EP2480405B1 - Prestressed hydraulic drive with variable-speed pump - Google Patents

Prestressed hydraulic drive with variable-speed pump Download PDF

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Publication number
EP2480405B1
EP2480405B1 EP10740535.9A EP10740535A EP2480405B1 EP 2480405 B1 EP2480405 B1 EP 2480405B1 EP 10740535 A EP10740535 A EP 10740535A EP 2480405 B1 EP2480405 B1 EP 2480405B1
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EP
European Patent Office
Prior art keywords
hydraulic
cylinder
piston
master
hydraulic machine
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EP10740535.9A
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German (de)
French (fr)
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EP2480405A1 (en
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Stefan Schmidt
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Robert Bosch GmbH
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Robert Bosch GmbH
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Classifications

    • 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
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/161—Control arrangements for fluid-driven presses controlling the ram speed and ram pressure, e.g. fast approach speed at low pressure, low pressing speed at high 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
    • F15B2211/205—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
    • F15B2211/20561—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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • 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
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7107—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being mechanically linked
    • 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
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7114—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators
    • 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
    • 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
    • F15B2211/78—Control of multiple output members
    • F15B2211/782—Concurrent control, e.g. synchronisation of two or more actuators
    • 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
    • F15B2211/785—Compensation of the difference in flow rate in closed fluid circuits using differential actuators

Description

Die vorliegende Erfindung betrifft im Allgemeinen einen hydraulischen Antrieb vorzugsweise für eine Presse, Kunststoffmaschine, Biegemaschine etc. gemäß dem Oberbegriff des Patentanspruchs 1.The present invention generally relates to a hydraulic drive preferably for a press, plastic machine, bending machine, etc. according to the preamble of claim 1.

Derartige Antriebe sind dafür ausgelegt, zumindest zwei Bewegungsabläufe, nämlich eine schnelle Überführungsbewegung (nachfolgend als "Eilgang" bezeichnet) sowie eine kraftaufbringende Arbeitsbewegung (nachfolgend als "Pressgang" bezeichnet) zu realisieren.Such drives are designed to realize at least two motion sequences, namely a fast transfer movement (hereinafter referred to as "rapid traverse") and a force-applying working movement (hereinafter referred to as "press gear").

Aus dem Stand der Technik beispielsweise gemäß der EP 0 785 861 B1 ist ein gattungsgemäßer hydraulischer Antrieb für eine Presse bekannt. Dieser Antrieb besteht aus einer angetriebenen hydrostatischen Maschine, die einen vorbestimmten konstanten Druck in einem primären Druckleitungssystem erzeugt und aus einem hydraulischen Transformator bestehend aus einem Hydraulikmotor und einer mechanisch daran angeschlossenen Hydraulikpumpe. Der vorzugsweise verstellbare Hydraulikmotor ist an das primäre Druckleitungssystem angeschlossen und wird somit von der hydrostatischen Maschine angetrieben. Die ebenfalls verstellbare Hydraulikpumpe beaufschlagt ein sekundäres Druckleitungssystem mit einem Hydraulikdruck, in das ein Presszylinder eingesetzt ist, dessen Zylinderräume über Ventile an die beiden hydraulischen Anschlüsse der Hydraulikpumpe angeschlossen sind.From the prior art, for example, according to the EP 0 785 861 B1 is a generic hydraulic drive for a press known. This drive consists of a driven hydrostatic machine that generates a predetermined constant pressure in a primary pressure line system and a hydraulic transformer consisting of a hydraulic motor and a hydraulic pump connected to it mechanically. The preferably adjustable hydraulic motor is connected to the primary pressure line system and is thus driven by the hydrostatic machine. The also adjustable hydraulic pump acts on a secondary pressure line system with a hydraulic pressure, in which a pressing cylinder is used, the cylinder chambers are connected via valves to the two hydraulic connections of the hydraulic pump.

Ein solches System ist auch aus JP 2006 316 800 bekannt.Such a system is also off JP 2006 316 800 known.

Schließlich sind die beiden Zylinderräume des Presszylinders über eine Druckleitung mit dem primären Druckleitungssystem verbunden, um den Presskolben mit dem Primärdruck (entspricht dem erforderlichen Vorspanndruck für den Presszylinder) vorzuspannen.Finally, the two cylinder chambers of the press cylinder are connected via a pressure line to the primary pressure line system to bias the plunger to the primary pressure (corresponding to the required bias pressure for the press cylinder).

