EP1097039B1 - Hydraulic control system for a hydraulically actuated clutch brake combination for the drive shaft of a mechanical press - Google Patents

Hydraulic control system for a hydraulically actuated clutch brake combination for the drive shaft of a mechanical press Download PDF

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Publication number
EP1097039B1
EP1097039B1 EP99932829A EP99932829A EP1097039B1 EP 1097039 B1 EP1097039 B1 EP 1097039B1 EP 99932829 A EP99932829 A EP 99932829A EP 99932829 A EP99932829 A EP 99932829A EP 1097039 B1 EP1097039 B1 EP 1097039B1
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EP
European Patent Office
Prior art keywords
pressure
control
valve
hydraulic
control valve
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EP99932829A
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German (de)
French (fr)
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EP1097039A1 (en
Inventor
Stefan Schmidt
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Bosch Rexroth AG
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Mannesmann Rexroth AG
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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 is based on a hydraulic control system for actuating a Clutch brake combination of the drive shaft of a mechanical press is provided and which has the features from the preamble of claim 1.
  • Such a hydraulic control is known from DE 35 23 163 A1. at This hydraulic control will primarily be a larger quantity Pressure fluid is required if the hydraulic actuator releases the brake and closing the clutch moves and when the high clutch pressure builds up and the pressure medium is compressed. During the rest of a press cycle little or no pressure fluid is required.
  • a hydraulic accumulator is part of the pressure medium source, that within the cycle time, in that of the hydraulic actuator little Pressure medium is needed, is charged by the hydraulic pump and then, if a lot of pressure medium is required, releases pressure medium.
  • the control is the inlet connection of a 3/2-way safety valve a non-return valve to the hydraulic pump connected to the hydraulic pump.
  • a branch line runs between the check valve and the inlet connection to the hydraulic accumulator, in which a pressure-controlled shut-off valve sits, that way is controlled that from the hydraulic accumulator to the inlet connection of the safety valve Pressure fluid can flow in if a lot of pressure medium is required, and that is otherwise in its locked position.
  • the hydraulic accumulator is filled from the hydraulic pump via another branch line that bypasses the check valve and in which there is another check valve that leads to the pressure line section between the first check valve and the inlet connection of the safety valve blocks.
  • the safety valve also has a drain connection, which is connected to a tank is, and a consumer connection, from which a line to the hydraulic Actuator leads.
  • a drain connection which is connected to a tank is, and a consumer connection, from which a line to the hydraulic Actuator leads.
  • On the latter line is a pilot operated pressure relief valve connected with two pilot valves that are set to different pressures are. Depending on the position of a directional valve, neither of the two pilot valves is or one or the other pilot valve effective.
  • the control is carried out so that the check valve during releasing the brake and during the time when the clutch pressure is low is held, is open and closed during the remaining times of a press cycle is held.
  • the aim of the invention is therefore a hydraulic control with the features to develop from the preamble of claim 1 so that the necessary Functions can be obtained with less effort on components can.
  • the arrangement of the 3-way pressure control valve according to the invention does not into the one leading from the safety valve arrangement to the hydraulic actuator Line intervened so that this to brake the drive shaft of the press can also be relieved of pressure when the pressure control valve is in a position in his control port is connected to his pressure port gets stuck.
  • the cost of hydraulic components is particularly low if according to Claim 5 the pressure control valve by an electric actuator, in particular is adjustable by a proportional magnet.
  • the pressure control valve can be set to different pressure values can be set.
  • the ram 10 of a press can be seen via a coupling rod 11 with a drive shaft designed as a crankshaft 12 is connected.
  • the drive shaft 12 can via a clutch 13 from one Electric motor 14 are driven.
  • the plates 16 of the clutch are from the piston rod 17 a single-acting hydraulic cylinder 18 together in the axial direction can be pressed against a stop plate 23 driven by the motor 14.
  • the inner of the hydraulic cylinder 18 is by a piston 19 on which the piston rod 17th is attached, in a fully cylindrical pressure chamber 20 remote from the piston rod and in an annular cylindrical piston-side receiving space 21 for a helical compression spring 22 divided.
  • the disks 16 of the brake 15 are composed of this and can be pressed against a fixed stop plate 24.
  • the pressure in the Pressure chamber 20 slightly due to the increasing tension of the helical compression spring 22 increases, the slats 16 or a part of the slats 16 lie against the Parts of the clutch which are connected to the output of the electric motor 14 in a manner fixed against relative rotation 13 on.
  • the torque that can be transmitted via the clutch 13 now depends on the Height of the pressure in the pressure chamber 20 from.
  • the hydraulic cylinder 18 is supplied with pressure medium from a pressure medium source which essentially comprises a hydraulic pump 25 and a hydraulic accumulator 26.
  • the hydraulic pump 25 with a constant displacement is operated by an electric motor 27 driven and is located in a tank 28. It sucks from the tank per unit of time to a relatively small amount of pressure medium, which they in an output channel 29 issues. From there, the pressure medium can be transferred to the hydraulic pump 25 blocking check valve 30 flow into a pressure line 31 leading to Pressure port 32 of a 3-way pressure control valve 33 leads.
  • the hydraulic accumulator 26 is also connected.
  • a Pressure relief valve 34 is provided through which the pressure in the pressure line 31 and thus in the hydraulic accumulator 26 is limited to a maximum value. This Value is greater than the value at which an output channel 29 of the hydraulic pump 25 connected and controlled by the pressure in the pressure line 31 pressure shut-off valve 35 switches the flow of the hydraulic pump 25 to circulation and back conducts into the tank 28.
  • the pressure control valve 33 has a tank connection in addition to the pressure connection 32 40, which is connected to the tank 28 via a tank line 41, and one Control port 42, in which a certain depending on a predetermined setpoint Pressure is regulated.
  • the control connection is with the inlet connection 43 connected to a safety valve assembly 44, which also has a consumer connection 45, the via a consumer line 46 with the pressure chamber 20 of the Hydraulic cylinder 18 is connected, and has a tank connection 47 which over the tank line 41 already mentioned is connected to tank 28.
  • the safety valve arrangement 44 consists of two 4/2-way valves 48 and 49, which with the pressure control valve 33 to a valve block are summarized, the tank connection T, a pressure connection P, has a consumer connection A and a leakage connection Y.
  • the Connections between the individual valves are through channels within the valve blocks made up of three plates.
  • the pressure control valve 33 of the embodiment according to FIG. 1 is a pilot operated one Pressure control valve, the pilot valve by a proportional solenoid 51 to different Pressure values can be set.
  • the sequence of the pilot valve is connected to the leakage port Y.
  • On a measuring surface of the not shown Control piston of the pressure control valve is, as through the control line 52 indicated, the pressure in the control port 42 of the valve is returned.
  • the Control oil for the pilot valve can be taken from the pressure connection or the control connection become.
  • the two directional control valves 48 and 49 each under the effect a compression spring 53, they each connect the consumer line for themselves 46 with the tank connection T of the valve block and thus with the Tank line 41.
  • the two further connections of each directional control valve 48 and 49 are shut off in the rest position of the valves. Both are against it Directional control valves 48 and 49 in their working position, so there are two more Connections of the directional valve 48 and the other connections in series the directional control valve 49 a connection between the pressure chamber 20 and the control port 42 of the pressure control valve 33.
  • the safety valve arrangement 44 is the same as that from Figure 1, but shown in a highly simplified manner compared to Figure 1.
  • the pilot operated pressure control valve 33 of the embodiment according to FIG. 2 is two designed as pressure relief valves and to different pressure values set pilot valves 60 and 61 and a directional control valve 62 with three switching positions assigned. Are in a spring-centered central position of the directional valve 62 a control chamber 63 of the pressure control valve 33 and the inputs of the two pilot valves 60 and 61 cordoned off from each other. With one electromagnet each 64 or 65, the directional control valve 62 in a first working position in which the Control room 63 is connected to the input of pilot valve 60, or in a second working position in which the control room 63 with the entrance of the pilot valve 61 set at a lower pressure is connected.
  • control line 66 67 of the pressure control valve 33 is subjected to the pressure on one end face, which prevails in control output 42.
  • This pressure works in the sense of a connection of the control port 42 with the tank port 41 in the opposite direction and in In the sense of a connection of the control connection 42 with the pressure connection 31 the control piston 67 from the pressure in the control chamber 63 and from a weak one Compression spring 68 acted upon.
  • the control oil for the pilot control is via a Control line 69 taken from the pressure port 31.
  • the ram 10 of the press is close by the brake 15 with maximum braking force held at its top dead center when the pressure chamber 20 of the hydraulic cylinder 18 through the safety valve arrangement 44 via its tank connection 47 is relieved to the tank.
  • Figure 1 is in the rest position of the plunger 10 of the proportional magnet 51 set to a pressure setpoint that is higher than the maximum storage pressure, so that the control port 42 of the Pressure control valve is wide open connected to the pressure port 32.
  • the safety valve arrangement is switched at the beginning of a press cycle.
  • the setpoint of the pressure control valve is also the same 33 set to a value that corresponds to a soft dome.
  • the directional control valve 62 by excitation of the electromagnet 64 brought into its first switching position, in which the pilot valve 60 is effective is also on a pressure value corresponding to a soft dome is set.
  • the setting of the respective pressure control valve is maintained as long as the drive shaft 12 of the press is designated 75 in FIG Angular range.
  • the electromagnet 51 is energized more and the pressure setpoint is increased so much, that the torque required for the pressing process via the clutch can be transferred.
  • the pressure setpoint can be determined by the pressure in the hydraulic accumulator 26 are placed so that this pressure is effective as a clutch pressure.
  • the electromagnet 64 is switched off and thereby the directional valve 62 brought into its central position, in which the control room 63 of the pressure control valve 33 is shut off.
  • the clutch pressure rises memory pressure.
  • After passing through the angular range 76 is the largest Coupling force reached.
  • the pressing process now takes place in the angular range 77 instead, before the plunger 10 is raised again, the clutch pressure is maximum.
  • the electromagnet 51 is then opened set a pressure setpoint that is less than the pressure setpoint for the soft Is domes.
  • FIG. 1 the pressure setpoint that is less than the pressure setpoint for the soft Is domes.
  • the directional valve 62 is activated by excitation brought the electromagnet 65 into its second switching position, in which the Pilot valve 61 is effective, which is set to a lower pressure than the pilot valve 60 is.
  • the brake 15 now engages softly after passing through the angular range 78 switches the safety valve arrangement 44 so that in the angular range 79 maximum braking force is effective and the tappet is stopped at top dead center becomes.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Presses (AREA)
  • Braking Arrangements (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Description

