EP1780420A2 - Hydraulic pressure supply unit and electro-hydraulic work unit - Google Patents

Hydraulic pressure supply unit and electro-hydraulic work unit Download PDF

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Publication number
EP1780420A2
EP1780420A2 EP06122576A EP06122576A EP1780420A2 EP 1780420 A2 EP1780420 A2 EP 1780420A2 EP 06122576 A EP06122576 A EP 06122576A EP 06122576 A EP06122576 A EP 06122576A EP 1780420 A2 EP1780420 A2 EP 1780420A2
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EP
European Patent Office
Prior art keywords
pressure
pump
supply unit
working
pumps
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP06122576A
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German (de)
French (fr)
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EP1780420B1 (en
EP1780420A3 (en
Inventor
Manfred Kurz
Bertold Grimmer
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Hoerbiger Automatisierungstechnik Holding GmbH
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Hoerbiger Automatisierungstechnik Holding GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/022—Systems essentially incorporating special features for controlling the speed or actuating force of an output member in which a rapid approach stroke is followed by a slower, high-force working stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/001—With multiple inputs, e.g. for dual control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20592—Combinations of pumps for supplying high and low pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/265—Control of multiple pressure sources
    • F15B2211/2654—Control of multiple pressure sources one or more pressure sources having priority
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/3051—Cross-check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/575—Pilot pressure control
    • F15B2211/5756—Pilot pressure control for opening a valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/775—Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press

Definitions

  • the invention relates to a hydraulic pressure supply unit, with two alternately pressurized outputs, with a reversible pump unit with at least two pumps and all pumps together driving reversible electric motor, possibly with mutually unblocking check valves in front of the outputs, and a supply for hydraulic medium, wherein a pump as a low pressure pump and a pump is designed as a high-pressure pump, wherein the pressurized outputs of both pumps are connected to the same output of the pressure supply unit, further comprising an electro-hydraulic working unit comprising a double-acting hydraulic cylinder, an electro-hydraulic pressure supply unit for alternately pressurizing a respective working space of the working cylinder, and a connection for the external power supply.
  • the object of the present invention was therefore a pressure supply unit with which a large amount of hydraulic medium can be made available until a predefinable pressure level is reached, while after reaching this pressure level hydraulic medium can be made available at high pressure, this function is fulfilled in two simple alternately pressurized outputs.
  • Another task was then a hydraulic working unit, the working cylinder can be reversed easily reversible first in both directions, then subsequently increases the load, which may also be stationary, the working cylinder exerts a high force.
  • the pressure supply unit is characterized in that both outputs of the high pressure pump from the low pressure pump are separated by check valves and each pump is connected via its own shuttle valve with the supply of hydraulic fluid, and that both outputs of the low pressure pump via pressure switching valves connected to the tank are, wherein the control terminals of the pressure switching valves are connected to the outputs of the high pressure pump such that the control terminal of that Druckschaltventils is acted upon on the currently pressurized side of the currently pressurized output of the high pressure pump.
  • the low-pressure pump is switched off by this valve and the consumer then only supplied with the delivery volume of the high-pressure pump.
  • this functionality can be achieved by simply reversing the direction of rotation of the pumps at both outputs of the pressure supply unit, the check valves operating between the different pressure stages of the pressure supply unit on both sides of the pumps independently of the other side. This ensures the greatest possible independence and thus flexibility for the design of the pressure supply unit on both sides.
  • the electric motor used to drive the pumps can be just for the desired highest system pressure, i. be designed for the high-pressure pump, since at lower pressure levels even when operating both pumps in parallel with the same engine Ausmaschine can be found.
  • At least one, preferably both, of the pressure switching valves has an independently adjustable from the other pressure switching valve switching point. This allows different characteristics to be set on both outputs.
  • the pumps are designed as constant pumps, which greatly simplifies the system in terms of manufacturing as well as operation.
  • a tank for the hydraulic medium in the pressure supply unit integrated and each pump is connected to its own shuttle valve for pressure tank switching.
  • an electro-hydraulic working unit with a double-acting hydraulic cylinder whose working spaces are alternately pressurized, characterized in that the pressure supply unit formed according to one of the preceding paragraphs and each working space of the working cylinder is always connected to the same output of the pressure supply unit ,
  • This can be achieved with simple control without complicated Umschaltventilan Aunt and compact design for the working cylinder fast rapid by initially supply of hydraulic medium by both pumps together and then a high level of force, if by increasing the load on the working cylinder, the pressure level rises so much that the low pressure pump is switched off. The flow rate is then reduced to the amount provided by the high pressure pump.
  • the working cylinder is designed as a differential cylinder.
  • a correspondingly opposite adjustment of the switching points of the pressure switching valves may be advantageous.
  • the working cylinder is designed as a synchronous cylinder with extendible on both sides piston rods.
  • the system can be made completely symmetrical.
  • a different force / displacement characteristic in the different directions of movement also due to different requirements, for example, high power only required in one direction, be provided.
  • the unimpeded power stroke in the connecting lines between the pump unit of the pressure supply unit and the working chambers of the working cylinder by the pressure in the respective other line unlockable check valves intended.
  • the drawing figure shows the hydraulic circuit diagram of an electro-hydraulic working unit according to the invention, as it can be used for a wide variety of applications.
  • the electro-hydraulic working unit consists of at least one working cylinder 1, the two working chambers 2, 3, alternately acted upon by hydraulic medium and in such a way the piston 4 and the piston rod 5 off or retract.
  • a connection for the external power supply is not shown.
  • other types of working cylinders 1 possible, for example, synchronous cylinder with extendable on both sides of the piston rods.
  • releasable check valves 8 in known per se. These check valves 8 can be provided as separate components in the lines 6, 7, but also on the working cylinder 1 itself or integrated in the pressure supply unit described below.
  • the hydraulic pressure supply unit in the illustrated embodiment which can be advantageously used in such working units, has two alternately pressurized outlets, which are formed by the lines 6, 7, or connected to these lines 6, 7.
  • a reversible pump unit with at least two pumps 9, 10 and a common all reversible electric motor 11 driving all pumps 9, 10 is provided for the promotion and the pressure build-up in the hydraulic medium of the system.
  • the pressure supply unit can either be connected to an external supply for hydraulic medium or can be provided with a tank 12 integrated in the unit (shown twice in the figure in order to simplify the illustration), as a result of which the unit is as self-sufficient as possible.
  • one of the pumps 10 is designed as a low pressure pump and another pump 9 as a high pressure pump, the pressurized outputs of both pumps 9, 10 are placed on the same output 6 and 7 of the pressure supply unit. This adds up the flow rates of both pumps 9, 10 and there is a lot of hydraulic fluid in the working spaces 2 and 3 promoted, so that the piston 4 and piston rod 5 are rapidly retracted or extended with little load.
  • the high pressure pump 9 is separated from the low pressure pump 10 by 10 in the direction of the low pressure pump check valves 13.
  • Each pump 9, 10 is also connected via its own shuttle valve 14, 15 with the supply for hydraulic medium or the tank 12.
  • the two outputs of the low-pressure pump 10 are connected via a respective pressure switching valve 16, 17 to the tank 12, wherein the control terminals of the pressure switching valves 16, 17 are connected to the outputs of the high pressure pump 9 such that the control terminal of that pressure switching valve 16, 17 on the currently pressurized Side is also acted upon by the currently pressurized output of the high pressure pump 9.
  • This is due to the respective control terminal of the pressure switching valve 16, 17 of the respectively prevailing in the line 6 and 7 system pressure, which reflects the load conditions on the piston rod 5 of the working cylinder 1.
  • the pumps 9, 10 are preferably designed as constant pumps and the delivery volume of the low pressure pump 10 is greater than or equal to the delivery volume of the high pressure pump 9.
  • the terms high pressure pump 9 and low pressure pump 10 can be seen in the relative ratio of the pressures generated by the pumps 9, 10, the yes also influenced by the motor power of the drive 11 of the pump.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The unit supplying a mechanism with hydraulic pressure comprises two alternately pressurized outlets (6,7), a high pressure (9) and a low pressure pump (10) with a mutual reversible electric drive (11) and two complementary check valves (8). The outlets of the pumps (9,10) are separated by check valves (13) and each pump (9,10) is connected with a two-way valve (14,15) to a supply unit for a hydraulic fluid. Both outlets of the low pressure pump (10) can be connected to the tank (12) by pressure switch valves (16,17) which are connected to the outlets of the high pressure pump (9). An independent claim is given for a unit incorporating the arrangement.