Es hat sich jedoch als technisch schwierig erwiesen, die Idee der Anordnung eines hydraulischen Transformators mit vorstehend beschriebenem Aufbau in die Praxis umzusetzen. Der konstruktive Aufwand sowie die Anzahl der erforderlichen hydraulischen Bauteile und deren Abstimmung aufeinander verringert nämlich die Wirtschaftlichkeit dieses bekannten hydraulischen Antriebs derart, dass es in der Fachwelt keine größere Akzeptanz gefunden hat.However, it has proved to be technically difficult to put into practice the idea of arranging a hydraulic transformer having the structure described above. The design effort and the number of required hydraulic components and their coordination successive reduces namely the economy of this known hydraulic drive such that it has not found greater acceptance in the art.

Angesichts dieses Stands der Technik besteht die Aufgabe der vorliegenden Erfindung darin, einen gattungsgemäßen hydraulischen Antrieb bereit zu stellen, der mit einer verminderten Anzahl hydraulischer Bauteile auskommt und trotzdem im Betrieb durch einen niedrigen Energieverbrauch gekennzeichnet ist.In view of this state of the art, the object of the present invention is to provide a generic hydraulic drive, which manages with a reduced number of hydraulic components and is nevertheless characterized in operation by a low energy consumption.

Diese Aufgabe wird durch einen hydraulischen Antrieb mit den Merkmalen des Patentanspruchs 1 gelöst. Weitere vorteilhafte Ausgestaltungen der Erfindung sind Gegenstand der Unteransprüche.This object is achieved by a hydraulic drive having the features of patent claim 1. Further advantageous embodiments of the invention are the subject of the dependent claims.

Die Erfindung betrifft demzufolge einen hydraulischen Antrieb mit einer von einem elektrischen Antriebsmotor drehzahlvariabel angesteuerten Hydromaschine, einem Hauptzylinder zur Durchführung eines kraftaufbauenden Bewegungsablaufs sowie einem Nebenzylinder zur Durchführung eines schnellen Bewegungsablaufs. Erfindungsgemäß ist der Hauptzylinder durch einen, vorzugsweise auf beide Kolbenflächen einwirkenden, weiter vorzugsweise von einer externen Druckquelle erzeugten vorbestimmten Permanentdruck vor- oder eingespannt, wobei die Hydromaschine durch ausgewähltes Umfördern von Druckmittel in einem geschlossenen Kreis, in den die Hydromaschine zwischengeschaltet ist, eine Hubbewegung des Hauptzylinders und des Nebenzylinders nach einem der zwei Bewegungsabläufe bewirkt.The invention accordingly relates to a hydraulic drive with a variable speed controlled by an electric drive motor hydraulic machine, a master cylinder for performing a force-building movement sequence and a slave cylinder to perform a fast movement. According to the invention, the master cylinder is pre-clamped or clamped by a predetermined permanent pressure, preferably acting on both piston surfaces, preferably generated by an external pressure source, wherein the hydraulic machine by selectively circulating pressure medium in a closed circuit, in which the hydraulic machine is interposed Stroke movement of the master cylinder and the slave cylinder after one of the two movements causes.

Durch das Vorspannen des Antriebs vorzugsweise mittels der auch für die Bewegungsabläufe verantwortlichen Hydromaschine oder durch die externe Druckquelle verringert sich erheblich die zu fördernden Kompressionsvolumen, wobei die Kombination von Vorspannung des Antriebs und der servoelektrisch betriebenen drehzahlvariablen Pumpe (Hydomaschine) als Vorspannmittel und als hydraulsiches Antriebsmittel für die beiden Zylinder eine wirtschaftliche Realisierung eines energiesparenden Hydraulikantriebs mit kurzen Taktzeiten darstellt.By biasing the drive preferably by means of responsible for the motion hydraulic machine or by the external pressure source significantly reduces the volume of compression to be funded, the combination of bias of the drive and the servo-electric variable-speed pump (hydraulic machine) as a biasing means and as hydraulsiches drive means for the two cylinders represent an economical realization of an energy-saving hydraulic drive with short cycle times.

Die Erfindung wird nachstehend anhand eines bevorzugten Ausführungsbeispiels unter Bezugnahme auf die begleitenden Zeichnungen näher erläutert.The invention will be explained below with reference to a preferred embodiment with reference to the accompanying drawings.

