EP1211059B1 - Hydraulic control system for a hydraulically actuated clutch-brake combination in particular for the eccentric shaft of a mechanical press - Google Patents

Hydraulic control system for a hydraulically actuated clutch-brake combination in particular for the eccentric shaft of a mechanical press

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Publication number
EP1211059B1
EP1211059B1 EP20010127201 EP01127201A EP1211059B1 EP 1211059 B1 EP1211059 B1 EP 1211059B1 EP 20010127201 EP20010127201 EP 20010127201 EP 01127201 A EP01127201 A EP 01127201A EP 1211059 B1 EP1211059 B1 EP 1211059B1
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EP
European Patent Office
Prior art keywords
pressure
valve
hydraulic
control valve
control
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP20010127201
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German (de)
French (fr)
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EP1211059A3 (en
EP1211059A2 (en
Inventor
Stefan Schmidt
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.)
Bosch Rexroth AG
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Bosch Rexroth AG
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Filing date
Publication date
Priority claimed from DE10062229A external-priority patent/DE10062229A1/en
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1211059A2 publication Critical patent/EP1211059A2/en
Publication of EP1211059A3 publication Critical patent/EP1211059A3/en
Application granted granted Critical
Publication of EP1211059B1 publication Critical patent/EP1211059B1/en
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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/10—Brakes specially adapted for presses

