EP0561185A1 - Hydraulic valve spool control for actuators with uneven piston velocities - Google Patents

Hydraulic valve spool control for actuators with uneven piston velocities Download PDF

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Publication number
EP0561185A1
EP0561185A1 EP93102909A EP93102909A EP0561185A1 EP 0561185 A1 EP0561185 A1 EP 0561185A1 EP 93102909 A EP93102909 A EP 93102909A EP 93102909 A EP93102909 A EP 93102909A EP 0561185 A1 EP0561185 A1 EP 0561185A1
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EP
European Patent Office
Prior art keywords
valve
control
piston
pilot
hydraulic
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
EP93102909A
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German (de)
French (fr)
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EP0561185B1 (en
Inventor
Friedrich Dipl.-Ing. Schwing
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Friedrich Wilhelm Schwing GmbH
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Friedrich Wilhelm Schwing 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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • 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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • 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
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional 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
    • F15B2211/30—Directional control
    • F15B2211/355—Pilot pressure 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out 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
    • 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
    • F15B2211/75—Control of speed of the output member

Definitions

  • the invention relates to a hydraulic slide control for working cylinders according to the preamble of claim 1.
  • Hydraulic working cylinders are used primarily in mechanical engineering to supply kinetic energy in two opposite directions. This allows moving parts to be moved back and forth.
  • the kinetic energy of such a hydraulic drive depends on the volume flow of the hydraulic medium, which is fed to the respective side of the piston in the hydraulic cylinder.
  • the piston While the piston generally develops a substantially uniform speed over the back and forth in the hydraulic working cylinder, the invention provides for the piston to be driven at different speeds in at least one of its two ways. This takes into account practical requirements that place different demands on the hydraulic drive. For example, it may be important to start the movement at a slow speed, then to accelerate in the central area and to slow it down again at the end of the movement.
  • Such hydraulic working cylinders are known per se.
  • One of the known embodiments provides a quantity control of the hydraulic volume flow corresponding to the respective piston speed in the working cylinder via the hydraulic pressure generator.
  • This usually requires quantity-adjustable pumps, where z. B. in a swash plate pump, the inclination of the control mirror determines the respective volume flow.
  • Such pumps are relatively expensive.
  • it is not always possible to provide pumps controlled in this way for the working cylinder. If such pumps are necessary in a control circuit from which the control circuit of the hydraulic working cylinder is derived, it is often not possible to easily achieve different piston speeds in this way.
  • the invention is based on the above-described possibility of controlling the piston speed via the volume flow acting on the drive piston, the direction of movement being switched over with a pilot-controlled directional valve. she goes however, another way, the basic idea of which is given in claim 1. Further features of the invention are the subject of the dependent claims.
  • the pilot control valve is precontrolled with a pilot valve which directs hydraulic medium to one or the other side of the valve piston and thus brings about the respectively desired switching state, which is determined by the higher-level control.
  • the piston speed is determined by the control of a control valve, the piston of which can assume any number of positions, adapted to the individual case, with the control bores assigned to it and thereby directly influence one of the volume flows in each position.
  • This control valve is located on both sides of its valve piston on a control line of the pilot control and is therefore pilot-controlled itself. As a result, the desired control state can be brought about hydraulically and determines one of the piston speeds.
  • the invention has the advantage that it enables different working speeds with a linear drive in the form of a hydraulic working cylinder in a simple manner, namely in particular without the aid of the hydraulic pressure generator. This also includes the possibility of stopping the piston of the working cylinder.
  • the feature of claim 5, namely to provide a memory as a pressure generator for the linear drive of a hydraulic working cylinder, has the advantage over a hydraulic pump with a constant delivery volume that the difference between the amount of pressure determined by the control bore for the working cylinder and the amount available from the pressure generator do not need to be routed to the tank via a safety valve to generate heat.
  • FIG. 1 shows the slide control according to the invention in symbols, while the hydraulic working cylinder 1 and the machine part driven by its piston rod 2 are shown schematically in the form of a two-armed rocker arm 3.
  • the piston 4 runs in the hydraulic working cylinder 1.
  • a line 5 applies a volume flow of the hydraulic pressure generator (pump or accumulator) indicated at 6 (piston or side) to the piston rod side 7 of the working piston 4, while the line 8 acts on the piston side 9 of the piston 4 in the working cylinder 1 becomes.
  • the hydraulic pressure generator pump or accumulator
  • the reversing valve S3 is a 4/2-way valve of known type and enables the hydraulic pressure oil flow to be applied to each piston side, while at the same time the opposite piston side is depressurized on the oil tank 10. in the
  • the piston side 9 is connected to the oil tank 10.
  • a pilot valve A which can be acted upon by switching control pulses on both sides of its valve piston, is used to control the two pilot control paths 11, 12 of the reversing valve S3.
  • This pilot valve essentially corresponds to the reversing valve S3, but it can also be switched over electrically or electronically.
  • the tank appears twice in the drawing, in practice it can be the same tank into which the outgoing volume flow is directed from the pilot control paths 11, 12.
  • a third directional valve in the form of a pilot-controlled control valve B is installed in the pilot paths 11, 12. It is also hydraulically piloted. This takes place via throttles 14, 15 from the pilot control paths 11, 12.
  • the valve piston of the control valve B has five paths. The drain from the drive cylinder connects to the tank in two ways. Two paths in between contain throttles with the same or different throttling effect, while the middle path blocks the volume flow.
  • the arrangement is such that the volume flow displaced from the piston side 9 runs via the line 8 through the control valve B, while the piston rod side 7 is connected to the hydraulic pressure generator 6 via line 5 and a bypass 16.
  • the throttle 14 acts on the unpressurized side of the valve piston in the control valve B.
  • the throttle 15 determines the respective position of the valve piston, the valve piston running through all switching paths one after the other.
  • the drive piston 4 is driven at different speeds and stopped in the middle position.
  • the rocker arm 3 of the lever mechanism therefore executes a sequence of movements via the effective path indicated by the double arrows.