Description

Die Erfindung betrifft eine hydraulische Druckversorgungseinheit, mit zwei abwechselnd druckbeaufschlagten Ausgängen, mit einer reversierbare Pumpeneinheit mit zumindest zwei Pumpen und einem alle Pumpen gemeinsam antreibenden reversierbaren Elektromotor, allenfalls mit gegenseitig entsperrenden Rückschlagventilen vor den Ausgängen, sowie einer Versorgung für Hydraulikmedium, wobei eine Pumpe als Niederdruckpumpe und eine Pumpe als Hochdruckpumpe ausgelegt ist, wobei die druckbeaufschlagten Ausgänge beider Pumpen an den gleichen Ausgang der Druckversorgungseinheit gelegt sind, weiters eine elektrohydraulische Arbeitseinheit, umfassend einen doppeltwirkenden hydraulischen Arbeitszylinder, eine elektrohydraulische Druckversorgungseinheit zur abwechselnden Druckbeaufschlagung jeweils eines Arbeitsraumes des Arbeitszylinders, sowie einen Anschluß für die externe Stromversorgung.The invention relates to a hydraulic pressure supply unit, with two alternately pressurized outputs, with a reversible pump unit with at least two pumps and all pumps together driving reversible electric motor, possibly with mutually unblocking check valves in front of the outputs, and a supply for hydraulic medium, wherein a pump as a low pressure pump and a pump is designed as a high-pressure pump, wherein the pressurized outputs of both pumps are connected to the same output of the pressure supply unit, further comprising an electro-hydraulic working unit comprising a double-acting hydraulic cylinder, an electro-hydraulic pressure supply unit for alternately pressurizing a respective working space of the working cylinder, and a connection for the external power supply.