Die Erfindung geht aus von einer hydraulischen Steuerung, die zur Betätigung einer Kupplungsbremskombination der Antriebswelle einer mechanischen Presse vorgesehen ist und die die Merkmale aus dem Oberbegriff des Anspruchs 1 aufweist.The invention is based on a hydraulic control system for actuating a Clutch brake combination of the drive shaft of a mechanical press is provided and which has the features from the preamble of claim 1.

Eine derartige hydraulische Steuerung ist aus der DE 35 23 163 A1 bekannt. Bei dieser hydraulischen Steuerung wird in erster Linie dann eine größere Menge Druckmittel benötigt, wenn sich der hydraulische Betätiger beim Lösen der Bremse und Schließen der Kupplung bewegt und wenn der hohe Kupplungsdruck aufgebaut und dazu das Druckmittel komprimiert wird. In der übrigen Zeit eines Pressenzyklus wird keine oder nur eine geringe Druckmittelmenge benötigt. Um eine kleine Hydropumpe verwenden zu können, gehört zur Druckmittelquelle ein Hydrospeicher, der innerhalb der Zykluszeit, in der vom hydraulischen Betätiger wenig Druckmittel benötigt wird, von der Hydropumpe aufgeladen wird und dann, wenn viel Druckmittel benötigt wird, Druckmittel abgibt. Bei der bekannten hydraulischen Steuerung ist der Zulaufanschluß eines 3/2-Wege-Sicherheitsventils über ein zur Hydropumpe sperrendes Rückschlagventil mit der Hydropumpe verbunden. Zwischen dem Rückschlagventil und dem Zulaufanschluß geht eine Zweigleitung zum Hydrospeicher ab, in der ein druckgesteuertes Sperrventil sitzt, das so gesteuert wird, daß aus dem Hydrospeicher dem Zulaufanschluß des Sicherheitsventils Druckmittel zufließen kann, wenn viel Druckmittel benötigt wird, und das sich ansonsten in seiner Sperrstellung befindet. Befüllt wird der Hydrospeicher von der Hydropumpe aus über eine weitere Zweigleitung, die das Sperrventil umgeht und in der sich ein weiteres Rückschlagventil befindet, das zu dem Druckleitungsabschnitt zwischen dem ersten Rückschlagventil und dem Zulaufanschluß des Sicherheitsventils hin sperrt.Such a hydraulic control is known from DE 35 23 163 A1. at This hydraulic control will primarily be a larger quantity Pressure fluid is required if the hydraulic actuator releases the brake and closing the clutch moves and when the high clutch pressure builds up and the pressure medium is compressed. During the rest of a press cycle little or no pressure fluid is required. To one To be able to use a small hydraulic pump, a hydraulic accumulator is part of the pressure medium source, that within the cycle time, in that of the hydraulic actuator little Pressure medium is needed, is charged by the hydraulic pump and then, if a lot of pressure medium is required, releases pressure medium. In the well-known hydraulic The control is the inlet connection of a 3/2-way safety valve a non-return valve to the hydraulic pump connected to the hydraulic pump. A branch line runs between the check valve and the inlet connection to the hydraulic accumulator, in which a pressure-controlled shut-off valve sits, that way is controlled that from the hydraulic accumulator to the inlet connection of the safety valve Pressure fluid can flow in if a lot of pressure medium is required, and that is otherwise in its locked position. The hydraulic accumulator is filled from the hydraulic pump via another branch line that bypasses the check valve and in which there is another check valve that leads to the pressure line section between the first check valve and the inlet connection of the safety valve blocks.