Landscapes

  • Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Actuator (AREA)
  • Sliding Valves (AREA)
  • Reciprocating Pumps (AREA)
  • Control Of Presses (AREA)
  • Harvester Elements (AREA)
  • Fluid-Driven Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Lifting Devices For Agricultural Implements (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

In hydraulic valve spool control for actuators with uneven piston velocities in which the volumetric flow of the hydraulic working medium acting on the piston is adapted to the respective piston velocity, and the direction of movement of the piston is set with a pilot-controlled directional valve, provision is made according to the invention for the reversing valve (S3) to be hydraulically pilot-controlled with a pilot-control valve (A) which is adjustable with the control impulses for the actuator (1), and for a hydraulically pilot-controlled control valve (B) to be installed between the pilot-control paths (11, 12) from the pilot-control valve (A) to the reversing valve (S3), through which control valve (B) one of the two volumetric flows of the hydraulic working medium passes, a piston velocity being allocated to each position of the control valve (B). <IMAGE>

Description

Die Erfindung betrifft eine hydraulische Schiebersteuerung für Arbeitszylinder gemäß dem Oberbegriff des Anspruches 1.The invention relates to a hydraulic slide control for working cylinders according to the preamble of claim 1.

Hydraulische Arbeitszylinder dienen vor allem im Maschinenbau zur Zuführung von Bewegungsenergie in zwei gegenläufigen Richtungen. Damit lassen sich bewegliche Teile hin- und herbewegen. Die Bewegungsenergie eines derartigen hydraulischen Antriebes hängt von dem Volumenstrom des hydraulischen Mediums ab, welcher der jeweiligen Seite des Kolbens im hydraulischen Zylinder zugeleitet wird. Während im allgemeinen der Kolben eine im wesentlichen gleichförmige Geschwindigkeit über den Hin- und Hergang im hydraulischen Arbeitszylinder entwickelt, ist erfindungsgemäß vorgesehen, den Kolben auf wenigstens einer seiner beiden Wege mit unterschiedlichen Geschwindigkeiten anzutreiben. Damit wird praktischen Erfordernissen Rechnung getragen, welche unterschiedliche Anforderungen an den hydraulischen Antrieb stellen. Beispielsweise kann es darauf ankommen, die Bewegung mit langsamer Geschwindigkeit starten zu lassen, dann im Mittelbereich zu beschleunigen und am Bewegungsende wieder zu verlangsamen. Eine andere Anforderung geht dahin, die Bewegung mit hoher Geschwindigkeit zu starten, zum Mittelbereich hin zu verzögern und erforderlichenfalls kurzzeitig zum Stillstand zu bringen, um dann am Ende wieder zu beschleunigen. Dies sind lediglich Beispiele. In der Praxis kann eine Vielzahl anderer Bewegungsablaufkombinationen gefordert werden, für die in frei wählbarer Folge der Kolben beschleunigt und verzögert werden muß.Hydraulic working cylinders are used primarily in mechanical engineering to supply kinetic energy in two opposite directions. This allows moving parts to be moved back and forth. The kinetic energy of such a hydraulic drive depends on the volume flow of the hydraulic medium, which is fed to the respective side of the piston in the hydraulic cylinder. While