Es zeigen:

  • Fig. 1 das Prinzipschaltbild eines hydraulischen Antriebs gemäß einem bevorzugten Ausführungsbeispiel der Erfindung im Stillstand (unter Vorspannung),
  • Fig. 2 das Prinzipschaltbild des hydraulischen Antriebs gemäß Fig. 1 im "Eilgang" abwärts,
  • Fig. 3 das Prinzipschaltbild des hydraulischen Antriebs gemäß Fig. 1 im "Pressgang",
  • Fig. 4 das Prinzipschaltbild des hydraulischen Antriebs gemäß Fig. 1 in einer Re-Kompressionsphase und
  • Fig. 5 das Prinzipschaltbild des hydraulischen Antriebs gemäß Fig. 1 im "Eilgang" aufwärts (Rückzugsphase).
Show it:
  • Fig. 1 the block diagram of a hydraulic drive according to a preferred embodiment of the invention at a standstill (under bias),
  • Fig. 2 the block diagram of the hydraulic drive according to Fig. 1 in "rapid" down,
  • Fig. 3 the block diagram of the hydraulic drive according to Fig. 1 in the "Pressgang",
  • Fig. 4 the block diagram of the hydraulic drive according to Fig. 1 in a re-compression phase and
  • Fig. 5 the block diagram of the hydraulic drive according to Fig. 1 in "rapid" upwards (withdrawal phase).

Wie aus sämtlichen Figuren zu entnehmen ist, hat der erfindungsgemäße hydraulische Antrieb eine Druckmittelquelle in Form einer drehzahlvariabel angetriebenen Hydromaschine 1 als Pumpe, die hierfür an einen Elektromotor 2 mechanisch angeschlossen ist. Die Hydromaschine 1 ist an ihren zwei Druckanschlüssen an ein hydraulisches Druckleitungssystem angeschlossen, welches einen geschlossenen Hydraulikdruckkreis bildet.As can be seen from all the figures, the inventive hydraulic drive a pressure medium source in the form of a variable speed driven hydraulic machine 1 as a pump, which is mechanically connected thereto for an electric motor 2. The hydraulic machine 1 is connected at its two pressure ports to a hydraulic pressure line system which forms a closed hydraulic pressure circuit.

Im Konkreten ist an einen ersten Druckanschluss der Hydromaschine 1 eine erste Verbindungsleitung 3 angeschlossen, die direkt zu einer kolbenseitigen Druckkammer 4a eines Hauptzylinders 4 führt. An den zweiten Druckanschluss der Hydromaschine 1 ist eine zweite Leitung 5 angeschlossen, die über ein Ventil 6 mit einer kolbenstangenseitigen Druckkammer 4b des Hauptzylinders 4 (nachfolgend als Ringkammer 4b bezeichnet) verbunden ist. Das Ventil 6 ist vorliegend als ein Wegeventil und insbesondere als ein 3/2 Wege-Schaltventil ausgebildet mit einer ersten Schaltposition, in der lediglich eine Hydraulikfluidströmung aus der Ringkammer 4b des Hauptzylinders 4 in Richtung Hydromaschine 1 zugelassen wird, einer zweiten Schaltposition, in der eine Hydraulikfluidströmung in beide Richtungen möglich ist und einer dritten Schaltposition, in der die zweite Leitung 5 vollständig gesperrt ist.Concretely, a first connecting line 3 is connected to a first pressure port of the hydraulic machine 1, which leads directly to a piston-side pressure chamber 4 a of a master cylinder 4. To the second pressure port of the hydraulic machine 1, a second line 5 is connected, which is connected via a valve 6 with a piston rod-side pressure chamber 4b of the master cylinder 4 (hereinafter referred to as annular chamber 4b). The valve 6 is presently designed as a directional control valve and in particular as a 3/2 way switching valve with a first switching position in which only a hydraulic fluid flow from the annular chamber 4b of the master cylinder 4 in the direction of hydraulic machine 1 is allowed, a second switching position in which a Hydraulic fluid flow in both directions is possible and a third switching position in which the second line 5 is completely blocked.