Das Sicherheitsventil hat noch einen Ablaufanschluß, der mit einem Tank verbunden ist, und einen Verbraucheranschluß, von dem eine Leitung zum hydraulischen Betätiger führt. An letztere Leitung ist ein vorgesteuertes Druckbegrenzungsventil mit zwei Pilotventilen angeschlossen, die auf unterschiedlich hohe Drücke eingestellt sind. Je nach Stellung eines Wegeventils ist keines der beiden Pilotventile oder das eine oder das andere Pilotventil wirksam. Mit dem Wegeventil wird auch das Sperrventil zwischen dem Hydrospeicher und dem Zulaufanschluß des Sicherheitsventils gesteuert. Die Steuerung erfolgt so, daß das Sperrventil während des Lösens der Bremse und während der Zeit, in der der Kupplungsdruck niedrig gehalten wird, offen ist und in den übrigen Zeiten eines Pressenzyklus geschlossen gehalten wird. Insbesondere wird dadurch verhindert, daß während des weichen Abbremsens der Antriebswelle Druckmittel aus dem Hydrospeicher über das Sicherheitsventil und das Druckbegrenzungsventil zum Tank abfließt. Andererseits muß das zum Aufbau des hohen Kupplungsdruckes notwendige Kompressionsöl allein von der Hydropumpe zur Verfügung gestellt werden. Nachteilig an der bekannten hydraulischen Steuerung ist darüber hinaus insbesondere die hohe Zahl der notwendigen hydraulischen Einzelkomponenten.The safety valve also has a drain connection, which is connected to a tank is, and a consumer connection, from which a line to the hydraulic Actuator leads. On the latter line is a pilot operated pressure relief valve connected with two pilot valves that are set to different pressures are. Depending on the position of a directional valve, neither of the two pilot valves is or one or the other pilot valve effective. With the directional valve too the check valve between the hydraulic accumulator and the inlet connection of the safety valve controlled. The control is carried out so that the check valve during releasing the brake and during the time when the clutch pressure is low is held, is open and closed during the remaining times of a press cycle is held. In particular, this prevents that during the soft Braking the drive shaft pressure medium from the hydraulic accumulator Safety valve and the pressure relief valve flows to the tank. on the other hand must the compression oil necessary to build up the high clutch pressure can only be provided by the hydraulic pump. Disadvantage of the Known hydraulic control is also particularly high Number of necessary hydraulic individual components.

Ziel der Erfindung ist es somit, eine hydraulische Steuerung mit den Merkmalen aus dem Oberbegriff des Anspruchs 1 so weiterzuentwickeln, daß die notwendigen Funktionen mit einem geringeren Aufwand an Bauteilen erhalten werden können.The aim of the invention is therefore a hydraulic control with the features to develop from the preamble of claim 1 so that the necessary Functions can be obtained with less effort on components can.

Dieses Ziel wird dadurch erreicht, daß die hydraulische Steuerung außer mit den Merkmalen aus dem Oberbegriff zusätzlich mit den Merkmalen aus dem kennzeichnenden Teil des Patentanspruchs 1 ausgestattet ist. This goal is achieved in that the hydraulic control except with the Features from the generic term additionally with the features from the identifying Part of claim 1 is equipped.

Durch die erfindungsgemäße Anordnung des 3-Wege-Druckregelventils wird nicht in die von der Sicherheitsventilanordnung zum hydraulischen Betätiger führende Leitung eingegriffen, so daß diese zum Abbremsen der Antriebswelle der Presse auch dann von Druck entlastbar ist, wenn das Druckregelventil in einer Stellung, in der sein Regelanschluß mit seinem Druckanschluß verbunden ist, hängenbleibt.The arrangement of the 3-way pressure control valve according to the invention does not into the one leading from the safety valve arrangement to the hydraulic actuator Line intervened so that this to brake the drive shaft of the press can also be relieved of pressure when the pressure control valve is in a position in his control port is connected to his pressure port gets stuck.

Wird die zum hydraulischen Betätiger führende Leitung für ein sanftes Abbremsen der Antriebswelle über das Druckregelventil von Druck entlastet, so ist der Druckanschluß des Druckregelventils abgesperrt, so daß kein Druckmittel aus dem Hydrospeicher oder von der Hydropumpe zum Tank wegfließt. Das Druckregelventil erfüllt somit auch die Funktion des zusätzlichen Sperrventils aus dem Stand der Technik. Zudem fließt immer dann auch aus dem Hydrospeicher Druckmittel über das Druckregelventil und die Sicherheitsventilanordnung dem hydraulischen Betätiger zu, wenn sich aus der über das Druckregelventil bestehenden Druckdifferenz und dem Öffnungsquerschnitt des Druckregelventils ein Druckmittelstrom ergibt, der größer als der von der Hydropumpe gelieferte Druckmittelstrom ist.Becomes the line leading to the hydraulic actuator for gentle braking relieved of pressure from the drive shaft via the pressure control valve, this is the pressure connection of the pressure control valve shut off, so that no pressure medium from the hydraulic accumulator or flows away from the hydraulic pump to the tank. The pressure control valve thus also fulfills the function of the additional check valve from the prior art Technology. In addition, pressure medium always overflows from the hydraulic accumulator the pressure control valve and the safety valve arrangement to the hydraulic actuator to if it results from the pressure difference across the pressure control valve and the opening cross section of the pressure control valve results in a pressure medium flow, which is greater than the pressure medium flow supplied by the hydraulic pump.