Für vielerlei Anwendungen bei hydraulischen Systemen besteht die Anforderung, einen Verbraucher mit zwei Anschlüssen wechselweise an beiden Anschlüssen mit Hydraulikmedium zu versorgen. Beispielsweise ist als Verbraucher oftmals ein hydraulischer Arbeitszylinder vorgesehen, dessen beide Arbeitsräume wechselweise mit Druck beaufschlagt werden sollen. Diese wechselweise Druckbeaufschlagung kann einerseits über Umschaltventilanordnungen, aber auch in einfacherer Art über reversierbare Pumpenanordnungen erzielt werden. Derartige Systeme sind, beispielsweise aus der DE 197 16 081 C1 bekannt und werden vielfach eingesetzt.For many applications in hydraulic systems, there is a requirement to provide a consumer with two connections alternately at both ports with hydraulic medium. For example, a hydraulic working cylinder is often provided as a consumer whose two working spaces are to be alternately pressurized. This alternating pressurization can be achieved on the one hand via Umschaltventilanordnungen, but also in a simpler way on reversible pump assemblies. Such systems are, for example from the DE 197 16 081 C1 known and widely used.

Bei vielen Anwendungen hydraulischer Systeme ist gefordert, daß zu bestimmten Zeiten oder unter bestimmten Bedingungen der Druck unterschiedliche Niveaus annimmt, ein allenfalls angeschlossener Arbeitszylinder also unterschiedliche Kraft ausübt. Beispielsweise ist oftmals für den größten Teil des Arbeitshubes des Arbeitszylinders keine sehr große Kraft erforderlich, jedoch eine rasche Bewegung erwünscht. Sobald die Last zu wirken beginnt, muss der Arbeitszylinder dann mit hoher Kraft bewegt werden, wobei der Weg der Last oft nur einen geringen Teil des gesamten Arbeitshubes ausmacht. In der US 6 886 332 B2 ist ein System wie eingangs beschrieben geoffenbart, bei welchem jedoch nur eine Seite der Druckverborgungseinheit die gewünschte Funktionalität des zweistufigen Betriebs bietet. Die beiden Anschlüsse der Druckversorgungseinheit sind durch die Steuerleitung für das auf lediglich einer Seite der Pumpenanordnung vorgesehene, entsperrbare Rückschlagventil zwischen den beiden Pumpen nicht mehr unabhängig. Auch werden beide Pumpen über die gleiche Leitung aus dem Tank versorgt. Ein ähnliches System ist auch in der US 3 864 911 beschrieben.In many applications of hydraulic systems is required that at certain times or under certain conditions, the pressure assumes different levels, a possibly connected working cylinder thus exerts different force. For example, often for the largest part of the working stroke of the working cylinder, no very large force is required, but a rapid movement is desired. As soon as the load begins to act, the power cylinder must then be moved with high force, with the path of the load often only a small part of the total working stroke. In the US Pat. No. 6,886,332 B2 For example, a system as disclosed in the opening paragraph is disclosed, but in which only one side of the print supply unit provides the desired functionality of two-stage operation. The two connections of the pressure supply unit are no longer independent by the control line for the provided on only one side of the pump assembly, unlockable check valve between the two pumps. Also both pumps are supplied from the tank via the same line. A similar system is also in the US 3,864,911 described.

Die Aufgabe der vorliegenden Erfindung war daher eine Druckversorgungseinheit, mit welcher bis zum Erreichen eines vorgebbaren Druckniveaus eine große Menge an Hydraulikmedium zur Verfügung gestellt werden kann, während nach Erreichen dieses Druckniveaus Hydraulikmedium mit großem Druck zur Verfügung gestellt werden kann, wobei diese Funktion an zwei in einfacher Weise abwechselnd druckbeaufschlagten Ausgängen erfüllt ist. Eine weitere Aufgabe war dann eine hydraulische Arbeitseinheit, deren Arbeitszylinder einfach reversierbar in beide Richtungen zuerst rasch verfahren werden kann, wobei anschließend bei Erhöhung der Last, welche auch stationär anliegen kann, der Arbeitszylinder eine hohe Kraft ausübt.The object of the present invention was therefore a pressure supply unit with which a large amount of hydraulic medium can be made available until a predefinable pressure level is reached, while after reaching this pressure level hydraulic medium can be made available at high pressure, this function is fulfilled in two simple alternately pressurized outputs. Another task was then a hydraulic working unit, the working cylinder can be reversed easily reversible first in both directions, then subsequently increases the load, which may also be stationary, the working cylinder exerts a high force.