Zwischen der Hydromaschine 1 und dem vorstehend genannten Wege-Schaltventil 6 ist in die zweite Leitung 5 eine Abzweigung 7 eingesetzt, die zu einer kolbenstangenseitigen Druckkammer 8a eines Nebenzylinders 8 führt. Der Kolben 8b des Nebenzylinders 8 ist dabei in seinem Durchmesser deutlich kleiner als der Kolben 4c des Hauptzylinders 4, sodass der Hub des Nebenzylinders 8 bei vergleichbarem Volumenstrom des Hydraulikfluids größer ist als der Hub des Hauptzylinders 4. Ferner besitzen die Ringseiten der Zylinder 4, 8 idealer Weise in Summe die gleiche Fläche wie die Kolbenseite des Hauptzylinders 4.Between the hydraulic machine 1 and the aforementioned directional control valve 6, a branch 7 is inserted into the second line 5, which leads to a piston rod side pressure chamber 8a of an auxiliary cylinder 8. The piston 8b of the auxiliary cylinder 8 is in its diameter significantly smaller than the piston 4c of the master cylinder 4, so that the stroke of the auxiliary cylinder 8 at a comparable volume flow of the hydraulic fluid is greater than the stroke of the master cylinder 4. Furthermore, the ring sides of the cylinder 4, 8 ideally in sum the same area as the piston side of the master cylinder. 4

Schließlich ist eine Bypass- oder Kurzschlussleitung 9 vorgesehen, welche die Kolbenkammer 4a des Hauptzylinders 4 mit dessen Ringkammer 4b verbindet. In diese Bypassleitung 9 ist ein Kurzschlussventil 10 zwischengeschaltet, das vorliegend als Wegeschaltventil und vorzugsweise als 2/2 Wege Schaltventil ausgebildet ist. In einer ersten Schaltposition dieses Kurzschlussventils 10 ist die Bypassleitung 9 vollständig (d.h. in beide Richtungen) geöffnet, wobei in einer zweiten Schaltposition lediglich eine Fluidströmung aus der Ringkammer 4b in die Kolbenkammer 4a des Hauptzylinders 4 über die Bypassleitung 9 zugelassen ist.Finally, a bypass or shorting line 9 is provided which connects the piston chamber 4a of the master cylinder 4 with the annular chamber 4b. In this bypass line 9, a short-circuit valve 10 is interposed, the in the present case designed as a way switching valve and preferably as a 2/2 way switching valve. In a first switching position of this short-circuit valve 10, the bypass line 9 is fully open (ie in both directions), wherein in a second switching position only a fluid flow from the annular chamber 4b is admitted into the piston chamber 4a of the master cylinder 4 via the bypass line 9.

Im konkreten Ausführungsbeispiel der Erfindung ist der hydraulische Antrieb mit vorstehendem Aufbau in einer Presse eingebaut. Hierfür sind die Kolbenstange 4d des Hauptzylinders 4 wie auch die Kolbenstange 8c des Nebenzylinders 8 mit einem verschiebbar gelagerten Pressstempel 11 verbunden an dem ein Presswerkzeug 12 oder ein Stanzwerkzeug befestigt ist.In the concrete embodiment of the invention, the hydraulic drive with the above structure is installed in a press. For this purpose, the piston rod 4d of the master cylinder 4 as well as the piston rod 8c of the slave cylinder 8 are connected to a displaceably mounted ram 11 to which a pressing tool 12 or a punching tool is attached.

Grundsätzlich hat das Hydraulikdrucksystem gemäß der Erfindung auch zahlreiche Sicherungseinrichtungen zur Vermeidung von Überdruckzuständen oder von unbeabsichtigem Absinken des Pressstempels 11, die jedoch in den Figuren nicht im Detail dargestellt sind. So kann die Ringkammer 8a des Nebenzylinders 8 über zwei in Serie geschaltete, überwachte Sitzventile (nicht gezeigt) gesichert sein. Dadurch kann ein Absinken des oberen Presswerkzeugs 12 sicher verhindert werden. Zudem kann die Kolbenkammer 4a des Hauptzylinders 4 gegen eine unbeabsichtigte Druckbeaufschlagung abgesichert sein. Erfolgen kann dies durch die gezeigten Wegeventile 6, 10 selbst, oder aber durch eine überwachte Freigabe des elektrischen Antriebsmotors 2 der Hydromaschine 1.Basically, the hydraulic pressure system according to the invention also has numerous safety devices to prevent overpressure conditions or unintentional lowering of the ram 11, which are not shown in detail in the figures. Thus, the annular chamber 8a of the auxiliary cylinder 8 can be secured via two series-monitored, monitored seat valves (not shown). Thereby, a lowering of the upper pressing tool 12 can be securely prevented. In addition, the piston chamber 4 a of the master cylinder 4 can be secured against unintentional pressurization. This can be achieved by the directional control valves 6, 10 themselves, or by a monitored release of the electric drive motor 2 of the hydraulic machine 1.