Vorteilhafte Ausgestaltungen einer erfindungsgemäßen hydraulischen Steuerung kann man den Unteransprüchen entnehmen.Advantageous configurations of a hydraulic control according to the invention can be found in the subclaims.

Bevorzugt ist gemäß Patentanspruch 2 in der Ruhestellung der Sicherheitsventilanordnung, in der der hydraulische Betätiger über die Sicherheitsventilanordnung von Druck entlastet und der Zulaufanschluß abgesperrt ist, die Verbindung zwischen dem Druckanschluß und dem Regelanschluß des Druckregelventils voll aufgesteuert. Dann reagiert der hydraulische Betätiger nach dem Umschalten der Sicherheitsventilanordnung besonders schnell, da sofort Druckmittel über das Druckregelventil fließen kann und dieses nicht erst von einer Stellung, in der sein Regelanschluß mit dem Tankanschluß verbunden ist, in die andere Stellung gebracht werden muß. Auf vorteilhafte Weise erreicht wird dies durch eine Ausgestaltung gemäß Patentanspruch 3 oder gemäß Patentanspruch 4.According to claim 2, in the rest position of the safety valve arrangement, in which the hydraulic actuator via the safety valve arrangement Relieved of pressure and the inlet connection is shut off, the connection between the pressure connection and the control connection of the pressure control valve full turned on. Then the hydraulic actuator reacts after switching the Safety valve arrangement particularly quickly, since pressure medium immediately via the Pressure control valve can flow and not from a position in which Control connection is connected to the tank connection, brought into the other position must become. This is advantageously achieved by an embodiment according to claim 3 or according to claim 4.

Der Aufwand an hydraulischen Komponenten ist besonders gering, wenn gemäß Patentanspruch 5 das Druckregelventil durch einen elektrischen Stellantrieb, insbesondere durch einen Proportionalmagneten verstellbar ist. Mithilfe des elektrischen Stellantriebs kann das Druckregelventil auf unterschiedliche Druckwerte eingestellt werden.The cost of hydraulic components is particularly low if according to Claim 5 the pressure control valve by an electric actuator, in particular is adjustable by a proportional magnet. Using the electrical Actuator, the pressure control valve can be set to different pressure values can be set.

Will man den Aufwand für die elektrische Steuerung etwas geringer halten, so kann das Druckregelventil durch eine Ausbildung gemäß den Ansprüchen 7 oder 8 auf unterschiedliche Druckhöhen eingestellt werden.If you want to keep the effort for the electrical control a little lower, so can the pressure control valve by training according to claims 7 or 8 can be set to different pressure levels.

Zwei Ausführungsbeispiele einer erfindungsgemäßen hydraulischen Steuerung für eine hydraulisch betätigbare Kupplungsbremskombination für die Antriebswelle einer mechanischen Presse sind in den Figuren dargestellt. Anhand dieser Figuren wird die Erfindung nun näher erläutert.Two exemplary embodiments of a hydraulic control according to the invention for a hydraulically operated clutch / brake combination for the drive shaft a mechanical press are shown in the figures. Based on these figures the invention will now be explained in more detail.

Es zeigen

Figur 1
ein erstes Ausführungsbeispiel, bei dem das Druckregelventil vorgesteuert und durch einen Elektromagneten proportional verstellbar ist,
Figur 2
ein zweites Ausführungsbeispiel mit einem vorgesteuerten Druckregelventil mit zwei auf unterschiedliche Drücke eingestellten Pilotventilen,
Figur 3
stark schematisiert das Druckregelventil aus Figur 2 und
Figur 4
den Ablauf eines Pressenzyklus in einem Winkeldiagramm.
Show it
Figure 1
a first embodiment in which the pressure control valve is pilot-controlled and proportionally adjustable by an electromagnet,
Figure 2
a second exemplary embodiment with a pilot-controlled pressure control valve with two pilot valves set to different pressures,
Figure 3
highly schematized the pressure control valve of Figure 2 and
Figure 4
the course of a press cycle in an angle diagram.