Zur Lösung der ersten Aufgabe ist die Druckversorgungseinheit dadurch gekennzeichnet, daß beide Ausgänge der Hochdruckpumpe von der Niederdruckpumpe durch Rückschlagventile getrennt sind und jede Pumpe über ein eigenes Wechselventil mit der Versorgung für Hydraulikmedium verbunden ist, und daß beide Ausgänge der Niederdruckpumpe über Druckschaltventile mit dem Tank verbindbar sind, wobei die Steueranschlüsse der Druckschaltventile mit den Ausgängen der Hochdruckpumpe derart verbunden sind, daß der Steueranschluß desjenigen Druckschaltventils auf der aktuell druckbeaufschlagten Seite vom aktuell druckbeaufschlagten Ausgang der Hochdruckpumpe beaufschlagt wird. Mit dieser Schaltung stellt die Druckversorgungseinheit für beide Ausgänge der Anordnung solange die Fördermenge beider Pumpen an Hydraulikmedium zur Verfügung, bis im System das vorzugsweise einstellbare Druckniveau erreicht ist, bei welchem das Druckschaltventil anspricht. Dann wird die Niederdruckpumpe durch dieses Ventil weggeschaltet und der Verbraucher dann nur noch mit dem Fördervolumen der Hochdruckpumpe versorgt. In einfacher Art und Weise kann unter Vermeidung von Umschaltventilen diese Funktionalität durch einfaches Reversieren der Drehrichtung der Pumpen an beiden Ausgängen der Druckversorgungseinheit erzielt werden, wobei die Rückschlagventile zwischen den verschiedenen Druckstufen der Druckversorgungseinheit auf beiden Seiten der Pumpen unabhängig von der jeweiligen anderen Seite arbeiten. Dadurch ist größtmögliche Unabhängigkeit und damit Flexibilität für die Auslegung der Druckversorgungseinheit auf beiden Seiten gewährleistet. Auch kann der für den Antrieb der Pumpen verwendete Elektromotor gerade für den gewünschten höchsten Systemdruck, d.h. für die Hochdruckpumpe, ausgelegt werden, da auf geringeren Druckniveaus selbst bei Betrieb beider Pumpen parallel mit dem gleichen Motor das Auslangen gefunden werden kann.To achieve the first object, the pressure supply unit is characterized in that both outputs of the high pressure pump from the low pressure pump are separated by check valves and each pump is connected via its own shuttle valve with the supply of hydraulic fluid, and that both outputs of the low pressure pump via pressure switching valves connected to the tank are, wherein the control terminals of the pressure switching valves are connected to the outputs of the high pressure pump such that the control terminal of that Druckschaltventils is acted upon on the currently pressurized side of the currently pressurized output of the high pressure pump. With this circuit, the pressure supply unit for both outputs of the arrangement as long as the flow of both pumps to hydraulic medium available until the preferably adjustable pressure level is reached in the system, in which the pressure switching valve responds. Then the low-pressure pump is switched off by this valve and the consumer then only supplied with the delivery volume of the high-pressure pump. In a simple way, while avoiding switching valves, this functionality can be achieved by simply reversing the direction of rotation of the pumps at both outputs of the pressure supply unit, the check valves operating between the different pressure stages of the pressure supply unit on both sides of the pumps independently of the other side. This ensures the greatest possible independence and thus flexibility for the design of the pressure supply unit on both sides. Also, the electric motor used to drive the pumps can be just for the desired highest system pressure, i. be designed for the high-pressure pump, since at lower pressure levels even when operating both pumps in parallel with the same engine Auslangen can be found.

Gemäß einer vorteilhaften Ausführungsform der Erfindung ist vorgesehen, daß zumindest eines, vorzugsweise beide, der Druckschaltventile einen unabhängig vom anderen Druckschaltventil einstellbaren Schaltpunkt aufweist. Damit können an beiden Ausgängen unterschiedliche Charakteristika eingestellt werden.According to an advantageous embodiment of the invention, it is provided that at least one, preferably both, of the pressure switching valves has an independently adjustable from the other pressure switching valve switching point. This allows different characteristics to be set on both outputs.

Vorzugsweise sind die Pumpen als Konstantpumpen ausgeführt, was das System in Bezug auf Fertigung als auch Betrieb wesentlich vereinfacht.Preferably, the pumps are designed as constant pumps, which greatly simplifies the system in terms of manufacturing as well as operation.

Um eine möglichst autarke Einheit zu erhalten, kann gemäß einem weiteren Merkmal der Erfindung vorgesehen sein, daß ein Tank für das Hydraulikmedium in die Druckversorgungseinheit integriert und jede Pumpe mit einem eigenen Wechselventil zur Druck-Tank-Umschaltung verbunden ist.In order to obtain a self-sufficient unit, it can be provided according to a further feature of the invention that a tank for the hydraulic medium in the pressure supply unit integrated and each pump is connected to its own shuttle valve for pressure tank switching.

Zur Lösung der zweiten Aufgabe ist eine elektrohydraulische Arbeitseinheit, mit einem doppeltwirkenden hydraulischen Arbeitszylinder, dessen Arbeitsräume abwechselnd mit Druck beaufschlagt werden, dadurch gekennzeichnet, daß die Druckversorgungseinheit gemäß einem der vorhergehenden Absätze ausgebildet und jeder Arbeitsraum des Arbeitszylinders mit immer dem gleichen Ausgang der Druckversorgungseinheit verbunden ist. Damit kann bei einfacher Ansteuerung ohne komplizierte Umschaltventilanordnung und kompakter Ausführung für den Arbeitszylinder ein schneller Eilgang durch vorerst Versorgung mit Hydraulikmedium durch beiden Pumpen gemeinsam und anschließend ein hohes Kraftniveau erzielt werden, wenn durch die Erhöhung der Last am Arbeitszylinder das Druckniveau soweit ansteigt, daß die Niederdruckpumpe weggeschaltet wird. Die Fördermenge wird dann auf die durch die Hochdruckpumpe zur Verfügung gestellte Menge reduziert.To achieve the second object is an electro-hydraulic working unit, with a double-acting hydraulic cylinder whose working spaces are alternately pressurized, characterized in that the pressure supply unit formed according to one of the preceding paragraphs and each working space of the working cylinder is always connected to the same output of the pressure supply unit , This can be achieved with simple control without complicated Umschaltventilanordnung and compact design for the working cylinder fast rapid by initially supply of hydraulic medium by both pumps together and then a high level of force, if by increasing the load on the working cylinder, the pressure level rises so much that the low pressure pump is switched off. The flow rate is then reduced to the amount provided by the high pressure pump.