Definitions

  • the invention relates to a hydraulic control, which is provided for actuating a clutch brake combination, in particular the eccentric shaft of a mechanical press and having the features of the preamble of patent claim 1.
  • Such a hydraulic control is known from WO 00/02720.
  • a larger amount of pressure medium is needed in the first place when the hydraulic cylinder moves when releasing the brake and closing the clutch and when the high clutch pressure is built up and to the pressure medium is compressed.
  • the pressure medium source includes a hydraulic accumulator, which is charged by the hydraulic pump within the cycle time in which the hydraulic cylinder little pressure medium is needed and then, if much pressure medium is needed, releases pressure medium.
  • a safety valve assembly which consists for example of two switch position monitored directional valves, in a flow path, which can be constructed by the pressure medium source to the hydraulic cylinder.
  • a 3-way pressure control valve with a connectable to the pressure medium source pressure port, with a tank port and with a control port is present, which is connected to the inlet port of the safety valve assembly.
  • the pressure control valve is an electrically piloted pressure control valve whose control piston is controlled on the one hand by a set by the electric pilot valve pressure and by the pressure at the control port.
  • Pressure valves tend to vibrate in general. This tendency can only be achieved by a suitable damping can be avoided. As a result, the time to build up a pressure is relatively long. The quality of control is relatively low. In this respect, by a pressure control valve is not always sufficient to meet the requirements.
  • the aim of the invention is thus to further develop a hydraulic control with the features of the preamble of claim 1 so that it has a high dynamics and thus allows short pressure build-up and pressure reduction times and a high control quality.
  • an electro-hydraulic pressure control circuit is constructed by means of the proportional directional control valve, the electrical pressure sensor and the control electronics.
  • Such a control circuit is distinguished from a hydromechanically operating pressure control valve by a higher dynamics and thus by shorter pressure change times and a higher control quality, a lower temperature and viscosity dependence, lower overshoot and a lower adjustable pressure, which can go down to atmospheric pressure.
  • a valve position of the control valve in the sense of its use as a press safety valve monitored is based on the rule that a pressure medium supply of the brake releasing and the clutch engaging hydraulic cylinder may only be possible if two-way valves work properly.
  • the two way valves switching position monitoring are the two way valves switching position monitoring.
  • only a single further switching position monitored directional control valve is now necessary in addition to the control valve in order to comply with the requirement.
  • control electronics and the pressure sensor are integrated into the control valve.
  • the control valve between the safety valve assembly and the hydraulic cylinder is located so that the prevailing hydraulic pressure in the hydraulic cylinder can be tapped directly on the connected to the hydraulic cylinder working connection of the control valve.
  • the plunger 10 of a press can be seen, which is connected via a coupling rod 11 with an eccentric shaft 12.
  • This can be driven by means of a clutch-brake combination 13 by an electric motor 14 via a drive shaft 15 with flywheel or be braked.
  • clutch-brake combinations are generally known, for example from DE-PS 1 207 725 or US-A 3,200,917, so that a more detailed description is unnecessary here. If no external force is applied, the clutch is released by a spring arrangement 16 and the brake is effective. The brake can be released hydraulically against the spring arrangement and the clutch engaged become.
  • an acceleration sensor 24 and / or a displacement sensor 25 is used for detecting states of the press ram 10.
  • another displacement sensor 26 is provided with which the position of the piston rod 17 can be detected.
  • the hydraulic cylinder 18 is supplied with pressure medium from a pressure medium source, which essentially comprises a hydraulic pump 35 and a hydraulic accumulator 36.
  • the hydraulic pump 35 with constant displacement is driven by an electric motor and sucks from a tank 37 per unit time a relatively small amount of pressure medium, which it emits in a pressure line 38, to which the hydraulic accumulator 36 is connected.
  • a proportional directional control valve 40 is provided with a pressure port 41 connected to the pressure line 38, a tank port 42 connected to the tank 37, and a consumer port 43.
  • the directional control valve 40 is continuously adjustable from a spring-centered position with negative coverage of the three ports, by controlling an electromagnet 44 and an electromagnet 45 in opposite directions, wherein in an adjustment in one direction an opening cross-section between the pressure port and the working port and in an adjustment in the opposite direction, an opening cross-section between the working port and the tank port is steadily increased.
  • the connection of the working connection to the respective other connection is completely closed already after a short distance.
  • the path of the control piston of the directional control valve 40 is detected by a displacement sensor 46.
  • valves 48 and 49 are inserted, each of which has a tank connected to the tank 37 and a first consumer terminal connected to a pressure chamber to the 20th the hydraulic cylinder 18 leading hydraulic line 50 is connected. Both valves 48 and 49 have a pressure port, wherein the pressure port of the valve 48 is connected to the load port of the directional control valve 40 and the pressure port of the valve 49 to a second consumer port of the valve 48. A second consumer port of the valve 49 is placed as the first consumer port to the hydraulic line 50.
  • the two valves 48 and 49 take under the action of a spring 51, a rest position in which each of the hydraulic line 50 connects to the tank 37.
  • the other two ports (pressure port and second consumer port) of each directional control valve 48 and 49 are shut off in the rest position of these valves. If, on the other hand, both directional control valves 48 and 49 are in their working position, into which they can be brought by energizing each one electromagnet 52, then there is the other two connections of the directional control valve 48 and in series with other terminals of the directional control valve 49 is a connection between the pressure chamber 20 and the consumer port 43 of the directional valve 40.
  • each of the two valves 48 and 49 is provided with a switch actuator 53 which outputs a signal when a valve switches. If there is no such signal, although it should be switched over, the system is shut down.
  • a pressure cell 60 is connected, from which thus the pressure in the pressure chamber 20 of the hydraulic cylinder 18 can be detected.
  • the pressure cell 60 can also sit directly on the consumer port 43 of the directional control valve 40, since there 48 and 49 at least approximately the same pressure as in the line 50 prevails at switched valves.
  • the electrical output signal of the load cell 60 and the sensors 22, 23, 24, 25 and 26 are applied to an electronic control unit 61, from which via an amplifier, the electromagnets 44 and 45 of the directional control valve 40 are driven.
  • the press ram 10 is held by the brake of the clutch brake combination at top dead center.
  • the two safety valves 48 and 49 are switched.
  • the control electronics now controls the opening cross-section between the terminals 41 and 43 of the directional control valve 40 so that the piston 19 of the hydraulic cylinder 18 moves with a desired and on the Wegaufillon 26 confirmed speed, thereby releasing the brake and the coupling parts abong.
  • the impact of the coupling parts on each other with a controlled, so reduced speed can be no or only small pressure overshoot arise.
  • the control electronics 61 allows in conjunction with the rotation angle or speed sensors 22 and 23 on the eccentric shaft 12 and on the drive shaft 15, a further control of the coupling process. It is conceivable, for example, a slip control for switching time minimization or wear optimization. It is also conceivable, for example, an acceleration control during the coupling or braking operation using the sensors 24 and 25th
  • the pressure in the pressure chamber 20 can also be regulated at the end and the piston can be returned in a regulated manner.
  • a single 4/2-way switching valve which may be designated 48, used as a safety valve.
  • the second safety valve is realized by the existing continuously adjustable directional control valve 70, which, like the directional control valve 40 of FIG. 1, has a pressure connection 41, a tank connection 42 connected directly to the tank 37 and two consumer connections 43 connected to the line 50.
  • the directional control valve 70 is therefore connected directly upstream of the pressure chamber 20.
  • a single connected to the line 50 consumer connection would suffice.
  • the load cell 60 which picks up the pressure directly in a consumer port 43, and the control electronics 61.
  • the position of the control piston of the directional control valve 70 can be detected by a displacement sensor 46.
  • a shift position sensor 53 monitors the directional control valve 70.
  • the directional control valve 70 assumes under the action of a spring 71 an end position in which the line 50 and thus the pressure chamber 20 of the hydraulic cylinder 18 via a consumer port 43 and the tank port 42 to the tank 37 are relieved.
  • a spring 71 By an electromagnet 45, the directional control valve 70 can be adjusted from the end position out steadily in one direction, the opening cross-section between the two terminals 42 and 43 is made smaller and smaller, before after a phase of negative overlap between the terminals, after which shut off the tank connection is an opening cross section between the Pressure port 41 and a consumer port 43 is opened more and more.
  • the safety valve 48 has a connected to the pressure line 38 pressure port, a connected to the tank 37 tank connection, a connected to the hydraulic line 50 first consumer terminal and connected to the pressure port 41 of the directional control valve 70 second consumer terminal and takes under the action of a spring 51 a rest position in, in which the first consumer connection to the tank connection, so the hydraulic line 50 is connected to the tank 37.
  • the other two ports (pressure port and second consumer port) of the directional control valve 48 are shut off in the rest position. After switching the directional control valve 48, the pressure port and the second consumer port are connected to each other and the other two ports shut off.
  • the pressure port and the second consumer port are connected to each other and the other two ports shut off.
  • a control of the speed of the Kolben19 and the pressure in the pressure chamber 20 in the same manner as in the embodiment of Figure 1 with the proportionally adjustable directional control valve 70, the control electronics 61 and the various sensors is possible in the clutch and braking.
  • the directional valve used for control also fulfills the function of a safety valve.
  • the safety valve 48 can sit in the intermediate plate construction directly on the directional control valve 70: Overall, one thus obtains a compact control module with the required valves, the control electronics and the load cell.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Control Of Presses (AREA)

Description

Die Erfindung geht aus von einer hydraulischen Steuerung, die zur Betätigung einer Kupplungsbremskombination insbesondere der Exzenterwelle einer mechanischen Presse vorgesehen ist und die die Merkmale aus dem Oberbegriff des Patentanspruchs 1 aufweist.The invention relates to a hydraulic control, which is provided for actuating a clutch brake combination, in particular the eccentric shaft of a mechanical press and having the features of the preamble of patent claim 1.