In den beiden Figuren 1 und 2 ist der Stößel 10 einer Presse zu erkennen, der über eine Koppelstange 11 mit einer als Kurbelwelle ausgebildeten Antriebswelle 12 verbunden ist. Die Antriebswelle 12 kann über eine Kupplung 13 von einem Elektromotor 14 angetrieben werden. Außerdem ist eine Bremse 15 vorhanden, mit der die Antriebswelle und damit der Stößel der Presse nach dem Trennen der Antriebswelle vom Elektromotor, also nach dem Lösen der Kupplung 13, stillgesetzt werden kann. Die Lamellen 16 der Kupplung sind von der Kolbenstange 17 eines einseitig wirkenden Hydrozylinders 18 in axialer Richtung zusammen- und gegen eine vom Motor 14 angetriebene Anschlagplatte 23 andrückbar. Das Innere des Hydrozylinders 18 wird durch einen Kolben 19, an dem die Kolbenstange 17 befestigt ist, in einen vollzylindrischen, kolbenstangenabseitigen Druckraum 20 und in einen ringzylindrischen kölbenseitigen Aufnahmeraum 21 für eine Schraubendruckfeder 22 aufgeteilt. Von dieser sind die Lamellen 16 der Bremse 15 zusammen- und gegen eine feststehende Anschlagplatte 24 andrückbar. Bei von Druck entlasteten Druckraum 20 ist die Bremse 15 mit einer durch die Vorspannung der Schraubendruckfeder 22 bestimmten Kraft betätigt. Bei einem Druckanstieg im Druckraum 20 verringert sich zunächst die Bremskraft, bis schließlich der Druck einen der Vorspannung der Schraubendruckfeder 22 äquivalenten Wert annimmt. Dann beginnen der Kolben 19 und die Kolbenstange 17 sich zu bewegen. Die Bremse 15 ist gelöst. Nach kurzem Hub, währenddessen der Druck im Druckraum 20 wegen der steigenden Spannung der Schraubendruckfeder 22 geringfügig zunimmt, legen sich die Lamellen 16 bzw ein Teil der Lamellen 16 an die drehfest mit dem Abtrieb des Elektromotors 14 verbundenen Teile der Kupplung 13 an. Das über die Kupplung 13 übertragbare Drehmoment hängt nun von der Höhe des Druckes im Druckraum 20 ab.In the two Figures 1 and 2, the ram 10 of a press can be seen via a coupling rod 11 with a drive shaft designed as a crankshaft 12 is connected. The drive shaft 12 can via a clutch 13 from one Electric motor 14 are driven. There is also a brake 15 with the drive shaft and thus the ram of the press after separating the Drive shaft of the electric motor, that is after the clutch 13 has been released, stopped can be. The plates 16 of the clutch are from the piston rod 17 a single-acting hydraulic cylinder 18 together in the axial direction can be pressed against a stop plate 23 driven by the motor 14. The inner of the hydraulic cylinder 18 is by a piston 19 on which the piston rod 17th is attached, in a fully cylindrical pressure chamber 20 remote from the piston rod and in an annular cylindrical piston-side receiving space 21 for a helical compression spring 22 divided. The disks 16 of the brake 15 are composed of this and can be pressed against a fixed stop plate 24. When from Pressure-relieved pressure chamber 20 is the brake 15 with a preload the helical compression spring 22 actuated certain force. When the pressure rises in the pressure chamber 20, the braking force initially decreases until finally the pressure is a value equivalent to the preload of the helical compression spring 22 accepts. Then the piston 19 and the piston rod 17 begin to move. The brake 15 is released. After a short stroke, the pressure in the Pressure chamber 20 slightly due to the increasing tension of the helical compression spring 22 increases, the slats 16 or a part of the slats 16 lie against the Parts of the clutch which are connected to the output of the electric motor 14 in a manner fixed against relative rotation 13 on. The torque that can be transmitted via the clutch 13 now depends on the Height of the pressure in the pressure chamber 20 from.

Mit Druckmittel gespeist wird der Hydrozylinder 18 von einer Druckmittelquelle aus, die im wesentlichen eine Hydropumpe 25 und einen Hydrospeicher 26 umfaßt. Die Hydropumpe 25 mit konstantem Hubvolumen wird von einem Elektromotor 27 angetrieben und befindet sich in einem Tank 28. Aus dem Tank saugt sie pro Zeiteinheit eine relativ kleine Druckmittelmenge an, die sie in einen Ausgangskanal 29 abgibt. Von dort aus kann das Druckmittel über ein zur Hydropumpe 25 hin sperrendes Rückschlagventil 30 in eine Druckleitung 31 fließen, die zum Druckanschluß 32 eines 3-Wege-Druckregelventils 33 führt. An die Druckleitung 31 ist auch der Hydrospeicher 26 angeschlossen. Zur Sicherheit ist außerdem ein Druckbegrenzungsventil 34 vorgesehen, durch das der Druck in der Druckleitung 31 und damit im Hydrospeicher 26 auf einen Maximalwert begrenzt ist. Dieser Wert liegt über dem Wert, bei dem ein an den Ausgangskanal 29 der Hydropumpe 25 angeschlossenes und vom Druck in der Druckleitung 31 gesteuertes Druckabschaltventil 35 den Förderstrom der Hydropumpe 25 auf Umlauf schaltet und zurück in den Tank 28 leitet.The hydraulic cylinder 18 is supplied with pressure medium from a pressure medium source which essentially comprises a hydraulic pump 25 and a hydraulic accumulator 26. The hydraulic pump 25 with a constant displacement is operated by an electric motor 27 driven and is located in a tank 28. It sucks from the tank per unit of time to a relatively small amount of pressure medium, which they in an output channel 29 issues. From there, the pressure medium can be transferred to the hydraulic pump 25 blocking check valve 30 flow into a pressure line 31 leading to Pressure port 32 of a 3-way pressure control valve 33 leads. To the pressure line 31, the hydraulic accumulator 26 is also connected. For security is also a Pressure relief valve 34 is provided through which the pressure in the pressure line 31 and thus in the hydraulic accumulator 26 is limited to a maximum value. This Value is greater than the value at which an output channel 29 of the hydraulic pump 25 connected and controlled by the pressure in the pressure line 31 pressure shut-off valve 35 switches the flow of the hydraulic pump 25 to circulation and back conducts into the tank 28.

Das Druckregelventil 33 besitzt außer dem Druckanschluß 32 einen Tankanschluß 40, der über eine Tankleitung 41 mit dem Tank 28 verbunden ist, und einen Regelanschluß 42, in dem je nach einem vorgegebenen Sollwert ein bestimmter Druck eingeregelt wird. Der Regelanschluß ist mit dem Zulaufanschluß 43 einer Sicherheitsventilanordnung 44 verbunden, die außerdem einen Verbraucheranschluß 45, der über eine Verbraucherleitung 46 mit dem Druckraum 20 des Hydrozylinders 18 verbunden ist, und einen Tankanschluß 47 aufweist, der über die schon erwähnte Tankleitung 41 mit Tank 28 verbunden ist.The pressure control valve 33 has a tank connection in addition to the pressure connection 32 40, which is connected to the tank 28 via a tank line 41, and one Control port 42, in which a certain depending on a predetermined setpoint Pressure is regulated. The control connection is with the inlet connection 43 connected to a safety valve assembly 44, which also has a consumer connection 45, the via a consumer line 46 with the pressure chamber 20 of the Hydraulic cylinder 18 is connected, and has a tank connection 47 which over the tank line 41 already mentioned is connected to tank 28.

Bei der Ausführung nach Figur 1 besteht die Sicherheitsventilanordnung 44 aus zwei 4/2-Wegeventilen 48 und 49, die mit dem Druckregelventil 33 zu einem Ventilblock zusammengefaßt sind, der einen Tankanschluß T, einen Druckanschluß P, einen Verbraucheranschluß A und einen Leckageanschluß Y aufweist. Die Verbindungen zwischen den einzelnen Ventilen sind durch Kanäle innerhalb des sich aus drei Platten zusammensetzenden Ventilblocks realisiert.In the embodiment according to FIG. 1, the safety valve arrangement 44 consists of two 4/2-way valves 48 and 49, which with the pressure control valve 33 to a valve block are summarized, the tank connection T, a pressure connection P, has a consumer connection A and a leakage connection Y. The Connections between the individual valves are through channels within the valve blocks made up of three plates.