Gemäß einer speziellen Ausführungsform der Erfindung ist vorgesehen, daß der Arbeitszylinder als Differentialzylinder ausgeführt ist. Dabei kann, um die gleichen Charakteristika bezüglich Hubgeschwindigkeit und Kraftniveaus in beiden Bewegungsrichtungen des Arbeitszylinders zu erzielen, eine entsprechend gegengleiche Einstellung der Schaltpunkte der Druckschaltventile vorteilhaft sein.According to a particular embodiment of the invention it is provided that the working cylinder is designed as a differential cylinder. In this case, in order to achieve the same characteristics with respect to stroke speed and force levels in both directions of movement of the working cylinder, a correspondingly opposite adjustment of the switching points of the pressure switching valves may be advantageous.

Eine weitere erfindungsgemäße Ausführungsform sieht vor, daß der Arbeitszylinder als Gleichgangzylinder mit auf beiden Seiten ausfahrbaren Kolbenstangen ausgebildet ist. In diesem Fall kann in einfacher Art und Weise das System vollkommen symmetrisch ausgeführt sein. Andererseits kann natürlich bei beiden Arten von Arbeitszylindern eine unterschiedliche Kraft/Weg-Charakteristik in den unterschiedlichen Bewegungsrichtungen auch aufgrund unterschiedlicher Anforderungen, beispielsweise hohe Kraftausübung nur in einer Richtung erforderlich, vorgesehen sein.Another embodiment of the invention provides that the working cylinder is designed as a synchronous cylinder with extendible on both sides piston rods. In this case, in a simple way, the system can be made completely symmetrical. On the other hand, of course, in both types of working cylinders, a different force / displacement characteristic in the different directions of movement also due to different requirements, for example, high power only required in one direction, be provided.

Um die sichere Haltewirkung durch den Arbeitszylinder bei Ausfall oder Stillstand der Druckversorgungseinrichtung und andererseits den ungehinderten Arbeitshub sicherzustellen, sind gemäß einer weiteren Ausführungsform der Erfindung in den Verbindungsleitungen zwischen der Pumpeneinheit der Druckversorgungseinheit und den Arbeitsräumen des Arbeitszylinders durch den Druck in der jeweils anderen Leitung entsperrbare Rückschlagventile vorgesehen.In order to ensure the secure holding action by the working cylinder in case of failure or stoppage of the pressure supply device and on the other hand, the unimpeded power stroke, according to a further embodiment of the invention in the connecting lines between the pump unit of the pressure supply unit and the working chambers of the working cylinder by the pressure in the respective other line unlockable check valves intended.

In der nachfolgenden Beschreibung soll die Erfindung anhand eines unter Bezugnahme auf die beigefügten Zeichnungen dargestellten Ausführungsbeispieles näher erläutert werden.In the following description, the invention will be explained in more detail with reference to an embodiment illustrated with reference to the accompanying drawings.

Die Zeichnungsfigur zeigt den hydraulischen Schaltplan einer erfindungsgemäßen elektrohydraulischen Arbeitseinheit, wie sie für verschiedenste Anwendungen zum Einsatz kommen kann.The drawing figure shows the hydraulic circuit diagram of an electro-hydraulic working unit according to the invention, as it can be used for a wide variety of applications.

Wie in der Zeichnungsfigur zu ersehen ist, besteht die elektrohydraulische Arbeitseinheit aus zumindest einem Arbeitszylinder 1, dessen beide Arbeitsräume 2, 3, wechselweise mit Hydraulikmedium beaufschlagt werden und derart den Kolben 4 und die Kolbenstange 5 aus- bzw. einfahren. Nicht dargestellt ist ein Anschluß für die externe Stromversorgung. Natürlich sind, neben der Ausführung des Arbeitszylinders 1 als Differentialzylinder, auch andere Arten von Arbeitszylindern 1 möglich, beispielsweise Gleichgangzylinder mit auf beiden Seiten ausfahrbaren Kolbenstangen. Vorteilhafterweise sind in den Verbindungsleitungen 6, 7 zu den Arbeitsräumen 2, 3 des Arbeitszylinders 1 durch den Druck in der jeweils anderen Leitung 7 bzw. 6 entsperrbare Rückschlagventile 8 in an sich bekannter Ausführung vorgesehen. Diese Rückschlagventile 8 können als separate Bauteile in den Leitungen 6, 7, aber auch am Arbeitszylinder 1 selbst oder auch integriert in der nachfolgend beschriebenen Druckversorgungseinheit vorgesehen sein.As can be seen in the drawing figure, the electro-hydraulic working unit consists of at least one working cylinder 1, the two working chambers 2, 3, alternately acted upon by hydraulic medium and in such a way the piston 4 and the piston rod 5 off or retract. Not shown is a connection for the external power supply. Of course, in addition to the execution of the working cylinder 1 as a differential cylinder, other types of working cylinders 1 possible, for example, synchronous cylinder with extendable on both sides of the piston rods. Advantageously, in the connecting lines 6, 7 to the working spaces 2, 3 of the working cylinder 1 by the pressure in the respective other line 7 and 6 are provided releasable check valves 8 in known per se. These check valves 8 can be provided as separate components in the lines 6, 7, but also on the working cylinder 1 itself or integrated in the pressure supply unit described below.

