1 EP 0216776A1 EP 19850903265 EP19850903265 EP 19850903265 EP 85903265 A EP85903265 A EP 85903265A EP 0216776 A1 EP0216776 A1 EP 0216776A1
Authority
EP
European Patent Office
Prior art keywords
pressure
press
valve
line
safety valve
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.)
Granted
Application number
EP19850903265
Other languages
German (de)
English (en)
Other versions
EP0216776B1 (fr
Inventor
Lothar Grotzinger
Alfred Hyrenbach
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.)
Herion Systemtechnik GmbH
Original Assignee
ZF Herion Systemtechnik 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=8164954&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0216776(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by ZF Herion Systemtechnik GmbH filed Critical ZF Herion Systemtechnik GmbH
Publication of EP0216776A1 publication Critical patent/EP0216776A1/fr
Application granted granted Critical
Publication of EP0216776B1 publication Critical patent/EP0216776B1/fr
Expired legal-status Critical Current

Links

Classifications

    • 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

  • Pressure influencing device for a hydraulically operated clutch and / or brake of the drive shaft of a press
  • the invention relates to pressure influencing devices for hydraulically actuatable clutch-brake combinations or separately arranged clutches or brakes for the drive shaft of a press.
  • E-PS 00 51 684 z For example, it was suggested that the actuating cylinder be preceded by a program-controlled proportional valve in the feed line and that the press stroke be started with an intermediate pressure that was greatly increased compared to a partial pressure, and then that the desired speed should be set by switching to a lower partial pressure before the max. Working pressure for the actual work process is released. Not only is a sudden start associated with high mechanical loads on the drive elements, but the arrangement of a throttle in the feed line also slows down the oil flow to and from the actuating cylinder, so that longer switching times also result with increased damping. This reduces the parts output. There is also no influence on the pressure reduction or braking phase at the end of the press stroke. In addition, safety concerns against the arrangement of a damping valve in the main pressure line itself appear justified.
  • 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 pressure fluid, in which differential throttle channel cross sections, dependent on the differential pressure, through a preselectable slope with a truncated cone provided locking member to cause different pressure relief effects 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, for example.
  • the device which can preferably be implemented in the cartridge principle, is free from 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 controls for each individual operating phase and rapid error detection. Thanks to flow obstacles such. B. throttle valves, the main feed line of the actuating cylinder kept free, the cylinder is filled very quickly, that is to say short cycle times with soft starting, clutching and braking, and thus a reduction in noise and wear during all engagement and disengagement processes of the entire press stroke without loss of time reached.
  • 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 also made valve inserts in special damper valves for different operating conditions must be exchanged. Once set values have been changed even after interim changes, e.g. B. for single stroke, can be found identically again quickly, and the change in a pressure phase of the partial strokes does not necessarily also entail 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 embodiment for two partial pressure stages and a maximum pressure with a refill possibility 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 shut-off valve that both pressure build-up as well as pressure reduction run quickly and always under the same preselected conditions.
  • a precaution is taken to automatically switch off interference from the parallel pressure line into the feed line with certainty.
  • 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-limiting stage are protected by a separate pressure damping device against interference from the feed line.
  • the starting phase is started with a reduced pressure, in that a partial quantity of the pressure fluid in the feed line predetermined in a branch of the pressure relief line can first be discharged into the tank via the pressure relief line or the directional 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 unequivocally 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 furthermore offers the possibility of connecting the electrical linkage between the press safety valve and the directional 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
  • Fig. 1 is a circuit diagram of a Druckbeeinflus ⁇ sungs adopted for a clutch-brake combination a press.
  • Fig. 1A shows the connection possibility of the same
  • FIG. 2 is the circulation diagram of a press stroke that determines the pressure influencing phases.
  • 3 is an associated switching position table of the magnetic actuators on the press safety valve and directional control valve.
  • FIG. 4 is a working diagram of a press stroke with the pressure influencing device according to the invention. 1 shows the most important elements of the hydraulic system and the most important electrical connections with the signal and position transmitters on the press or on its tappet or drive shaft in the position which they have at top dead center (zero position) ) of the press ram as starting 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 in the actuating cylinder 5 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, thereby locking the press ram, not shown is.
  • a pressure cut-off valve 16 is connected via the line 12, which is switched off by a switch-back valve 51 maintains the feed pressure upstream of the press safety valve 4, irrespective of its position and any previous withdrawals, and, with the appropriate setting, allows excess fluid delivered to flow back into the tank 1.
  • the line 13 has a non-return valve 17 and is a pressure compensation line for a further pressure maintenance system.
  • This directional valve 23 is the completion of the pressure relief load line 15, which branches off the current after the press safety valve 4 and, depending on its position, turn its outputs either 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 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 in Fig. 1 shown initial position or zero position 0 of the press in the locked position, ie 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, for opening a passage position, it is provided on one side with magnetic actuators 31 which work against return springs 32 on the other side.