the piston generally develops a substantially uniform speed over the back and forth in the hydraulic working cylinder, the invention provides for the piston to be driven at different speeds in at least one of its two ways. This takes into account practical requirements that place different demands on the hydraulic drive. For example, it may be important to start the movement at a slow speed, then to accelerate in the central area and to slow it down again at the end of the movement. Another requirement is to start the movement at high speed, decelerate to the central area and, if necessary, bring it to a standstill for a short time and then accelerate again at the end. These are just examples. In practice, a variety of other combinations of motion sequences are required for which the piston must be accelerated and decelerated in a freely selectable sequence.

Solche hydraulischen Arbeitszylinder sind an sich bekannt. Eine der bekannten Ausführungsformen sieht eine der jeweiligen Kolbengeschwindigkeit im Arbeitszylinder entsprechende Mengensteuerung des hydraulischen Volumenstromes über den hydraulischen Druckerzeuger vor. Das setzt in der Regel mengenverstellbare Pumpen voraus, bei denen z. B. bei einer Schiefscheibenpumpe die Neigung des Steuerspiegels den jeweiligen Volumenstrom bestimmt. Solche Pumpen sind verhältnismäßig aufwendig. Außerdem ist es nicht immer möglich, derart gesteuerte Pumpen für den Arbeitszylinder vorzusehen. Sind solche Pumpen in einem Steuerkreis notwendig, von dem der Steuerkreis des hydraulischen Arbeitszylinders abgeleitet ist, kann man auf diese Weise unterschiedliche Kolbengeschwindigkeiten häufig nicht ohne weiteres verwirklichen.Such hydraulic working cylinders are known per se. One of the known embodiments provides a quantity control of the hydraulic volume flow corresponding to the respective piston speed in the working cylinder via the hydraulic pressure generator. This usually requires quantity-adjustable pumps, where z. B. in a swash plate pump, the inclination of the control mirror determines the respective volume flow. Such pumps are relatively expensive. In addition, it is not always possible to provide pumps controlled in this way for the working cylinder. If such pumps are necessary in a control circuit from which the control circuit of the hydraulic working cylinder is derived, it is often not possible to easily achieve different piston speeds in this way.

Eine andere bekannte Möglichkeit, eine Maschine oder ein Maschinenelement mit einem Arbeitszylinder in einer Bewegungsrichtung mit unterschiedlicher Geschwindigkeit anzutreiben, besteht darin, in die Vermittlung der Bewegungsenergie ein mechanisches Getriebe einzuschalten. Insbesondere kommen hierfür Hebelgetriebe in Betracht. Solche Getriebe sind vergleichsweise aufwendig und benötigen auch Platz, der nicht immer zur Verfügung gestellt werden kann.Another known possibility of driving a machine or a machine element with a working cylinder in one direction of movement at different speeds consists in engaging a mechanical transmission in the mediation of the kinetic energy. Lever gears are particularly suitable for this. Such gears are comparatively complex and also require space that cannot always be made available.