Die hydraulische Druckversorgungseinheit in der dargestellten Ausführungsform, die vorteilhafterweise in derartigen Arbeitseinheiten verwendet werden kann, weist zwei abwechselnd druckbeaufschlagte Ausgänge auf, die durch die Leitungen 6, 7, gebildet oder mit diesen Leitungen 6, 7 verbunden sind. Eine reversierbare Pumpeneinheit mit zumindest zwei Pumpen 9, 10 und einem alle Pumpen 9, 10 gemeinsam antreibenden reversierbaren Elektromotor 11 ist für die Förderung und den Druckaufbau im Hydraulikmedium des Systems vorgesehen. Die Druckversorgungseinheit kann entweder an eine externe Versorgung für Hydraulikmedium angeschlossen sein oder mit einem in die Einheit integrierten Tank 12 (in der Zeichnungsfigur doppelt dargestellt, um die Darstellung zu vereinfachen) versehen sein, wodurch die Einheit bestmöglich autark betreibbar ist.The hydraulic pressure supply unit in the illustrated embodiment, which can be advantageously used in such working units, has two alternately pressurized outlets, which are formed by the lines 6, 7, or connected to these lines 6, 7. A reversible pump unit with at least two pumps 9, 10 and a common all reversible electric motor 11 driving all pumps 9, 10 is provided for the promotion and the pressure build-up in the hydraulic medium of the system. The pressure supply unit can either be connected to an external supply for hydraulic medium or can be provided with a tank 12 integrated in the unit (shown twice in the figure in order to simplify the illustration), as a result of which the unit is as self-sufficient as possible.

Damit nun bis zum Erreichen eines vorgebbaren Druckniveaus im System und damit einer vorgebbaren Kraft des Arbeitszylinders 1 eine große Menge an Hydraulikmedium zur Verfügung gestellt werden kann, womit ein Eilgang für den Arbeitszylinder 1 erzielt wird, während nach Erreichen dieses Druckniveaus Hydraulikmedium mit großem Druck zur Verfügung gestellt werden kann, ist eine der Pumpen 10 als Niederdruckpumpe und eine andere Pumpe 9 als Hochdruckpumpe ausgelegt, wobei die druckbeaufschlagten Ausgänge beider Pumpen 9, 10 an den gleichen Ausgang 6 bzw. 7 der Druckversorgungseinheit gelegt sind. Damit addieren sich die Fördermengen beider Pumpen 9, 10 und es wird viel Hydraulikmedium in die Arbeitsräume 2 bzw. 3 gefördert, so daß Kolben 4 und Kolbenstange 5 bei wenig Last rasch ein- oder ausgefahren werden.In order that a large amount of hydraulic medium can now be provided until reaching a predefinable pressure level in the system and thus a predeterminable force of the working cylinder 1, whereby a rapid traverse for the working cylinder 1 is achieved, while after reaching this pressure level hydraulic medium with high pressure available can be made, one of the pumps 10 is designed as a low pressure pump and another pump 9 as a high pressure pump, the pressurized outputs of both pumps 9, 10 are placed on the same output 6 and 7 of the pressure supply unit. This adds up the flow rates of both pumps 9, 10 and there is a lot of hydraulic fluid in the working spaces 2 and 3 promoted, so that the piston 4 and piston rod 5 are rapidly retracted or extended with little load.

Die Hochdruckpumpe 9 ist von der Niederdruckpumpe 10 durch in Richtung der Niederdruckpumpe 10 sperrende Rückschlagventile 13 getrennt. Jede Pumpe 9, 10 ist auch über ein eigenes Wechselventil 14, 15 mit der Versorgung für Hydraulikmedium bzw. dem Tank 12 verbunden.The high pressure pump 9 is separated from the low pressure pump 10 by 10 in the direction of the low pressure pump check valves 13. Each pump 9, 10 is also connected via its own shuttle valve 14, 15 with the supply for hydraulic medium or the tank 12.

Die beiden Ausgänge der Niederdruckpumpe 10 sind über jeweils ein Druckschaltventil 16, 17 mit dem Tank 12 verbindbar, wobei die Steueranschlüsse der Druckschaltventile 16, 17 mit den Ausgängen der Hochdruckpumpe 9 derart verbunden sind, daß der Steueranschluß desjenigen Druckschaltventils 16, 17 auf der aktuell druckbeaufschlagten Seite auch vom aktuell druckbeaufschlagten Ausgang der Hochdruckpumpe 9 beaufschlagt wird. Damit liegt am jeweiligen Steueranschluß des Druckschaltventils 16, 17 der jeweils in der Leitung 6 bzw. 7 herrschende Systemdruck an, der die Lastverhältnisse an der Kolbenstange 5 des Arbeitszylinders 1 widerspiegelt.The two outputs of the low-pressure pump 10 are connected via a respective pressure switching valve 16, 17 to the tank 12, wherein the control terminals of the pressure switching valves 16, 17 are connected to the outputs of the high pressure pump 9 such that the control terminal of that pressure switching valve 16, 17 on the currently pressurized Side is also acted upon by the currently pressurized output of the high pressure pump 9. This is due to the respective control terminal of the pressure switching valve 16, 17 of the respectively prevailing in the line 6 and 7 system pressure, which reflects the load conditions on the piston rod 5 of the working cylinder 1.