Das Druckregelventil 33 der Ausführung nach Figur 1 ist ein vorgesteuertes Druckregelventil, dessen Pilotventil durch einen Proportionalmagneten 51 auf unterschiedliche Druckwerte eingestellt werden kann. Der Ablauf des Pilotventils ist mit dem Leckageanschluß Y verbunden. Auf eine Meßfläche des nicht näher dargestellten Regelkolbens des Druckregelventils wird, wie durch die Steuerleitung 52 angedeutet, der Druck im Regelanschluß 42 des Ventils zurückgeführt. Das Steueröl für das Pilotventil kann am Druckanschluß oder am Regelanschluß entnommen werden.The pressure control valve 33 of the embodiment according to FIG. 1 is a pilot operated one Pressure control valve, the pilot valve by a proportional solenoid 51 to different Pressure values can be set. The sequence of the pilot valve is connected to the leakage port Y. On a measuring surface of the not shown Control piston of the pressure control valve is, as through the control line 52 indicated, the pressure in the control port 42 of the valve is returned. The Control oil for the pilot valve can be taken from the pressure connection or the control connection become.

In der Ruhestellung, die die beiden Wegeventile 48 und 49 jeweils unter der Wirkung einer Druckfeder 53 einnehmen, verbinden sie jedes für sich die Verbraucherleitung 46 mit dem Tankanschluß T des Ventilblocks und damit mit der Tankleitung 41. Die beiden weiteren Anschlüsse jedes Wegeventils 48 und 49 sind in der Ruhestellung der Ventile abgesperrt. Befinden sich dagegen beide Wegeventile 48 und 49 in ihrer Arbeitsstellung, so besteht über die beiden weiteren Anschlüsse des Wegeventils 48 und die in Serie dazu liegenden weiteren Anschlüsse des Wegeventils 49 eine Verbindung zwischen dem Druckraum 20 und dem Regelanschluß 42 des Druckregelventils 33. Somit ist, wenn sich auch nur eines der beiden Wegeventile in seiner Ruhestellung befindet, der Druckraum 20 des Hydrozylinders 18 von Druck entlastet und der Zulaufanschluß 43 der Sicherheitsventilanordnung 44 abgesperrt.In the rest position, the two directional control valves 48 and 49 each under the effect a compression spring 53, they each connect the consumer line for themselves 46 with the tank connection T of the valve block and thus with the Tank line 41. The two further connections of each directional control valve 48 and 49 are shut off in the rest position of the valves. Both are against it Directional control valves 48 and 49 in their working position, so there are two more Connections of the directional valve 48 and the other connections in series the directional control valve 49 a connection between the pressure chamber 20 and the control port 42 of the pressure control valve 33. Thus, if only one of the two directional control valves is in its rest position, the pressure chamber 20 of the hydraulic cylinder 18 relieved of pressure and the inlet port 43 of the safety valve assembly 44 cordoned off.

Bei der Ausführung nach Figur 2 ist die Sicherheitsventilanordnung 44 gleich derjenigen aus Figur 1, jedoch gegenüber Figur 1 stark vereinfacht dargestellt.In the embodiment according to FIG. 2, the safety valve arrangement 44 is the same as that from Figure 1, but shown in a highly simplified manner compared to Figure 1.

Dem vorgesteuerten Druckregelventil 33 der Ausführung nach Figur 2 sind zwei als Druckbegrenzungsventile ausgebildete und auf unterschiedliche Druckwerte eingestellte Pilotventile 60 und 61 sowie ein Wegeventil 62 mit drei Schaltstellungen zugeordnet. In einer federzentrierten Mittelstellung des Wegeventils 62 sind ein Steuerraum 63 des Druckregelventils 33 und die Eingänge der beiden Pilotventile 60 und 61 gegeneinander abgesperrt. Durch jeweils einen Elektromagneten 64 bzw. 65 kann das Wegeventil 62 in eine erste Arbeitsstellung, in der der Steuerraum 63 mit dem Eingang des Pilotventils 60 verbunden ist, bzw. in eine zweite Arbeitsstellung gebracht werden, in der der Steuerraum 63 mit dem Eingang des auf einen niedrigeren Druck eingestellten Pilotventils 61 verbunden ist. Über eine Steuerleitung 66 wird der schematisch in Figur 3 dargestellte Regelkolben 67 des Druckregelventils 33 an einer Stirnfläche mit dem Druck beaufschlagt, der im Regelausgang 42 herrscht. Dieser Druck wirkt im Sinne einer Verbindung des Regelanschlusses 42 mit dem Tankanschluß 41. in Gegenrichtung und im Sinne einer Verbindung des Regelanschlusses 42 mit dem Druckanschluß 31 wird der Regelkolben 67 vom Druck im Steuerraum 63 und von einer schwachen Druckfeder 68 beaufschlagt. Das Steueröl für die Vorsteuerung wird über eine Steuerleitung 69 dem Druckanschluß 31 entnommen.The pilot operated pressure control valve 33 of the embodiment according to FIG. 2 is two designed as pressure relief valves and to different pressure values set pilot valves 60 and 61 and a directional control valve 62 with three switching positions assigned. Are in a spring-centered central position of the directional valve 62 a control chamber 63 of the pressure control valve 33 and the inputs of the two pilot valves 60 and 61 cordoned off from each other. With one electromagnet each 64 or 65, the directional control valve 62 in a first working position in which the Control room 63 is connected to the input of pilot valve 60, or in a second working position in which the control room 63 with the entrance of the pilot valve 61 set at a lower pressure is connected. The control piston shown schematically in FIG. 3 is connected via a control line 66 67 of the pressure control valve 33 is subjected to the pressure on one end face, which prevails in control output 42. This pressure works in the sense of a connection of the control port 42 with the tank port 41 in the opposite direction and in In the sense of a connection of the control connection 42 with the pressure connection 31 the control piston 67 from the pressure in the control chamber 63 and from a weak one Compression spring 68 acted upon. The control oil for the pilot control is via a Control line 69 taken from the pressure port 31.