Die Erfindung geht von der oben wiedergegebenen Möglichkeit der Steuerung der Kolbengeschwindigkeit über den den Antriebskolben beaufschlagenden Volumenstrom aus, wobei die Umschaltung der Bewegungsrichtung mit einem vorgesteuerten Wegeventil erfolgt. Sie geht jedoch einen anderen Weg, dessen Grundgedanke im Anspruch 1 wiedergegeben ist. Weitere Merkmale der Erfindung sind Gegenstand der Unteransprüche.The invention is based on the above-described possibility of controlling the piston speed via the volume flow acting on the drive piston, the direction of movement being switched over with a pilot-controlled directional valve. she goes however, another way, the basic idea of which is given in claim 1. Further features of the invention are the subject of the dependent claims.

Erfindungsgemäß erfolgt die Vorsteuerung des Umsteuerwegeventils mit einem Vorsteuerventil, welches hydraulisches Medium auf die eine oder die andere Seite des Ventilkolbens leitet und so den jeweils gewünschten Schaltzustand herbeiführt, der von der übergeordneten Steuerung bestimmt wird. Die Kolbengeschwindigkeit wird durch die Steuerung eines Steuerventiles bestimmt, dessen Kolben eine beliebige, dem Einzelfall jedoch angepaßte Anzahl von Stellungen mit diesen zugeordneten Steuerbohrungen einnehmen kann und dadurch in jeder Stellung einen der Volumenströme unmittelbar beeinflußt. Dieses Steuerventil liegt mit beiden Seiten seines Ventilkolbens an je einer Steuerleitung der Vorsteuerung und ist dadurch selbst vorgesteuert. Dadurch kann der jeweils gewünschte Steuerzustand hydraulisch herbeigeführt werden und bestimmt jeweils eine der Kolbengeschwindigkeiten.According to the invention, the pilot control valve is precontrolled with a pilot valve which directs hydraulic medium to one or the other side of the valve piston and thus brings about the respectively desired switching state, which is determined by the higher-level control. The piston speed is determined by the control of a control valve, the piston of which can assume any number of positions, adapted to the individual case, with the control bores assigned to it and thereby directly influence one of the volume flows in each position. This control valve is located on both sides of its valve piston on a control line of the pilot control and is therefore pilot-controlled itself. As a result, the desired control state can be brought about hydraulically and determines one of the piston speeds.

Die Erfindung hat den Vorteil, daß sie auf einfache Weise, nämlich insbesondere ohne Zuhilfenahme des hydraulischen Druckerzeugers, jedoch auf hydraulischem Wege unterschiedliche Arbeitsgeschwindigkeiten mit einem Linearantrieb in Form eines hydraulischen Arbeitszylinders ermöglicht. Dazu gehört auch die Möglichkeit, den Kolben des Arbeitszylinders anzuhalten.The invention has the advantage that it enables different working speeds with a linear drive in the form of a hydraulic working cylinder in a simple manner, namely in particular without the aid of the hydraulic pressure generator. This also includes the possibility of stopping the piston of the working cylinder.

Vorzugsweise und mit den Merkmalen der Ansprüche 2 und 4 lassen sich mehrere Kolbengeschwindigkeiten nacheinander einstellen. Die dazu erforderlichen und in die Vorsteuerwege des Steuerventiles eingebauten Drosseln stellen einfache Mittel dar, die sich in hydraulischen Schaltungen leicht verwirklichen lassen.Preferably and with the features of claims 2 and 4, several piston speeds can be set in succession. The chokes required for this purpose and built into the pilot control paths of the control valve represent simple means which can be found in hydraulic circuits can be easily implemented.