Eine derartige hydraulische Steuerung ist aus der WO 00/02720 bekannt. Bei dieser hydraulischen Steuerung wird in erster Linie dann eine größere Menge Druckmittel benötigt, wenn sich der Hydrozylinder 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 Hydrozylinder wenig Druckmittel benötigt wird, von der Hydropumpe aufgeladen wird und dann, wenn viel Druckmittel benötigt wird, Druckmittel abgibt.Such a hydraulic control is known from WO 00/02720. In this hydraulic control, a larger amount of pressure medium is needed in the first place when the hydraulic cylinder moves when releasing the brake and closing the clutch and when the high clutch pressure is built up and to the pressure medium is compressed. In the remaining time of a press cycle, no or only a small amount of pressure medium is needed. In order to use a small hydraulic pump, the pressure medium source includes a hydraulic accumulator, which is charged by the hydraulic pump within the cycle time in which the hydraulic cylinder little pressure medium is needed and then, if much pressure medium is needed, releases pressure medium.

Bei der bekannten hydraulischen Steuerung liegt der Zulaufanschluß einer Sicherheitsventilanordnung, die zum Beispiel aus zwei schaltstellungsüberwachten Wegeventilen besteht, in einem Strömungspfad, der von der Druckmittelquelle zu dem Hydrozylinder aufgebaut werden kann. Außerdem ist ein 3-Wege-Druckregelventil mit einem mit der Druckmittelquelle verbindbaren Druckanschluß, mit einem Tankanschluß und mit einem Regelanschluß vorhanden, der mit dem Zulaufanschluß der Sicherheitsventilanordnung verbunden ist. Das Druckregelventil ist ein elektrisch vorgesteuertes Druckregelventil, dessen Regelkolben einerseits durch einen durch das elektrische Pilotventil eingestellten Druck und durch den Druck am Regelanschluß gesteuert wird. Druckventile neigen im allgemeinen zum Schwingen. Diese Neigung kann nur durch eine entsprechende Bedämpfung vermieden werden kann. Dadurch aber wird die Zeit zum Aufbau eines Drucks relativ lang. Die Regelgüte ist verhältnismäßig niedrig. Insofern ist durch ein Druckregelventil nicht in allen Fällen den gestellten Anforderungen zu genügen.In the known hydraulic control of the inlet port of a safety valve assembly, which consists for example of two switch position monitored directional valves, in a flow path, which can be constructed by the pressure medium source to the hydraulic cylinder. In addition, a 3-way pressure control valve with a connectable to the pressure medium source pressure port, with a tank port and with a control port is present, which is connected to the inlet port of the safety valve assembly. The pressure control valve is an electrically piloted pressure control valve whose control piston is controlled on the one hand by a set by the electric pilot valve pressure and by the pressure at the control port. Pressure valves tend to vibrate in general. This tendency can only be achieved by a suitable damping can be avoided. As a result, the time to build up a pressure is relatively long. The quality of control is relatively low. In this respect, by a pressure control valve is not always sufficient to meet the requirements.

Eine weitere hydraulische Steuerung zur Betätigung einer Kupplungsbremskombination ist aus der WO-A-86 00849 bekannt.Another hydraulic control for actuating a clutch brake combination is known from WO-A-86 00849.

Ziel der Erfindung ist es somit, eine hydraulische Steuerung mit den Merkmalen aus dem Oberbegriff des Patentanspruchs 1 so weiterzuentwickeln, daß sie eine hohe Dynamik besitzt und damit kurze Druckaufbau- und Druckabbauzeiten und eine hohe Regelgüte ermöglicht.The aim of the invention is thus to further develop a hydraulic control with the features of the preamble of claim 1 so that it has a high dynamics and thus allows short pressure build-up and pressure reduction times and a high control quality.

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 object is achieved in that the hydraulic control is equipped except with the features of the preamble in addition to the features of the characterizing part of patent claim 1.

Bei einer erfindungsgemäßen Steuerung für eine hydraulisch betätigbare Kupplungsbremskombination ist mittels des Proportional-Wegeventils, des elektrischen Drucksensors und der Regelelektronik ein elektrohydraulischer Druckregelkreis aufgebaut. Ein solcher Regelkreis zeichnet sich gegenüber einem hydromechanisch arbeitenden Druckregelventil durch eine höhere Dynamik und damit durch kürzere Druckänderungszeiten und eine höhere Regelgüte, eine geringere Temperatur- und Viskositätsabhängigkeit, geringere Überschwinger und einen niedriger einstellbaren Druck aus, der bis auf Atmosphärendruck heruntergehen kann.In an inventive control for a hydraulically actuated clutch brake combination, an electro-hydraulic pressure control circuit is constructed by means of the proportional directional control valve, the electrical pressure sensor and the control electronics. Such a control circuit is distinguished from a hydromechanically operating pressure control valve by a higher dynamics and thus by shorter pressure change times and a higher control quality, a lower temperature and viscosity dependence, lower overshoot and a lower adjustable pressure, which can go down to atmospheric pressure.

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

Besonders bevorzugt ist gemäß Patentanspruch 2 eine Ventilstellung des Regelventils im Sinne von dessen Verwendung als Pressensicherheitsventil überwachbar. Dem liegt die Vorschrift zugrunde, daß eine Druckmittelversorgung des die Bremse lösenden und die Kupplung einrückenden Hydrozylinders nur dann möglich sein darf, wenn zwei Wegeventile ordnungsgemäß funktionieren. Für die zyklische Kontrolle der ordnungsgemäßen Funktion sind die beiden Wegeventile schaltstellungsüberwacht. Bei einer Ausbildung gemäß Patentanspruch 2 ist nun neben dem Regelventil nur noch ein einziges weiteres schaltstellungüberwachtes Wegeventil notwendig, um der Vorschrift genüge zu leisten.Particularly preferred according to claim 2, a valve position of the control valve in the sense of its use as a press safety valve monitored. This is based on the rule that a pressure medium supply of the brake releasing and the clutch engaging hydraulic cylinder may only be possible if two-way valves work properly. For the cyclic control of the proper function are the two way valves switching position monitoring. In an embodiment according to claim 2, only a single further switching position monitored directional control valve is now necessary in addition to the control valve in order to comply with the requirement.