Sobald beispielsweise die Last beim Ausfahren der Kolbenstange größer wird bremst diese den Hub des Arbeitszylinders 1 und der Druck in der den Arbeitsraum 2 beaufschlagenden Leitung 6 wächst solange an, bis der Schaltpunkt des Druckschaltventils 16 erreicht ist und dieses die Verbindung zwischen Niederdruckpumpe 10 und Tank 12 freigibt. Durch das Rückschlagventil 13 kann das von der Hochdruckpumpe 9 geförderte Hydraulikmedium nicht in den Tank 12 abströmen, sondern wird weiter zum Arbeitsraum 2 gefördert, in dem sich nun der höhere Druck einstellt, so daß der Arbeitszylinder 1 die Last mit hoher Kraft beaufschlagt.As soon as, for example, the load on extension of the piston rod becomes larger, it slows down the stroke of the working cylinder 1 and the pressure in the working space 2 acts on line 6 increases until the switching point of the pressure switching valve 16 is reached and this the connection between the low pressure pump 10 and tank 12th releases. By the check valve 13, the funded by the high pressure pump 9 hydraulic medium can not flow into the tank 12, but is further promoted to the working space 2, in which now sets the higher pressure, so that the working cylinder 1, the load applied with high force.

Um unsymmetrische Geschwindigkeits- und/oder Lastverhältnisse am Arbeitszylinder 1 berücksichtigen zu können, oder auch um die Unterschiede von Differentialzylindern ausgleichen zu können, weist vorzugsweise zumindest eines der Druckschaltventile 16, 17 einen unabhängig vom anderen Druckschaltventil 17, 16 einstellbaren Schaltpunkt auf.In order to take unbalanced speed and / or load conditions on the cylinder 1, or to compensate for the differences of differential cylinders, preferably at least one of the pressure switching valves 16, 17 a independently of the other pressure switching valve 17, 16 adjustable switching point on.

Die Pumpen 9, 10 sind vorzugsweise als Konstantpumpen ausgeführt und das Fördervolumen der Niederdruckpumpe 10 ist größer oder gleich dem Fördervolumen der Hochdruckpumpe 9. Die Begriffe Hochdruckpumpe 9 und Niederdruckpumpe 10 sind im relativen Verhältnis der von den Pumpen 9, 10 erzeugbaren Drücke zu sehen, das ja auch durch die Motorleistung des Antriebs 11 der Pumpen beeinflusst ist.The pumps 9, 10 are preferably designed as constant pumps and the delivery volume of the low pressure pump 10 is greater than or equal to the delivery volume of the high pressure pump 9. The terms high pressure pump 9 and low pressure pump 10 can be seen in the relative ratio of the pressures generated by the pumps 9, 10, the yes also influenced by the motor power of the drive 11 of the pump.

Claims (8)