Mit den Merkmalen des Anspruches 3 wird die Möglichkeit verwirklicht, den Kolben auf seinem Wege im hydraulischen Zylinder bedarfsweise anzuhalten.With the features of claim 3, the possibility is realized to stop the piston on its way in the hydraulic cylinder if necessary.

Das Merkmal des Anspruchs 5, nämlich als Druckerzeuger für den Linearantrieb eines hydraulischen Arbeitszylinders einen Speicher vorzusehen, hat gegenüber einer Hydraulikpumpe mit konstantem Fördervolumen den Vorteil, daß die Differenzmenge zwischen der von der Steuerbohrung bestimmte Beaufschlagungsmenge für den Arbeitszylinder und der vom Druckerzeuger zur Verfügung stehenden Menge nicht wärmeerzeugend über ein Sicherheitsventil zum Tank geleitet werden müssen.The feature of claim 5, namely to provide a memory as a pressure generator for the linear drive of a hydraulic working cylinder, has the advantage over a hydraulic pump with a constant delivery volume that the difference between the amount of pressure determined by the control bore for the working cylinder and the amount available from the pressure generator do not need to be routed to the tank via a safety valve to generate heat.

In der Zeichnung ist ein Ausführungsbeispiel der Erfindung wiedergegeben. Die Zeichnung zeigt die erfindungsgemäße Schiebersteuerung in Symbolen, während der hydraulische Arbeitszylinder 1 sowie der von seiner Kolbenstange 2 angetriebene Maschinenteil in Form einer zweiarmigen Schwinge 3 schematisch wiedergegeben sind. In dem hydraulischen Arbeitszylinder 1 läuft der Kolben 4. Eine Leitung 5 beaufschlagt mit einem Volumenstrom des bei 6 angedeuteten hydraulischen Druckerzeugers (Pumpe oder Speicher) die Kolbenstangenseite 7 des Arbeitskolbens 4, während über die Leitung 8 die Kolbenseite 9 des Kolbens 4 im Arbeitszylinder 1 beaufschlagt wird.In the drawing, an embodiment of the invention is shown. The drawing shows the slide control according to the invention in symbols, while the hydraulic working cylinder 1 and the machine part driven by its piston rod 2 are shown schematically in the form of a two-armed rocker arm 3. The piston 4 runs in the hydraulic working cylinder 1. A line 5 applies a volume flow of the hydraulic pressure generator (pump or accumulator) indicated at 6 (piston or side) to the piston rod side 7 of the working piston 4, while the line 8 acts on the piston side 9 of the piston 4 in the working cylinder 1 becomes.

Das Umsteuerventil S3 ist ein 4/2-Wegeventil bekannter Art und ermöglicht die Beaufschlagung jeder Kolbenseite mit dem hydraulischen Druckölstrom, während gleichzeitig die gegenüberliegende Kolbenseite drucklos auf den Öltank 10 geschaltet ist. ImThe reversing valve S3 is a 4/2-way valve of known type and enables the hydraulic pressure oil flow to be applied to each piston side, while at the same time the opposite piston side is depressurized on the oil tank 10. in the

Ausführungsbeispiel ist die Kolbenseite 9 auf den Öltank 10 geschaltet.In the exemplary embodiment, the piston side 9 is connected to the oil tank 10.

Ein von einer übergeordneten Steuerung mit Schaltimpulsen auf beiden Seiten seines Ventilkolbens beaufschlagbares Vorsteuerventil A dient zur Steuerung der beiden Vorsteuerwege 11, 12 des Umsteuerventils S3. Dieses Vorsteuerventil entspricht im wesentlichen dem Umsteuerventil S3, jedoch kann es auch elektrisch bzw. elektronisch umgeschaltet werden. Obwohl der Tank in der Zeichnung zweimal erscheint, kann es sich in der Praxis um den gleichen Tank handeln, in den der ablaufende Volumenstrom aus den Vorsteuerwegen 11, 12 geleitet wird.A pilot valve A, which can be acted upon by switching control pulses on both sides of its valve piston, is used to control the two pilot control paths 11, 12 of the reversing valve S3. This pilot valve essentially corresponds to the reversing valve S3, but it can also be switched over electrically or electronically. Although the tank appears twice in the drawing, in practice it can be the same tank into which the outgoing volume flow is directed from the pilot control paths 11, 12.