Vorteilhafterweise werden gemäß den Patentansprüchen 5 und 6 die Regelelektronik und der Drucksensor in das Regelventil integriert. Für eine Druckerfassung ohne lange Leitung ist es dann günstig, wenn sich das Regelventil zwischen der Sicherheitsventilanordnung und dem Hydrozylinder befindet, so daß der im Hydrozylinder herrschende Arbeitsdruck unmittelbar an dem mit dem Hydrozylinder verbunden Arbeitsanschluß des Regelventils abgegriffen werden kann.Advantageously, according to the claims 5 and 6, the control electronics and the pressure sensor are integrated into the control valve. For a pressure detection without a long line, it is advantageous if the control valve between the safety valve assembly and the hydraulic cylinder is located so that the prevailing hydraulic pressure in the hydraulic cylinder can be tapped directly on the connected to the hydraulic cylinder working connection of the control valve.

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 embodiments of a hydraulic control according to the invention for a hydraulically actuated clutch brake combination for the drive shaft of 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 Proportional-Wegeventil zwischen der Druckmittelquelle und zwei Sicherheitsventilen angeordnet ist und
Figur 2
das zweites Ausführungsbeispiel, bei dem das Proportional-Wegeventil auch als Sicherheitsventil benutzt wird.
Show it
FIG. 1
a first embodiment in which the proportional directional control valve between the pressure medium source and two safety valves is arranged and
FIG. 2
the second embodiment, in which the proportional directional control valve is also used as a safety valve.

In den beiden Figuren 1 und 2 ist der Stößel 10 einer Presse zu erkennen, der über eine Koppelstange 11 mit einer Exzenterwelle 12 verbunden ist. Diese kann mit Hilfe einer Kupplung-Brems-Kombination 13 von einem Elektromotor 14 über eine Antriebswelle 15 mit Schwungrad angetrieben werden oder aber abgebremst werden. Derartige Kupplungs-Brems-Kombinationen sind allgemein, zum Beispiel aus der DE-PS 1 207 725 oder der US-A 3 200 917 bekannt, so daß sich hier eine nähere Beschreibung erübrigt. Wird keine äußere Kraft aufgebracht, so ist durch eine Federanordnung 16 die Kupplung gelöst und die Bremse wirksam. Gegen die Federanordnung kann hydraulisch die Bremse gelöst und die Kupplung eingerückt werden. Dazu dient ein einseitig wirkender Hydrozylinder 18, dessen Inneres durch einen Kolben 19, an dem eine Kolbenstange 17 befestigt ist, in einen vollzylindrischen, kolbenstangenabseitigen Druckraum 20 und in einen ringzylindrischen kolbenstangenseitigen Aufnahmeraum 21 für die als Schraubendruckfeder ausgebildete Federanordnung 16 aufgeteilt ist. Bei von Druck entlasteten Druckraum 20 ist die Bremse mit einer durch die Vorspannung der Schraubendruckfeder 16 bestimmten Kraft betätigt. Bei einem Druckanstieg im Druckraum 20 verringert sich zunächst die Bremskraft, bis schließlich der Druck einen der Vorspannung der Schraubendruckfeder 16 äquivalenten Wert annimmt. Dann beginnen der Kolben 19 und die Kolbenstange 17 sich zu bewegen. Die Bremse ist gelöst. Nach kurzem Hub, währenddessen der Druck im Druckraum 20 wegen der steigenden Spannung der Schraubendruckfeder 16 geringfügig zunimmt, legen sich Teile der Kupplung 13 aneinander. 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 plunger 10 of a press can be seen, which is connected via a coupling rod 11 with an eccentric shaft 12. This can be driven by means of a clutch-brake combination 13 by an electric motor 14 via a drive shaft 15 with flywheel or be braked. Such clutch-brake combinations are generally known, for example from DE-PS 1 207 725 or US-A 3,200,917, so that a more detailed description is unnecessary here. If no external force is applied, the clutch is released by a spring arrangement 16 and the brake is effective. The brake can be released hydraulically against the spring arrangement and the clutch engaged become. Serves a unilaterally acting hydraulic cylinder 18, the interior of which is divided by a piston 19, to which a piston rod 17 is fixed, in a fully cylindrical, piston rod side pressure chamber 20 and in a ring-cylindrical piston rod side receiving space 21 for trained as a helical compression spring spring assembly 16. When relieved of pressure pressure chamber 20, the brake is actuated with a determined by the bias of the helical compression spring 16 force. At a pressure increase in the pressure chamber 20, the braking force initially decreases until finally the pressure assumes a value equivalent to the prestressing of the helical compression spring 16. Then, the piston 19 and the piston rod 17 start to move. The brake is released. After a short stroke, during which the pressure in the pressure chamber 20 increases slightly due to the increasing tension of the helical compression spring 16, parts of the clutch 13 abut each other. The transmittable torque via the clutch 13 now depends on the height of the pressure in the pressure chamber 20.

Mit der Exzenterwelle ist ein Drehwinkelgeber oder ein Drehzahlgeber 22 und mit der Antriebswelle ein Drehwinkelgeber oder ein Drehzahlgeber 23 gekoppelt. Zur Erfassung von Zuständen des Pressenstößels 10 dient ein Beschleunigungssensor 24 und/oder ein Wegsensor 25. Schließlich ist ein weiterer Wegsensor 26 vorgesehen, mit dem die Position der Kolbenstange 17 erfaßt werden kann.With the eccentric shaft, a rotary encoder or a speed sensor 22 and to the drive shaft, a rotary encoder or a speed sensor 23 is coupled. For detecting states of the press ram 10, an acceleration sensor 24 and / or a displacement sensor 25 is used. Finally, another displacement sensor 26 is provided with which the position of the piston rod 17 can be detected.