  • the directional control valve 23 has magnetic actuators and return springs 33, 34 and 35, 36, which lie opposite one another and can be actuated separately from one another via an electrical control system 37, which is coupled to the magnetic actuator 31 of the press safety valve 4 via a switch box 38 and its switching commands both from Hand as well as one or more signal generator (s) 39 can receive the z. B. from distance, time or angle encoders on the press, in the press ram or the drive shaft, etc., may exist.
  • the feed line 3 with a separate arrangement of the brake 6 and clutch 7 is only divided into their separate actuating cylinder 5, without the need for separate switching elements.
  • 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 ram at approximately 120 to 150 °.
  • valves 4 and 23 are again in the start position.
  • Fig. 3 the positions of the magnetic actuators 31, 33, 35 and 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, i.e. 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 excited, so that the press safety valve 4 releases inlet to the actuating cylinder 5.
  • the first pressure relief position of the directional 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 With a press stroke of approximately 10 to 20 °, press safety valve 4 or magnetic actuator 31 remains activated, however directional valve 23 or its magnetic actuator 33 returns to the blocking position and thus causes the full pump pressure as the filling pressure on actuating cylinder 8 for the working area 43 is available.
  • 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 causes a pressure reduction which corresponds to the reduced torque in the braking phase 45 justice.
  • 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 pressure increases up to the value of the so-called switch-on pressure P ′′, at which the clutch maintains torque M ′′ until the clutch engagement is complete and the pressure rises to the nominal pressure P N then the actual press work area 43A begins.
  • the pressure runs down to a pressure reduction area 44, in which the pressure fluid is pushed out of the brake cylinder 8, with a braking area 45 reduced by the hydraulic counterpressure P ".
  • the speed change is initiated smoothly by the braking effect of the braking pressure ⁇ P.
  • a braking torque M_ 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 area 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 starting 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 drops back to 0 in the starting position 46.
  • the steadily increasing or decreasing step-by-step acceleration and braking within a very short time result in shocks at Tearing away in the starting phase is avoided or greatly reduced, as is when braking after the pressing work has ended.
  • 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 one on the pressure limiting valve 27 preselected pressure equalization on the first branch 25 of the pressure relief line 15 brings about.
  • the accumulator 19 delivers oil via the switch-back valve 53 or the line 14 into the main feed line 3, as long as the shut-off valve 18 is relieved on the spring side via the line 14A and the line 22 via the directional valve 23 to the 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.
  • oil flows with both the pressure of the pump 2 and of the reservoir 19 in the high pressure phase via the line 3 to the actuating cylinder 5, without having to pass through a further throttle element other than the press safety valve 4.
  • the piston rod 10 of the clutch / brake combination 6/7 has hitherto been in the braking position on the brake 6 due to the pressure of the spring 9.
  • the piston 8 settles on the clutch 7.
  • the pressure in the actuating cylinder 5 rises at a maximum delivery rate (without throttling effect in FIG. 3), initially rapidly according to the spring characteristic up to the spring pressure P 1, then further as a result of the spring characteristic of the clutch 7 up to the clutch closing pressure P ⁇ . Only now that no more compression volume is needed does the pressure rise rapidly in accordance with the total delivery rate from pump 2 and accumulator 19 to a value preselected at pressure relief valve 27, which is above the closing pressure of the clutch, and which is used as switch-on pressure P " works. With the same, the damper valve 24 is spring-loaded and can release excess pressure to the tank 1, so that during this phase the pressure in the actuating cylinder 5 on one reduced value remains constant.
  • 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 limiting valve 27 and the closing pressure P R of the clutch.
  • P " the acceleration pressure
  • the speed change on the shaft from 0 to the operating speed takes place with a much lower pressure surge than at full pump pressure, ie 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 stands, while no pressure relief takes place via the directional valve 23.
  • the magnetic actuator 35 is then excited 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 ".
  • the relevant stop point of the signal transmitter 39 is placed in this case or the excitation of the magnetic actuator 35 is adjusted electrically such that the press ram comes to rest exactly in the top dead center, in the initial 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 limiting valve 28, the brake does not stop hard, but rather with shock absorption.

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.
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 true EP0216776A1 (fr) 1987-04-08
EP0216776B1 EP0216776B1 (fr) 1988-10-19

Family

ID=8164954

Family Applications (1)

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) DE3523163A1 (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
ES2243299T3 (es) * 1999-08-13 2005-12-01 Herion Systemtechnik Gmbh Valvula de seguridad para una prensa.
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
DE50110744D1 (de) * 2000-12-02 2006-09-28 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
EA006497B1 (ru) 2002-05-24 2005-12-29 Метсо Линдеманн Гмбх Устройство гидравлического управления в гидравлической системе для работы станка, такого как пресс, для обработки материала любого типа, в частности для работы ножниц для резки металлолома
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.

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8600849A1 *

Also Published As

Publication number Publication date
DE3523163A1 (de) 1986-02-13
JPS61502735A (ja) 1986-11-27
DE3565651D1 (fr) 1988-11-24
EP0216776B1 (fr) 1988-10-19
WO1986000849A1 (fr) 1986-02-13

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