Zwischen das Vorsteuerventil A und das Umsteuerventil S3 ist in die Vorsteuerwege 11, 12 ein drittes Wegeventil in Gestalt eines vorgesteuerten Steuerventiles B eingebaut. Es ist ebenfalls hydraulisch vorgesteuert. Dies erfolgt über Drosseln 14, 15 aus den Vorsteuerwegen 11, 12. Der Ventilkolben des Steuerventils B weist gemäß dem dargestellten Ausführungsbeispiel fünf Wege auf. Zwei Wege schalten den Ablauf aus dem Antriebszylinder auf den Tank durch. Zwei dazwischenliegende Wege enthalten Drosseln mit gleicher oder unterschiedlicher Drosselwirkung, während der mittlere Weg den ablaufenden Volumenstrom sperrt.Between the pilot valve A and the reversing valve S3, a third directional valve in the form of a pilot-controlled control valve B is installed in the pilot paths 11, 12. It is also hydraulically piloted. This takes place via throttles 14, 15 from the pilot control paths 11, 12. According to the exemplary embodiment shown, the valve piston of the control valve B has five paths. The drain from the drive cylinder connects to the tank in two ways. Two paths in between contain throttles with the same or different throttling effect, while the middle path blocks the volume flow.

In der Schaltung ist die Anordnung so getroffen, daß der von der Kolbenseite 9 verdrängte Volumenstrom über die Leitung 8 durch das Steuerventil B verläuft, während die Kolbenstangenseite 7 über Leitung 5 und einen Bypaß 16 an den hydraulischen Druckerzeuger 6 angeschlossen ist.In the circuit, the arrangement is such that the volume flow displaced from the piston side 9 runs via the line 8 through the control valve B, while the piston rod side 7 is connected to the hydraulic pressure generator 6 via line 5 and a bypass 16.

Im Betrieb wirkt die Drossel 14 an der drucklosen Seite des Ventilkolbens im Steuerventil B. Die Drossel 15 bestimmt die jeweilige Stellung des Ventilkolbens, wobei der Ventilkolben sämtliche Schaltwege nacheinander durchläuft. Infolgedessen wird der Antriebskolben 4 mit unterschiedlicher Geschwindigkeit angetrieben und in der Mittelstellung angehalten. Die Schwinge 3 des Hebelgetriebes führt daher eine Folge von Bewegungen über den wirksamen und durch die Doppelpfeile gekennzeichneten Weg aus.In operation, the throttle 14 acts on the unpressurized side of the valve piston in the control valve B. The throttle 15 determines the respective position of the valve piston, the valve piston running through all switching paths one after the other. As a result, the drive piston 4 is driven at different speeds and stopped in the middle position. The rocker arm 3 of the lever mechanism therefore executes a sequence of movements via the effective path indicated by the double arrows.

Wird das Umsteuerventil S3 umgeschaltet, so kehrt der Kolben des Steuerventils B in seine Anfangsstellung zurück und kann hierbei wiederum verschiedene Bewegungsabläufe ausführen.If the reversing valve S3 is switched over, the piston of the control valve B returns to its initial position and can in turn carry out various movements.