Der Hydrozylinder 18 wird mit Druckmittel von einer Druckmittelquelle aus gespeist, die im wesentlichen eine Hydropumpe 35 und einen Hydrospeicher 36 umfaßt. Die Hydropumpe 35 mit konstantem Hubvolumen wird von einem Elektromotor angetrieben und saugt aus einem Tank 37 pro Zeiteinheit eine relativ kleine Druckmittelmenge an, die sie in einen Druckleitung 38 abgibt, an die auch der Hydrospeicher 36 angeschlossen ist.The hydraulic cylinder 18 is supplied with pressure medium from a pressure medium source, which essentially comprises a hydraulic pump 35 and a hydraulic accumulator 36. The hydraulic pump 35 with constant displacement is driven by an electric motor and sucks from a tank 37 per unit time a relatively small amount of pressure medium, which it emits in a pressure line 38, to which the hydraulic accumulator 36 is connected.

Die Einspeisung von Druckmittel in den Druckraum 20 und den Ablauf von Druckmittel aus dem Druckraum wird bei beiden gezeigten Ausführungsbeispielen durch ein elektrisch proportional verstellbares Wegeventil und wenigstens ein weiteres elektrisch umschaltbares Wegeventil gesteuert. Bei dem Ausführungsbeispiel nach Figur 1 ist ein Proportional-Wegeventil 40 mit einem mit der Druckleitung 38 verbundenen Druckanschluß 41, einem mit dem Tank 37 verbundenen Tankanschluß 42 und mit einem Verbraucheranschluß 43 vorhanden. Das Wegeventil 40 ist von einer federzentrierten Mittelstellung mit negativer Überdeckung der drei genannten Anschlüsse aus, durch Ansteuerung eines Elektromagneten 44 bzw. eines Elektromagneten 45 nach entgegengesetzten Richtungen stetig verstellbar, wobei bei einer Verstellung in die eine Richtung ein Öffnungsquerschnitt zwischen dem Druckanschluß und dem Arbeitsanschluß und bei einer Verstellung in die entgegengesetzte Richtung ein Öffnungsquerschnitt zwischen dem Arbeitsanschluß und dem Tankanschluß stetig vergrößert wird. Die Verbindung des Arbeitsanschlusses zum jeweiligen anderen Anschluß wird dagegen schon nach kurzem Weg vollständig geschlossen. Der Weg des Steuerkolbens des Wegeventils 40 wird durch einen Weggeber 46 erfaßt.The supply of pressure medium in the pressure chamber 20 and the flow of pressure medium from the pressure chamber is controlled in both embodiments shown by an electrically proportional proportional directional control valve and at least one further electrically switchable way valve. In the embodiment 1, a proportional directional control valve 40 is provided with a pressure port 41 connected to the pressure line 38, a tank port 42 connected to the tank 37, and a consumer port 43. The directional control valve 40 is continuously adjustable from a spring-centered position with negative coverage of the three ports, by controlling an electromagnet 44 and an electromagnet 45 in opposite directions, wherein in an adjustment in one direction an opening cross-section between the pressure port and the working port and in an adjustment in the opposite direction, an opening cross-section between the working port and the tank port is steadily increased. On the other hand, the connection of the working connection to the respective other connection is completely closed already after a short distance. The path of the control piston of the directional control valve 40 is detected by a displacement sensor 46.

Zwischen den Verbraucheranschluß 43 des Wegeventils 40 und dem Hydrozylinder 18 sind als Sicherheitsventile zwei 4/2-Wege-Schaltventile 48 und 49 eingefügt, die von denen jedes einen mit dem Tank 37 verbunden Tankanschluß und einen ersten Verbraucheranschluß aufweist, der an eine zum Druckraum 20 des Hydrozylinders 18 führende Hydroleitung 50 angeschlossen ist. Beide Ventile 48 und 49 haben einen Druckanschluß, wobei der Druckanschluß des Ventils 48 mit dem Verbraucheranschluß des Wegeventils 40 und der Druckanschluß des Ventils 49 mit einem zweiten Verbraucheranschluß des Ventils 48 verbunden ist. Ein zweiter Verbraucheranschluß des Ventils 49 ist wie dessen erster Verbraucheranschluß an die Hydroleitung 50 gelegt.Between the consumer port 43 of the directional control valve 40 and the hydraulic cylinder 18 as safety valves two 4/2-way switching valves 48 and 49 are inserted, each of which has a tank connected to the tank 37 and a first consumer terminal connected to a pressure chamber to the 20th the hydraulic cylinder 18 leading hydraulic line 50 is connected. Both valves 48 and 49 have a pressure port, wherein the pressure port of the valve 48 is connected to the load port of the directional control valve 40 and the pressure port of the valve 49 to a second consumer port of the valve 48. A second consumer port of the valve 49 is placed as the first consumer port to the hydraulic line 50.