Um Leckageverluste im System auszugleichen, ist an die erste Druckleitung 3 zwischen der Hydromaschine 1 und der Kolbenkammer 4a des Hauptzylinders 4 ein Druckspeicher 13 über ein Ventil 14 angeschlossen. Dieses Ventil 14 wird durch ein Wegeventil, vorzugsweise ein 2/2 Wege Schaltventil bereitgestellt, mit einer ersten Schaltposition, in der die Verbindung zwischen der externen Druckquelle 13 und der ersten Druckleitung 3 vollständig freigegeben ist und einer zweiten Schaltposition, in der lediglich eine Fluidströmung aus der externen Druckquelle 13 in die erste Druckleitung 3 zugelassen wird.To compensate for leakage losses in the system, a pressure accumulator 13 is connected via a valve 14 to the first pressure line 3 between the hydraulic machine 1 and the piston chamber 4a of the master cylinder 4. This valve 14 is provided by a directional control valve, preferably a 2/2 way switching valve, with a first switching position in which the connection between the external pressure source 13 and the first pressure line 3 is fully released and a second switching position in which only a fluid flow the external pressure source 13 in the first pressure line 3 is allowed.

Im Betriebszustand des hydraulischen Antriebs gemäß der Erfindung ist zumindest die kolbenseitige Druckkammer 4a des Hauptzylinders 4 ständig über die Druckmittelquelle mit einem vorbestimmten etwa konstanten (insbesondere geregelten) Hydraulikdruck beaufschlagt. Die Bewegung beider Zylinder 4, 8 wird dabei durch Umfördern von Druckmittel in dem geschlossenen Druckkreis mittels der drehzahlvariabel angetriebenen Hydromaschine 1 gesteuert.In the operating state of the hydraulic drive according to the invention, at least the piston-side pressure chamber 4a of the master cylinder 4 is constantly acted upon by the pressure medium source with a predetermined approximately constant (in particular regulated) hydraulic pressure. The movement of the two cylinders 4, 8 is controlled by circulating pressure medium in the closed pressure circuit by means of the variable-speed driven hydraulic machine 1.

Maßgeblich für die Steuerung des Bewegungsablaufs beider Zylinder 4, 8 ist die Zufuhr oder Abfuhr von Druckmittel aus den jeweiligen Ringkammern 4b, 8a über die drehzahlvariabel angetriebene Hydromaschine 1, wobei der komplette Bewegungsablauf des Arbeitshubs der Presse unter Beteiligung beider Zylinder mittels der Ventile 6, 10 und der drehzahlvariabel angetriebenen (Konstant-)Pumpe gesteuert werden kann.Decisive for the control of the movement sequence of both cylinders 4, 8 is the supply or discharge of pressure medium from the respective annular chambers 4b, 8a via the variable speed driven hydraulic machine 1, wherein the complete movement of the power stroke of the press with participation of both cylinders by means of the valves 6, 10th and the variable speed driven (constant) pump can be controlled.

Die Funktionsweise des erfindungsgemäßen hydraulischen Antriebs lässt sich anhand der anliegenden Figuren wie folgt beschreiben:

  • Gemäß der Fig. 1 befinden sich bei Stillstand des hydraulischen Antriebs (in zurückgezogener Stellung des Pressstempels 11) das Wegeschaltventil 6 in jener Schaltposition, in der nur eine Fluidströmung aus der Ringkammer 4b des Hauptzylinders 4 zugelassen ist und das Kurzschlussventil 10 in der Schaltposition, in der die Bypassleitung 9 vollständig geöffnet ist. Der elektrische Antriebsmotor 2 der Hydromaschine 1 ist ferner abgeschaltet.
The mode of operation of the hydraulic drive according to the invention can be described as follows with reference to the attached figures:
  • According to the Fig. 1 are located at a standstill of the hydraulic drive (in the retracted position of the ram 11) the directional control valve 6 in that switching position in which only a fluid flow from the annular chamber 4b of the master cylinder 4 is allowed and the short-circuit valve 10 in the switching position in which the bypass line 9 completely is open. The electric drive motor 2 of the hydraulic machine 1 is also switched off.

In diesem (statischen) Zustand wird das Gewicht des Pressstempels 11 durch den Druck innerhalb der Kolbenkammer 8a des Nebenzylinders 8 abgestützt, während in der Ring- und Kolbenkammer 4a, 4b des Hauptzylinders 4 über das Kurzschlussventil 10 Druckausgleich herrscht.In this (static) state, the weight of the ram 11 is supported by the pressure within the piston chamber 8a of the slave cylinder 8, while in the ring and piston chamber 4a, 4b of the master cylinder 4 via the short-circuit valve 10 pressure equalization prevails.