Der Stößel 10 der Presse wird durch die Bremse 15 mit maximaler Bremskraft nahe an seinem oberen Totpunkt gehalten, wenn der Druckraum 20 des Hydrozylinders 18 durch die Sicherheitsventilanordnung 44 über deren Tankanschluß 47 zum Tank entlastet ist. Bei der Ausführung nach Figur 1 ist in der Ruhestellung des Stößels 10 der Proportionalmagnet 51 auf einen Drucksollwert eingestellt, der höher als der maximale Speicherdruck ist, so daß der Regelanschluß 42 des Druckregelventils weit offen mit dem Druckanschluß 32 verbunden ist. Auch bei der Ausführung nach Figur 2 ist letzteres der Fall, da das Wegeventil 62 in seiner Mittelstellung den Steuerraum 63 absperrt, Eine weitere Möglichkeit, um in der Ruhestellung des Stößels 10 eine offene Verbindung zwischen dem Regelanschluß und dem Druckanschluß des Druckregelventils 33 zu gewährleisten, besteht darin, den auf die Meßfläche des Regelkolbens wirkenden Druck zwischen der Sicherheitsventilanordnung 44 und dem Hydrozylinder 18 abzugreifen. Weil nämlich die Leitung 46 über die Sicherheitsventilanordnung 44 zum Tank entlastet ist, greift dann keine im Sinne einer Verbindung des Regelanschlusses mit dem Tankanschluß wirkende Kraft am Regelkolben an. In Figur 2 ist diese Alternative des Druckabgriffs durch die punktierte Steuerleitung 70 angedeutet. The ram 10 of the press is close by the brake 15 with maximum braking force held at its top dead center when the pressure chamber 20 of the hydraulic cylinder 18 through the safety valve arrangement 44 via its tank connection 47 is relieved to the tank. In the embodiment of Figure 1 is in the rest position of the plunger 10 of the proportional magnet 51 set to a pressure setpoint that is higher than the maximum storage pressure, so that the control port 42 of the Pressure control valve is wide open connected to the pressure port 32. Also at 2, the latter is the case since the directional valve 62 in its Middle position shuts off control room 63, another way to get in the Rest position of the plunger 10 an open connection between the control connection and to ensure the pressure connection of the pressure control valve 33 exists therein, the pressure acting on the measuring surface of the control piston between to tap the safety valve assembly 44 and the hydraulic cylinder 18. Because namely the line 46 is relieved via the safety valve arrangement 44 to the tank then no one intervenes in the sense of connecting the control connection to the The force acting on the tank connection on the control piston. This alternative is in FIG of the pressure tap indicated by the dotted control line 70.

Zu Beginn eines Pressenzyklus wird die Sicherheitsventilanordnung geschaltet. Bei der Ausführung nach Figur 1 wird zugleich der Sollwert des Druckregelventils 33 auf einen Wert eingestellt, der einem weichen Kuppeln entspricht. Bei der Ausführung nach Figur 2 wird das Wegeventil 62 durch Erregung des Elektromagneten 64 in seine erste Schaltstellung gebracht, in der das Pilotventil 60 wirksam ist, das ebenfalls auf einen einem weichen Kuppeln entsprechenden Druckwert eingestellt ist. Die Einstellung des jeweiligen Druckregelventils wird aufrechterhalten, solange sich die Antriebswelle 12 der Presse in dem in Figur 4 mit 75 bezeichneten Winkelbereich befindet. Bei der Ausführung nach Figur 1 wird dann der Elektromagnet 51 stärker bestromt und dadurch der Drucksollwert so weit erhöht, daß das für den Preßvorgang notwendige Drehmoment über die Kupplung übertragen werden kann. Der Drucksollwert kann über den Druck im Hydrospeicher 26 gelegt werden, so daß dieser Druck als Kupplungsdruck wirksam ist. Bei der Ausführung nach Figur 2 wird der Elektromagnet 64 ausgeschaltet und dadurch das Wegeventil 62 in seine Mittelstellung gebracht, in der der Steuerraum 63 des Druckregelventils 33 abgesperrt ist. Der Kupplungsdruck steigt somit auf den Speicherdruck an. Nach Durchfahren des Winkelbereichs 76 ist die größte Kupplungskraft erreicht. Im Winkelbereich 77 findet nun zunächst der Preßvorgang statt, ehe der Stößel 10 wieder angehoben wird, wobei der Kupplungsdruck maximal ist. Bei der Ausführung nach Figur 1 wird dann der Elektromagnet 51 auf einen Drucksollwert eingestellt, der kleiner als der Drucksollwert für das weiche Kuppeln ist. Bei der Ausführung nach Figur 2 wird das Wegeventil 62 durch Erregung des Elektromagneten 65 in seine zweite Schaltstellung gebracht, in der das Pilotventil 61 wirksam ist, das auf einen kleineren Druck als das Pilotventil 60 eingestellt ist. Es greift nun weich die Bremse 15. Nach Durchfahren des Winkelbereichs 78 schaltet die Sicherheitsventilanordnung 44 um, so daß im Winkelbereich 79 maximale Bremskraft wirksam ist und der Stößel am oberen Totpunkt stillgesetzt wird.The safety valve arrangement is switched at the beginning of a press cycle. In the embodiment according to FIG. 1, the setpoint of the pressure control valve is also the same 33 set to a value that corresponds to a soft dome. In the 2 is the directional control valve 62 by excitation of the electromagnet 64 brought into its first switching position, in which the pilot valve 60 is effective is also on a pressure value corresponding to a soft dome is set. The setting of the respective pressure control valve is maintained as long as the drive shaft 12 of the press is designated 75 in FIG Angular range. In the embodiment according to FIG. 1 the electromagnet 51 is energized more and the pressure setpoint is increased so much, that the torque required for the pressing process via the clutch can be transferred. The pressure setpoint can be determined by the pressure in the hydraulic accumulator 26 are placed so that this pressure is effective as a clutch pressure. at 2, the electromagnet 64 is switched off and thereby the directional valve 62 brought into its central position, in which the control room 63 of the pressure control valve 33 is shut off. The clutch pressure rises memory pressure. After passing through the angular range 76 is the largest Coupling force reached. The pressing process now takes place in the angular range 77 instead, before the plunger 10 is raised again, the clutch pressure is maximum. In the embodiment according to FIG. 1, the electromagnet 51 is then opened set a pressure setpoint that is less than the pressure setpoint for the soft Is domes. In the embodiment according to FIG. 2, the directional valve 62 is activated by excitation brought the electromagnet 65 into its second switching position, in which the Pilot valve 61 is effective, which is set to a lower pressure than the pilot valve 60 is. The brake 15 now engages softly after passing through the angular range 78 switches the safety valve arrangement 44 so that in the angular range 79 maximum braking force is effective and the tappet is stopped at top dead center becomes.