Die beiden Ventile 48 und 49 nehmen unter der Wirkung einer Feder 51 eine Ruhestellung ein, in der jedes für sich die Hydroleitung 50 mit dem Tank 37 verbindet. Die beiden weiteren Anschlüsse (Druckanschluß und zweiter Verbraucheranschluß) jedes Wegeventils 48 und 49 sind in der Ruhestellung dieser Ventile abgesperrt. Befinden sich dagegen beide Wegeventile 48 und 49 in ihrer Arbeitsstellung, in diese durch Bestromung von jeweils einem Elektromagneten 52 gebracht werden können, 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 Verbraucheranschluß 43 des Wegeventils 40. Somit ist, wenn sich auch nur eines der beiden Wegeventile in seiner Ruhestellung befindet, der Druckraum 20 des Hydrozylinders 18 von Druck entlastet. Jedes der beiden Ventile 48 und 49 ist mit einem Schaltstellungsgeber 53 ausgestattet, der ein Signal abgibt, wenn ein Ventil umschaltet. Unterbleibt ein solches Signal, obwohl umgeschaltet werden soll, wird die Anlage stillgesetzt.The two valves 48 and 49 take under the action of a spring 51, a rest position in which each of the hydraulic line 50 connects to the tank 37. The other two ports (pressure port and second consumer port) of each directional control valve 48 and 49 are shut off in the rest position of these valves. If, on the other hand, both directional control valves 48 and 49 are in their working position, into which they can be brought by energizing each one electromagnet 52, then there is the other two connections of the directional control valve 48 and in series with other terminals of the directional control valve 49 is a connection between the pressure chamber 20 and the consumer port 43 of the directional valve 40. Thus, if only one of the two-way valves is in its rest position, the pressure chamber 20 of the hydraulic cylinder 18 of pressure relieved. Each of the two valves 48 and 49 is provided with a switch actuator 53 which outputs a signal when a valve switches. If there is no such signal, although it should be switched over, the system is shut down.

An die Hydroleitung 50 ist eine Druckmeßdose 60 angeschlossen, von der somit der Druck in dem Druckraum 20 des Hydrozylinders 18 erfaßbar ist. Alternativ kann die Druckmeßdose 60 auch unmittelbar am Verbraucheranschluß 43 des Wegeventils 40 sitzen, da dort bei geschalteten Ventilen 48 und 49 wenigstens annähernd der gleiche Druck wie in der Leitung 50 herrscht. Das elektrische Ausgangssignal der Druckmeßdose 60 sowie der Sensoren 22, 23, 24, 25 und 26 werden an eine Regelelektronik 61 gegeben, von der über einen Verstärker die Elektromagnete 44 und 45 des Wegeventils 40 angesteuert werden.To the hydraulic line 50, a pressure cell 60 is connected, from which thus the pressure in the pressure chamber 20 of the hydraulic cylinder 18 can be detected. Alternatively, the pressure cell 60 can also sit directly on the consumer port 43 of the directional control valve 40, since there 48 and 49 at least approximately the same pressure as in the line 50 prevails at switched valves. The electrical output signal of the load cell 60 and the sensors 22, 23, 24, 25 and 26 are applied to an electronic control unit 61, from which via an amplifier, the electromagnets 44 and 45 of the directional control valve 40 are driven.

Im Ruhezustand der Presse wird der Pressenstößel 10 durch die Bremse der Kupplungsbremskombination am oberen Totpunkt gehalten. Zu Beginn eines Pressenzyklus werden die beiden Sicherheitsventil 48 und 49 umgeschaltet. Die Regelelektronik steuert nun den Öffnungsquerschnitt zwischen den Anschlüssen 41 und 43 des Wegeventils 40 so, daß sich der Kolben 19 des Hydrozylinders 18 mit einer gewünschten und über den Wegaufnehmer 26 rückgemeldeten Geschwindigkeit bewegt und dabei die Bremse löst und die Kupplungsteile aneinanderfährt. Das Auftreffen der Kupplungsteile aufeinander mit einer kontrollierten, also reduzierter Geschwindigkeit läßt dabei keine oder nur kleine Drucküberschwinger entstehen. Anschließend wird durch Zufuhr von Druckmittel von der Druckmittelquelle über die Anschlüsse 41 und 43 des Wegeventils 40 in den Druckraum 20 und durch Abfuhr von Druckmittel aus dem Druckraum über die beiden Anschlüsse 43 und 42 des Wegeventils 40 zum Tank 37 der Druck in dem Druckraum 20 entsprechend einem gewünschten Druckprofil geregelt. Die Regelelektronik 61 ermöglicht in Verbindung mit den Drehwinkel- oder Drehzahlsensoren 22 und 23 an der Exzenterwelle 12 und an der Antriebswelle 15 eine weiterführende Regelung des Kupplungsvorganges. Denkbar ist zum Beispiel eine Schlupfregelung zur Schaltzeitminimierung oder Verschleißoptimierung. Ebenso denkbar ist zum Beispiel eine Beschleunigungsregelung während des Kuppel- oder Bremsvorganges mit Hilfe der Sensoren 24 und 25.At rest of the press, the press ram 10 is held by the brake of the clutch brake combination at top dead center. At the beginning of a press cycle, the two safety valves 48 and 49 are switched. The control electronics now controls the opening cross-section between the terminals 41 and 43 of the directional control valve 40 so that the piston 19 of the hydraulic cylinder 18 moves with a desired and on the Wegaufnehmer 26 confirmed speed, thereby releasing the brake and the coupling parts abeinander. The impact of the coupling parts on each other with a controlled, so reduced speed can be no or only small pressure overshoot arise. Subsequently, by supplying pressure medium from the pressure medium source via the ports 41 and 43 of the directional valve 40 into the pressure chamber 20 and by removing pressure medium from the pressure chamber via the two ports 43 and 42 of the directional control valve 40 to the tank 37, the pressure in the pressure chamber 20 accordingly regulated a desired pressure profile. The control electronics 61 allows in conjunction with the rotation angle or speed sensors 22 and 23 on the eccentric shaft 12 and on the drive shaft 15, a further control of the coupling process. It is conceivable, for example, a slip control for switching time minimization or wear optimization. It is also conceivable, for example, an acceleration control during the coupling or braking operation using the sensors 24 and 25th

Wie beim Beginn eines Pressenzyklus kann auch an dessen Ende der Druck in dem Druckraum 20 geregelt und der Kolben geregelt zurückgefahren werden.As at the beginning of a press cycle, the pressure in the pressure chamber 20 can also be regulated at the end and the piston can be returned in a regulated manner.