Um aus diesem (statischen) Zustand in den Eilgang abwärts zu kommen, wird gemäß der Fig. 2 das Ventil 6 in die vollständige Sperrposition geschaltet und die Hydromaschine 1 angetrieben. Hierdurch wird Druckmittel ausschließlich aus der Ringkammer 8a des Nebenzylinders 8 über die Leitung 5 abgesaugt und in die Kolbenkammer 4a des Hauptkolbens 4 abgegeben. Gleichzeitig bleibt der Druckausgleich zwischen den Hauptzylinderkammern 4a, 4b über das immer noch vollständig offene Kurzschlussventil 10 erhalten.To get down from this (static) state in the rapid, is according to the Fig. 2 the valve 6 is switched to the full blocking position and the hydraulic machine 1 driven. As a result, pressure fluid is sucked out exclusively from the annular chamber 8a of the auxiliary cylinder 8 via the line 5 and discharged into the piston chamber 4a of the main piston 4. At the same time, the pressure compensation between the main cylinder chambers 4a, 4b is maintained via the still completely open short-circuit valve 10.

Da der Nebenzylinder 8 kleiner ist als der Hauptzylinder 4 und die Pumpe 1 nur auf das Volumen der Ringseite des Nebenzylinders 8 wirkt, erfolgt die Abwärtsbewegung (und später auch die Rückziehbewegung) des Pressstempels 11 bei vorbestimmtem Volumenstrom bei einer relativ hohen Geschwindigkeit, auch dann, wenn die Hydromaschine 1 mit einer kleinen Kapazität ausgelegt ist. Darüber hinaus kann durch kurzzeitige Überlastung des elektrischen Antriebsmotors 2 (zulässig) die Geschwindigkeit aber auch die spätere Presskraft weiter erhöht werden.Since the slave cylinder 8 is smaller than the master cylinder 4 and the pump 1 acts only on the volume of the ring side of the slave cylinder 8, the downward movement (and later the retraction movement) of the ram 11 at a predetermined volume flow at a relatively high speed, even then, when the hydraulic machine 1 is designed with a small capacity. In addition, by briefly overloading the electric drive motor 2 (permissible), the speed but also the subsequent pressing force can be further increased.

Sobald das Presswerkzeug 12 ein zu bearbeitendes Werkstück 15 erreicht hat, schaltet das Kurzschlussventil 10 in die Schaltposition in der nur eine Strömung aus der Ringkammer 4b des Hauptzylinders 4 zugelassen ist und das Ventil 6 in die Schaltposition, in der eine Fluidströmung aus de Ringkammer 4b zur Hydromaschine 1 zugelassen wird. In diesem Zustand gemäß der Fig. 3 wird nunmehr auch der Druck innerhalb der Ringkammer 4b durch die Hydromaschine 1 abgebaut, da kein Druckausgleich zwischen den Hauptzylinderkammern 4a, 4b über das Kurzschlussventil 10 mehr stattfindet, wohingegen der Druck innerhalb der Kolbenkammer 4a des Hauptzylinders 4 beibehalten bzw. erhöht wird. D.h., anstatt einer erheblichen Kompression der Kolbenseite des Hauptzylinders 4, wird die eigentliche Presskraft durch Druckentspannung der Ringseiten der Zylinder 4, 8 erzeugt. Da kein Druckausgleich zwischen den Hauptzylinderkammern 4a, 4b mehr erfolgt, nimmt ferner die fortlaufende Pressbewegung des Hauptzylinders 4 bei gleich bleibendem Volumenstrom eine zur Absenkbewegung deutlich geringere Geschwindigkeit an als beim vorherigen Eilgang.Once the pressing tool 12 has reached a workpiece to be machined 15, the short-circuit valve 10 switches to the switching position in which only one flow from the annular chamber 4b of the master cylinder 4 is allowed and the valve 6 in the switching position in which a fluid flow from the annular chamber 4b to Hydromachine 1 is allowed. In this state according to the Fig. 3 Now, the pressure within the annular chamber 4b degraded by the hydraulic machine 1, since no pressure equalization between the master cylinder chambers 4a, 4b via the short-circuit valve 10 takes place more, whereas the pressure within the piston chamber 4a of the master cylinder 4 is maintained or increased. That is, instead of a significant compression of the piston side of the master cylinder 4, the actual pressing force is generated by pressure release of the ring sides of the cylinder 4, 8. Since no pressure equalization takes place between the main cylinder chambers 4a, 4b, furthermore, the continuous pressing movement of the master cylinder 4, while maintaining the volume flow constant, assumes a velocity which is much lower than that of the previous rapid traverse.