Claims (8)

  1. A hydraulic control system for a hydraulically actuable coupling-brake combination (13, 15) for the drive shaft (12) of a mechanical press with a pressure-fluid source having a hydraulic pump (25) and a hydraulic accumulator (26) for the supply with pressure fluid of a hydraulic actuator (18), with a safety valve arrangement (44), which has a supply port (43) through which a flow path leads from the pressure-fluid source (25, 26) to the hydraulic actuator (18), and with an adjustable pressure valve (33) according to the setting of which the hydraulic actuator (18) can be subjected to different working pressures,
    characterized in that the pressure valve is a 3-way pressure control valve (33) with a pressure port (32), which can be connected with the pressure-fluid source (25, 26), a tank port (40) and a control port (42) connected to the supply port (43) of the safety valve arrangement (44).
  2. A hydraulic control system according to Claim 1, characterized in that, in the rest position of the safety valve arrangement (44), in which rest position the hydraulic actuator (18) is relieved of pressure via the safety valve arrangement (44) and the supply port (43) is blocked off, the connection between the pressure port (32) and the control port (42) of the pressure control valve (33) is fully opened.
  3. A hydraulic control system according to Claim 2, characterized in that the connection from the pressure port (32) to the control port (42) of the pressure control valve (33) is opened by predetermination of a pressure setpoint exceeding the maximum system pressure.
  4. A hydraulic control system according to Claim 2, characterized in that a control chamber at a measuring surface (71) of the pressure control valve (33) is fluidically connected with a line (46) leading from the safety valve arrangement (44) to the hydraulic actuator (18).
  5. A hydraulic control system according to any of the preceding claims, characterized in that the pressure control valve (33) can be adjusted by means of an electric actuator drive, in particular by a proportional solenoid (51).
  6. A hydraulic control system according to any of the preceding claims, characterized in that the pressure control valve (33) is piloted.
  7. A hydraulic control system according to Claim 6, characterized in that a plurality of pilot valves (60, 61) set to pressures of different magnitude are associated with the pressure control valve (33) and that as a function of the position of the directional control valve means (62) a different pilot valve (60, 61) in each case acts to limit the pressure in a control chamber (63) of the pressure control valve (33).
  8. A hydraulic control system according to Claim 6 or 7, characterized in that in one position of the directional control valve means (62) a control chamber (63) of the pressure control valve (33) is blocked against the outflow of control oil and that in a further position of the directional control valve means (62) the control pressure in the control chamber (63) is limited by a pilot valve (60, 61).
EP99932829A 1998-07-11 1999-07-06 Hydraulic control system for a hydraulically actuated clutch brake combination for the drive shaft of a mechanical press Expired - Lifetime EP1097039B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19831144A DE19831144A1 (en) 1998-07-11 1998-07-11 Hydraulic control for a hydraulically operated clutch / brake combination for the drive shaft of a mechanical press
DE19831144 1998-07-11
PCT/EP1999/004691 WO2000002720A1 (en) 1998-07-11 1999-07-06 Hydraulic control system for a hydraulically actuated clutch brake combination for the drive shaft of a mechanical press

Publications (2)

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EP1097039A1 EP1097039A1 (en) 2001-05-09
EP1097039B1 true EP1097039B1 (en) 2002-12-11

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EP (1) EP1097039B1 (en)
DE (2) DE19831144A1 (en)
ES (1) ES2189441T3 (en)
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ES2267653T3 (en) * 2000-12-02 2007-03-16 Bosch Rexroth Ag HYDRAULIC COMMAND FOR A HYDRAULICALLY OPERATED BRAKE-CLUTCH COMBINATION, ESPECIALLY IN THE EXCENTRIC TREE OF A MECHANICAL PRESS.
DE10155050A1 (en) * 2001-11-09 2003-05-22 Porsche Ag Motor vehicle drive train with at least one clutch arrangement which can be actuated by mediation of pressure medium and operates under the influence of an operating medium and a transmission which can be actuated by mediation of pressure medium, as well as a corresponding clutch system
US6922991B2 (en) * 2003-08-27 2005-08-02 Moog Inc. Regulated pressure supply for a variable-displacement reversible hydraulic motor
DE102006050300B4 (en) * 2006-10-23 2013-05-08 Ortlinghaus-Werke Gmbh Pressure fluid operated circuit
DE102012022086B4 (en) * 2012-11-09 2023-05-11 Volkswagen Aktiengesellschaft Hydraulic control device
US10183852B2 (en) * 2015-07-30 2019-01-22 Danfoss Power Solutions Gmbh & Co Ohg Load dependent electronic valve actuator regulation and pressure compensation
CN105257605B (en) * 2015-11-06 2017-05-10 杨贝贝 Energy conversation method and energy conversation device for pressure control hydraulic systems
CN105485067B (en) * 2016-01-28 2017-09-29 佛山市佛锐达机电科技有限公司 A kind of force control hydraulic pressure energy saving of system device
CN105697436B (en) * 2016-04-12 2017-07-28 浙江大学 The small volume cell pressure control hydraulic system that a kind of flow is preferentially supplied

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DE2935702A1 (en) * 1979-09-04 1981-03-12 Herion-Werke Kg, 7012 Fellbach Eccentric press clutch and brake control circuit - has distribution valve assembly with operation dependent on pressure of clutch and brake respectively
GB2068823A (en) * 1980-02-12 1981-08-19 Arosverken Ab Hydraulic control device for a mechanical press
EP0051684B1 (en) * 1980-10-31 1984-02-15 L. SCHULER GmbH Control for the clutch and/or the brake of a press
EP0216776B1 (en) * 1984-07-19 1988-10-19 Zf-Herion-Systemtechnik Gmbh Pressure-adjusting system for a hydraulically-operated clutch and/or brake for the drive shaft of a press
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DE19831144A1 (en) 2000-01-13
ES2189441T3 (en) 2003-07-01
DE59903768D1 (en) 2003-01-23
EP1097039A1 (en) 2001-05-09
WO2000002720A1 (en) 2000-01-20

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