Bei dem Ausführungsbeispiel nach Figur 2 ist nur ein einziges 4/2-Wege-Schaltventil, das mit 48 bezeichnet sein möge, als Sicherheitsventil verwendet. Das zweite Sicherheitsventil ist durch das vorhandene stetig verstellbare Wegeventil 70 realisiert, das wie das Wegeventil 40 aus Figur 1 einen Druckanschluß 41, einen unmittelbar mit dem Tank 37 verbunden Tankanschluß 42 und zwei mit der Leitung 50 verbundene Verbraucheranschlüsse 43 aufweist. Das Wegeventil 70 ist also nun unmittelbar dem Druckraum 20 vorgeschaltet. Natürlich würde auch ein einziger mit der Leitung 50 verbundener Verbraucheranschluß genügen. Mit dem Wegeventil 70 zu einer Baueinheit zusammengefaßt und in dieses integriert ist die Druckmeßdose 60, die unmittelbar in einem Verbraucheranschluß 43 den Druck abgreift, und die Regelelektronik 61. Die Position des Steuerkolbens des Wegeventils 70 ist durch einen Weggeber 46 erfaßbar. Außerdem überwacht ein Schaltstellungsgeber 53 das Wegeventil 70.In the embodiment of Figure 2, only a single 4/2-way switching valve, which may be designated 48, used as a safety valve. The second safety valve is realized by the existing continuously adjustable directional control valve 70, which, like the directional control valve 40 of FIG. 1, has a pressure connection 41, a tank connection 42 connected directly to the tank 37 and two consumer connections 43 connected to the line 50. The directional control valve 70 is therefore connected directly upstream of the pressure chamber 20. Of course, a single connected to the line 50 consumer connection would suffice. With the directional control valve 70 combined to form a unit and integrated into this is the load cell 60, which picks up the pressure directly in a consumer port 43, and the control electronics 61. The position of the control piston of the directional control valve 70 can be detected by a displacement sensor 46. In addition, a shift position sensor 53 monitors the directional control valve 70.

Das Wegeventil 70 nimmt unter der Wirkung einer Feder 71 eine Endstellung ein, in der die Leitung 50 und damit der Druckraum 20 des Hydrozylinders 18 über einen Verbraucheranschluß 43 und den Tankanschluß 42 zum Tank 37 entlastet sind. Durch einen Elektromagneten 45 kann das Wegeventil 70 aus der Endstellung heraus stetig in die eine Richtung verstellt werden, wobei der Öffnungsquerschnitt zwischen den beiden Anschlüssen 42 und 43 immer kleiner gemacht wird, ehe nach einer Phase negativer Überdeckung zwischen den Anschlüssen, nach der der Tankanschluß abgesperrt ist, ein Öffnungsquerschnitt zwischen dem Druckanschluß 41 und einem Verbraucheranschluß 43 immer mehr aufgemacht wird.The directional control valve 70 assumes under the action of a spring 71 an end position in which the line 50 and thus the pressure chamber 20 of the hydraulic cylinder 18 via a consumer port 43 and the tank port 42 to the tank 37 are relieved. By an electromagnet 45, the directional control valve 70 can be adjusted from the end position out steadily in one direction, the opening cross-section between the two terminals 42 and 43 is made smaller and smaller, before after a phase of negative overlap between the terminals, after which shut off the tank connection is an opening cross section between the Pressure port 41 and a consumer port 43 is opened more and more.

Das Sicherheitsventil 48 hat einen mit der Druckleitung 38 verbundenen Druckanschluß, einen mit dem Tank 37 verbundenen Tankanschluß, einen mit der Hydroleitung 50 verbundenen ersten Verbraucheranschluß und einen mit dem Druckanschluß 41 des Wegeventils 70 verbundenen zweiten Verbraucheranschluß und nimmt unter der Wirkung einer Feder 51 eine Ruhestellung ein, in der der erste Verbraucheranschluß mit dem Tankanschluß, also die Hydroleitung 50 mit dem Tank 37 verbunden ist. Die beiden weiteren Anschlüsse (Druckanschluß und zweiter Verbraucheranschluß) des Wegeventils 48 sind in der Ruhestellung abgesperrt. Nach Umschaltung des Wegeventils 48 sind der Druckanschluß und der zweite Verbraucheranschluß miteinander verbunden und die beiden anderen Anschlüsse abgesperrt. Somit entlastet in der Ruhestellung jedes der beiden Wegeventile 48 und 70 den Druckraum 20 für sich allein zum Tank. Also müssen beide Wegeventile aus ihre Ruhestellung gebracht worden sein, damit ein Zufluß von Druckmittel zum Druckraum 20 möglich ist.The safety valve 48 has a connected to the pressure line 38 pressure port, a connected to the tank 37 tank connection, a connected to the hydraulic line 50 first consumer terminal and connected to the pressure port 41 of the directional control valve 70 second consumer terminal and takes under the action of a spring 51 a rest position in, in which the first consumer connection to the tank connection, so the hydraulic line 50 is connected to the tank 37. The other two ports (pressure port and second consumer port) of the directional control valve 48 are shut off in the rest position. After switching the directional control valve 48, the pressure port and the second consumer port are connected to each other and the other two ports shut off. Thus relieves in the rest position each of the two-way valves 48 and 70, the pressure chamber 20 alone to the tank. So both valves have been brought from their rest position, so that an inflow of pressure medium to the pressure chamber 20 is possible.