Zum Beenden des Pressvorgangs wird das Ventil 6 in eine Schaltposition gemäß der Fig. 4 gebracht, wonach eine Fluidströmung innerhalb der Verbindungsleitung 5 in beide Richtungen, d.h. aus und zu der Ringkammer 4b des Hauptzylinders 4 ermöglicht ist. In diesem Fall erfolgt ein Druckausgleich zwischen den Hauptzylinderkammern 4a, 4b und der Ringkammer 8a des Nebenzylinders 8 über die Verbindungsleitung 5 und die Abzweigung 7, wobei gleichzeitig Energie über den elektrischen Antriebsmotor 2 zurückgewonnen werden kann.To end the pressing operation, the valve 6 is in a switching position according to the Fig. 4 brought, after which a fluid flow within the connecting line 5 in both directions, ie, from and to the annular chamber 4b of the master cylinder 4 is made possible. In this case, a pressure equalization takes place between the main cylinder chambers 4a, 4b and the annular chamber 8a of the auxiliary cylinder 8 via the connecting line 5 and the branch 7, wherein at the same time energy can be recovered via the electric drive motor 2.

Schließlich kann der Pressstempel 11 zurückgezogen werden, indem wie in Fig. 5 dargestellt ist, das Ventil 6 in die Schaltposition gebracht wird, in der nur eine Strömung aus dem Ringraum 4a des Hauptzylinders 4 zugelassen ist und das Kurzschlussventil 10 in die Schaltposition geschaltet wird, in der die Bypassleitung 9 vollständig (in beide Richtungen) geöffnet ist.Finally, the punch 11 can be withdrawn by, as in Fig. 5 is shown, the valve 6 is brought into the switching position in which only one flow from the annular space 4a of the master cylinder 4 is allowed and the short-circuit valve 10 is switched to the switching position in which the bypass line 9 is fully open (in both directions).

Wird in diesem Zustand die Hydromaschine 1 angetrieben, um Druckmittel aus der Kolbenkammer 4a des Hauptzylinders 4 abzuziehen, wird das abgezogene Druckmittel bei vollständigem Druckausgleich der beiden Hauptzylinderkammern 4a, 4b in die Ringkammer 8a des Nebenzylinders 8 gedrückt, der den Pressstempel 11 mit hoher Geschwindigkeit wieder zurückzieht.If in this state the hydraulic machine 1 is driven to withdraw pressure medium from the piston chamber 4a of the master cylinder 4, the withdrawn pressure medium is pressed with complete pressure equalization of the two master cylinder chambers 4a, 4b in the annular chamber 8a of the slave cylinder 8, 11 of the press die at high speed again withdraws.

Bei dem vorstehend beschriebenen hydraulischen Antrieb kann die Hydromaschine 1 an einen Ventilblock (nicht weiter dargestellt) angeflanscht sein, welcher die Funktions- bzw. Sicherheitsventile des Antriebs enthält. An diesen kann wiederum der Elektromotor zum Betrieb der Pumpe angebaut sein. Diese Einheit kann wiederum auf einem Hydrozylinder aufgebaut sein, wodurch eine besonders kompakte Anstriebsachse zur Verfügung steht.In the hydraulic drive described above, the hydraulic machine 1 can be flanged to a valve block (not shown), which contains the functional or safety valves of the drive. In turn, the electric motor for operating the pump can be attached to these. This unit can in turn be constructed on a hydraulic cylinder, whereby a particularly compact Anstriebsachse is available.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11 Hydromaschinehydromachine 22 Servomotor (drehzahlvariabel)Servomotor (variable speed) 33 erste Verbindungsleitungfirst connection line 44 Hauptzylindermaster cylinder 4a4a Kolbenkammerpiston chamber 4b4b Ringkammerannular chamber 4c4c HauptzylinderkolbenMaster cylinder piston 4d4d Kolbenstangepiston rod 55 zweite Druckleitungsecond pressure line 66 VentilValve 77 Abzweigungdiversion 88th Nebenzylinderslave cylinder 8a8a Ringkammerannular chamber 8b8b NebenzylinderkolbenSlave cylinder piston 8c8c Kolbenstangepiston rod 99 Bypassleitungbypass line 1010 KurzschlussventilShort-circuit valve 1111 Pressstempelpress die 1212 Presswerkzeugpress tool 1313 Druckspeicheraccumulator 1414 VentilValve 1515 Werkstückworkpiece