Hydraulische Druckversorgungseinheit, mit zwei abwechselnd druckbeaufschlagten Ausgängen (6, 7), mit einer reversierbare Pumpeneinheit mit zumindest zwei Pumpen (9 10) und einem alle Pumpen gemeinsam antreibenden reversierbaren Elektromotor (11), allenfalls mit gegenseitig entsperrenden Rückschlagventilen (8) vor den Ausgängen, sowie einer Versorgung für Hydraulikmedium, wobei eine Pumpe als Niederdruckpumpe (10) und eine Pumpe als Hochdruckpumpe (9) ausgelegt ist, wobei die druckbeaufschlagten Ausgänge beider Pumpen an den gleichen Ausgang (6, 7) der Druckversorgungseinheit gelegt sind, dadurch gekennzeichnet, daß beide Ausgänge der Hochdruckpumpe (9) von der Niederdruckpumpe (10) durch Rückschlagventile (10, 13) getrennt sind und jede Pumpe (9, 10) über ein eigenes Wechselventil (14, 15) mit der Versorgung für Hydraulikmedium verbunden ist, und daß beide Ausgänge der Niederdruckpumpe (10) über Druckschaltventile (16, 17) mit dem Tank (12) verbindbar sind, wobei die Steueranschlüsse der Druckschaltventile (16, 17) mit den Ausgängen der Hochdruckpumpe (9) derart verbunden sind, daß der Steueranschluß desjenigen Druckschaltventils (16, 17) auf der aktuell druckbeaufschlagten Seite vom aktuell druckbeaufschlagten Ausgang der Hochdruckpumpe (9) beaufschlagt wird.Hydraulic pressure supply unit, with two alternately pressurized outputs (6, 7), with a reversible pump unit with at least two pumps (9 10) and a reversible electric motor (11) driving all the pumps together, possibly with mutually unlocking non-return valves (8) in front of the outputs, and a supply for hydraulic medium, wherein a pump is designed as a low pressure pump (10) and a pump as a high pressure pump (9), wherein the pressurized outputs of both pumps at the same output (6, 7) of the pressure supply unit are laid, characterized in that both Outputs of the high pressure pump (9) from the low pressure pump (10) by check valves (10, 13) are separated and each pump (9, 10) via its own shuttle valve (14, 15) is connected to the supply for hydraulic medium, and that both outputs the low-pressure pump (10) via pressure switching valves (16, 17) with the tank (12) are connectable, wherein the Steue Connections of the pressure switching valves (16, 17) are connected to the outputs of the high-pressure pump (9), that the control terminal of that pressure switching valve (16, 17) is acted upon on the currently pressurized side of the currently pressurized output of the high-pressure pump (9). Druckversorgungseinheit nach Anspruch 1, dadurch gekennzeichnet, daß zumindest eines, vorzugsweise beide, der Druckschaltventile (16, 17) einen unabhängig vom anderen Druckschaltventil einstellbaren Schaltpunkt aufweist.Pressure supply unit according to claim 1, characterized in that at least one, preferably both, of the pressure switching valves (16, 17) has an independently adjustable from the other pressure switching valve switching point. Druckversorgungseinheit nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, daß die Pumpen (9, 10) als Konstantpumpen ausgeführt sind.Pressure supply unit according to one of claims 1 or 2, characterized in that the pumps (9, 10) are designed as constant pumps. Druckversorgungseinheit nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß ein Tank (12) für das Hydraulikmedium in die Druckversorgungseinheit integriert und jede Pumpe (9, 10) mit einem eigenen Wechselventil (14, 15) zur Druck-Tank-Umschaltung verbunden ist.Pressure supply unit according to one of Claims 1 to 3, characterized in that a tank (12) for the hydraulic medium is integrated in the pressure supply unit and each pump (9, 10) is connected to its own change-over valve (14, 15) for pressure-tank changeover , Elektrohydraulische Arbeitseinheit, umfassend einen doppeltwirkenden hydraulischen Arbeitszylinder (1), eine elektrohydraulische Druckversorgungseinheit zur abwechselnden Druckbeaufschlagung jeweils eines Arbeitsraumes (2, 3) des Arbeitszylinders, sowie einen Anschluß für die externe Stromversorgung, dadurch gekennzeichnet, daß die Druckversorgungseinheit gemäß einem der Ansprüche 1 bis 4 ausgebildet und jeder Arbeitsraum (2, 3) des Arbeitszylinders (1) mit immer dem gleichen Ausgang (6, 7) der Druckversorgungseinheit verbunden ist.Electrohydraulic working unit comprising a double-acting hydraulic working cylinder (1), an electrohydraulic pressure supply unit for alternately pressurizing a working space (2, 3) of the working cylinder, and a connection for the external power supply, characterized in that the pressure supply unit according to one of claims 1 to 4 educated and everyone Working space (2, 3) of the working cylinder (1) with always the same output (6, 7) of the pressure supply unit is connected. Arbeitseinheit nach Anspruch 5, dadurch gekennzeichnet, daß der Arbeitszylinder (1) als Differentialzylinder ausgeführt ist.Working unit according to claim 5, characterized in that the working cylinder (1) is designed as a differential cylinder. Arbeitseinheit nach Anspruch 5, dadurch gekennzeichnet, daß der Arbeitszylinder (1) als Gleichgangzylinder mit auf beiden Seiten ausfahrbaren Kolbenstangen (5) ausgebildet ist.Working unit according to claim 5, characterized in that the working cylinder (1) is designed as a synchronous cylinder with extendible piston rods (5) on both sides. Arbeitseinheit nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, daß in den Verbindungsleitungen (6, 7) zwischen der Pumpeneinheit (9, 10) der Druckversorgungseinheit und den Arbeitsräumen (2, 3) des Arbeitszylinders (1) durch den Druck in der jeweils anderen Leitung entsperrbare Rückschlagventile (8) vorgesehen sind.Work unit according to one of claims 5 to 7, characterized in that in the connecting lines (6, 7) between the pump unit (9, 10) of the pressure supply unit and the working spaces (2, 3) of the working cylinder (1) by the pressure in the respective other line check valves (8) are provided.
EP06122576A 2005-10-28 2006-10-19 Hydraulic pressure supply unit and electro-hydraulic work unit Ceased EP1780420B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT0074205U AT8986U1 (en) 2005-10-28 2005-10-28 HYDRAULIC PRESSURE SUPPLY UNIT, AND ELECTRO-HYDRAULIC WORKING UNIT AND CLAMPING SYSTEM WITH SUCH A PRESSURE SUPPLY UNIT

Publications (3)

Publication Number Publication Date
EP1780420A2 true EP1780420A2 (en) 2007-05-02
EP1780420A3 EP1780420A3 (en) 2008-04-02
EP1780420B1 EP1780420B1 (en) 2009-10-14

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EP06122576A Ceased EP1780420B1 (en) 2005-10-28 2006-10-19 Hydraulic pressure supply unit and electro-hydraulic work unit

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US (1) US7493757B2 (en)
EP (1) EP1780420B1 (en)
KR (1) KR101311009B1 (en)
CN (1) CN1971068B (en)
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DE (1) DE502006005089D1 (en)

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CN1971068B (en) 2010-07-21
US7493757B2 (en) 2009-02-24
CN1971068A (en) 2007-05-30
AT8986U1 (en) 2007-03-15
DE502006005089D1 (en) 2009-11-26
US20070095060A1 (en) 2007-05-03
EP1780420B1 (en) 2009-10-14
EP1780420A3 (en) 2008-04-02
KR20070046015A (en) 2007-05-02
KR101311009B1 (en) 2013-09-24

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