Beim Ausführungsbeispiel nach Figur 2 ist beim Kupplungs- und beim Bremsvorgang ein Regelung der Geschwindigkeit des Kolbens19 und des Drucks im Druckraum 20 in derselben Weise wie bei dem Ausführungsbeispiel nach Figur 1 mit dem proportional verstellbaren Wegeventil 70, der Regelelektronik 61 und den verschieden Sensoren möglich. Darüber hinaus erfüllt das zur Regelung benutzte Wegeventil auch die Funktion eines Sicherheitsventils. Das Sicherheitsventil 48 kann in Zwischenplattenbauweise unmittelbar am Wegeventil 70 sitzen: Insgesamt erhält man somit einen kompakten Steuerungsmodul mit den benötigten Ventilen, der Regelelektronik und der Druckmeßdose.In the embodiment of Figure 2, a control of the speed of the Kolben19 and the pressure in the pressure chamber 20 in the same manner as in the embodiment of Figure 1 with the proportionally adjustable directional control valve 70, the control electronics 61 and the various sensors is possible in the clutch and braking. In addition, the directional valve used for control also fulfills the function of a safety valve. The safety valve 48 can sit in the intermediate plate construction directly on the directional control valve 70: Overall, one thus obtains a compact control module with the required valves, the control electronics and the load cell.

Claims (6)

  1. A hydraulic control system for a hydraulically actuated clutch-brake combination (13) in particular for the eccentric shaft of a mechanical press, having a pressure medium source with a hydraulic pump (35) and preferably also a hydraulic accumulator (36) for supplying pressure fluid to a hydraulic cylinder (18) which actuates the clutch and/or the brake,
    having a safety valve arrangement (48, 49) with a pressure port via which a flow path leads from the pressure medium source (35, 36) to the hydraulic cylinder (18),
    and having a proportionally adjustable control valve (40, 70) with which the pressure acting on the cylinder (18) can be set,
    characterized by the fact
    that an electrical pressure sensor (60) is present, by means of which the pressure acting on the hydraulic cylinder (18) can be sensed,
    that a control electronics system (61) is present, to which is fed an electric signal of the pressure sensor (60) corresponding to the pressure sensed,
    and that the control valve (40, 70) is an electrically controlled proportional control valve which is controlled by the control electronics system (61) in manner corresponding to the sensed actual pressure and the desired target pressure.
  2. A hydraulic control system according to claim 1, characterized by the fact that a valve position of the control valve (70) is monitored with the effect of utilizing said control valve (70) as a safety valve.
  3. A hydraulic control system according to claim 2, characterized by the fact that the control valve (70) is equipped with a position sensor (46) for the valve position and that the monitoring of the valve position is done by evaluation of the output signal of the position sensor (46).
  4. A hydraulic control system according to claim 2, characterized by the fact that the control valve (70) is equipped with a valve position sensor (53) by means of which the specific valve position at any time can be sensed.
  5. A hydraulic control system according to any of the preceding claims, characterized by the fact that the control electronics system (61) and the control valve (70) are combined to form one structural unit.
  6. A hydraulic control system according to any of the preceding claims, characterized by the fact that the pressure sensor (60) and the control valve (70) are combined to form one structural unit.
EP20010127201 2000-12-02 2001-11-16 Hydraulic control system for a hydraulically actuated clutch-brake combination in particular for the eccentric shaft of a mechanical press Expired - Lifetime EP1211059B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE10060083 2000-12-02
DE10060083 2000-12-02
DE10062229A DE10062229A1 (en) 2000-12-02 2000-12-13 Hydraulic control for a hydraulically actuated clutch / brake combination, in particular on the eccentric shaft of a mechanical press
DE10062229 2000-12-13

Publications (3)

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EP1211059A2 EP1211059A2 (en) 2002-06-05
EP1211059A3 EP1211059A3 (en) 2003-04-16
EP1211059B1 true EP1211059B1 (en) 2006-08-16

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EP20010127201 Expired - Lifetime EP1211059B1 (en) 2000-12-02 2001-11-16 Hydraulic control system for a hydraulically actuated clutch-brake combination in particular for the eccentric shaft of a mechanical press

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008051209B4 (en) * 2008-10-14 2012-02-16 Ortlinghaus-Werke Gmbh Control system for influencing the ram dynamics in press machines
EP3067192A1 (en) * 2015-03-09 2016-09-14 Ortlinghaus-Werke GmbH Control device, system and method for operating a clutch or brake

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3200917A (en) * 1963-05-14 1965-08-17 Ortlinghaus Geb Air cooled compact clutch and brake
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
ATE6231T1 (en) * 1980-10-31 1984-03-15 L. Schuler Gmbh CONTROL FOR THE CLUTCH AND/OR BRAKE OF A PRESS.
DE3523163A1 (en) * 1984-07-19 1986-02-13 ZF-Herion-Systemtechnik GmbH, 7990 Friedrichshafen PRESSURE CONTROL DEVICE FOR A HYDRAULICALLY OPERABLE CLUTCH AND / OR BRAKE OF THE DRIVE SHAFT OF A PRESS
DD256851A1 (en) * 1986-12-31 1988-05-25 Warnke Umformtech Veb K DEVICE FOR CONTROLLING THE MOMENT PROCESSING OF PRESSURE-RELATED FRICTION COUPLINGS OR BZW. BRAKING TO PRESSES
DE4314801B4 (en) * 1993-05-05 2004-09-09 Bosch Rexroth Ag Hydraulic system, especially for a press brake
ES2128920B1 (en) * 1996-02-02 1999-12-16 Coop Goizper S HYDRAULIC SYSTEM FOR THE CONTROL OF BRAKES, CLUTCHES AND BRAKES-CLUTCHES.
DE19831144A1 (en) * 1998-07-11 2000-01-13 Mannesmann Rexroth Ag Hydraulic control for a hydraulically operated clutch / brake combination for the drive shaft of a mechanical press

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EP1211059A3 (en) 2003-04-16
DE50110744D1 (en) 2006-09-28
EP1211059A2 (en) 2002-06-05

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