Claims (7)

  1. Hydraulic drive having a hydraulic machine (1) which is actuated in a variable-speed manner by an electric drive motor (2), a master cylinder (4) for carrying out a force-building movement sequence and an auxiliary cylinder (8) for carrying out a rapid movement sequence, characterized in that, during operation, at least one piston side of the master cylinder (4) is loaded with a predefined permanent pressure which is built up by an external pressure source (13) and/or by the hydraulic machine (1) which is actuated mechanically by the drive motor (2), at the one pressure connection of the said hydraulic machine (1), the hydraulic machine (1), furthermore, bringing about a reciprocating movement of the master cylinder (4) and of the auxiliary cylinder (8) during operation after in each case one of the two movement sequences, by way of the selected cross-conveying of pressure medium in a closed circuit, into which the hydraulic machine (1) is interconnected.
  2. Hydraulic drive according to Claim 1, characterized in that the other pressure connection of the hydraulic machine (1) is connected to a piston rod-side annular chamber (4b) of the master cylinder (4) and to a piston rod-side annular chamber (8a) of the auxiliary cylinder (8).
  3. Hydraulic drive according to Claim 2, characterized in that a valve, preferably a directional control valve (6), is interconnected in a connecting line (5) of the closed circuit between the hydraulic machine (1) and the master-cylinder annular chamber (4b).
  4. Hydraulic drive according to Claim 3, characterized in that the valve (6) is a 3/2-way control valve with a first switching position, in which merely a hydraulic fluid flow from the master-cylinder annular chamber (4b) in the direction of the hydraulic machine (1) is permitted, a second switching position, in which a hydraulic fluid flow is made possible in both directions, and a third switching position, in which the connecting line (5) is completely shut off.
  5. Hydraulic drive according to Claim 3 or 4, characterized by a bypass line of the closed circuit, which bypass line connects the master-cylinder piston chamber (4a) to the master-cylinder annular chamber (4b), and into which bypass line a bypass valve (10) is interconnected.
  6. Hydraulic drive according to Claim 5, characterized in that the bypass valve (10) is a 2/2-way control valve which completely opens the bypass line (9) in a first switching position and permits merely a fluid flow from the annular chamber (4b) into the piston chamber (4a) of the master cylinder (4) via the bypass line (9) in a second switching position.
  7. Hydraulic drive according to one of the preceding claims, characterized in that the piston-rod sides (4b, 8a) of both cylinders (4, 8) have the same area in total as the piston side (4a) of the master cylinder (4) .
EP10740535.9A 2009-09-25 2010-07-27 Prestressed hydraulic drive with variable-speed pump Revoked EP2480405B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910043034 DE102009043034A1 (en) 2009-09-25 2009-09-25 Prestressed hydraulic drive with variable speed pump
PCT/EP2010/004578 WO2011035828A1 (en) 2009-09-25 2010-07-27 Prestressed hydraulic drive with variable-speed pump

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EP2480405A1 EP2480405A1 (en) 2012-08-01
EP2480405B1 true EP2480405B1 (en) 2013-06-19

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EP (1) EP2480405B1 (en)
CN (1) CN102612430B (en)
DE (1) DE102009043034A1 (en)
TW (1) TWI519717B (en)
WO (1) WO2011035828A1 (en)

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DE102017202131A1 (en) 2017-02-10 2018-08-16 Siemens Aktiengesellschaft Piezo-hydraulic actuator and method for operating such a piezohydraulic actuator

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DE102014226236A1 (en) * 2014-09-29 2016-03-31 Robert Bosch Gmbh Hydraulic circuit and machine with a hydraulic circuit
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DE102017202131A1 (en) 2017-02-10 2018-08-16 Siemens Aktiengesellschaft Piezo-hydraulic actuator and method for operating such a piezohydraulic actuator

Also Published As

Publication number Publication date
CN102612430B (en) 2016-04-27
WO2011035828A1 (en) 2011-03-31
TWI519717B (en) 2016-02-01
EP2480405A1 (en) 2012-08-01
CN102612430A (en) 2012-07-25
DE102009043034A1 (en) 2011-03-31
TW201115034A (en) 2011-05-01

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