Claims (5)

Hydraulische Schiebersteuerung für Arbeitszylinder mit ungleichen Kolbengeschwindigkeiten, bei der der den Kolben beaufschlagende Volumenstrom des hydraulischen Arbeitsmediums der jeweiligen Kolbengeschwindigkeit angepaßt und die Bewegungsrichtung des Kolbens mit einem vorgesteuerten Wegeventil eingestellt wird, dadurch gekennzeichnet, daß das Umsteuerventil (S3) hydraulisch mit einem Vorsteuerventil (A) vorgesteuert ist, welches mit den Steuerimpulsen für den Arbeitszylinder (1) verstellbar ist und daß zwischen die Vorsteuerwege (11, 12) vom Vorsteuerventil (A) zum Umsteuerventil (S3) ein hydraulisch vorgesteuertes Steuerventil (B) eingebaut ist, durch das einer der beiden Volumenströme des hydraulischen Arbeitsmediums verläuft, wobei jeder Stellung des Schaltventils (B) eine Kolbengeschwindigkeit zugeordnet ist.Hydraulic slide control for working cylinders with unequal piston speeds, in which the volume flow of the hydraulic working medium acting on the piston is adapted to the respective piston speed and the direction of movement of the piston is set with a pilot-controlled directional valve, characterized in that the reversing valve (S3) is hydraulically controlled with a pilot valve (A) is pilot-controlled, which is adjustable with the control pulses for the working cylinder (1) and that between the pilot control paths (11, 12) from the pilot valve (A) to the reversing valve (S3) a hydraulically piloted control valve (B) is installed, through which one of the two Volume flows of the hydraulic working medium runs, with a piston speed being assigned to each position of the switching valve (B). Hydraulische Schiebersteuerung nach Anspruch 1, dadurch gekennzeichnet, daß die hydraulische Vorsteuerung des Steuerventiles (B) mit in die Vorsteuerwege eingeschalteten Drosseln (14, 15) erfolgt.Hydraulic slide control according to claim 1, characterized in that the hydraulic pilot control of the control valve (B) takes place with throttles (14, 15) switched into the pilot control paths. Hydraulische Schiebersteuerung nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, daß in mindestens einer Stellung des Steuerventiles (B) in den dieser zugeordneten Weg eine Sperre eingebaut ist.Hydraulic slide control according to one of claims 1 or 2, characterized in that in at least one position of the control valve (B) a lock is installed in the path assigned to it. Hydraulische Schiebersteuerung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der Kolben des Steuerventiles (B) eine Folge von Durchgangsbohrungen, Drosselbohrungen und Sperren aufweist.Hydraulic slide control according to one of claims 1 to 3, characterized in that the piston of the control valve (B) has a series of through bores, throttle bores and locks. Hydraulische Schiebersteuerung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß als Druckerzeuger für den Linearantrieb eines hydraulischen Arbeitszylinders ein Speicher vorgesehen ist.Hydraulic slide control according to one of claims 1 to 4, characterized in that a memory is provided as the pressure generator for the linear drive of a hydraulic working cylinder.
EP93102909A 1992-03-19 1993-02-25 Hydraulic valve spool control for actuators with uneven piston velocities Expired - Lifetime EP0561185B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4208755A DE4208755A1 (en) 1992-03-19 1992-03-19 HYDRAULIC SLIDER CONTROL FOR WORK CYLINDERS WITH UNEQUALIZED PISTON SPEEDS
DE4208755 1992-03-19

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EP0561185A1 true EP0561185A1 (en) 1993-09-22
EP0561185B1 EP0561185B1 (en) 1997-05-02

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EP (1) EP0561185B1 (en)
JP (1) JPH0610904A (en)
KR (1) KR100280255B1 (en)
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AT (1) ATE152502T1 (en)
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KR100280255B1 (en) 2001-02-01
CN1078542A (en) 1993-11-17
CN1036730C (en) 1997-12-17
BR9301230A (en) 1993-09-21
RU2134363C1 (en) 1999-08-10
DE4208755A1 (en) 1993-09-23
ES2103390T3 (en) 1997-09-16
JPH0610904A (en) 1994-01-21
KR930020037A (en) 1993-10-19
GR3024142T3 (en) 1997-10-31
US5353684A (en) 1994-10-11
EP0561185B1 (en) 1997-05-02
DE59306308D1 (en) 1997-06-05
ATE152502T1 (en) 1997-05-15

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