EP0561185B1 - 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
EP0561185B1
EP0561185B1 EP93102909A EP93102909A EP0561185B1 EP 0561185 B1 EP0561185 B1 EP 0561185B1 EP 93102909 A EP93102909 A EP 93102909A EP 93102909 A EP93102909 A EP 93102909A EP 0561185 B1 EP0561185 B1 EP 0561185B1
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EP
European Patent Office
Prior art keywords
control
valve
piston
hydraulic
superposed
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Expired - Lifetime
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EP93102909A
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German (de)
French (fr)
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EP0561185A1 (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.
  • a slide control is known from US-A-4 125 844.
  • 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 supplied 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 relates to hydraulic working cylinders, the pistons of which are 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 volume-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.
  • a third of the known possibilities (US-A-4 215 844), which, however, only allows two different piston speeds, uses a pneumatic-hydraulic slide control for this.
  • a pneumatic-hydraulic slide control for this.
  • the pneumatic pilot control of both directional control valves is carried out by a setpoint-actual value comparator, which is acted upon by control pulses for the working cylinder.
  • the directional valve located in the by-pass is linked via the pneumatic pilot control to the reversing valve in such a way that in the event of large control deviations, the piston is driven at high speed via the by-pass, while the lower piston speed is achieved via the reduced volume of the throttle arrangement, which is at small control deviations is switched through.
  • 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 desired switching state, which is determined by the higher-level control.
  • the piston speed is determined by the control of a directional 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 directional valve is in contact with both sides of its valve piston a control line of the pilot control and is itself piloted by the pressure difference between the two control lines. With the built-in throttles, 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 chokes required for this purpose and built into the pilot control paths of the control valve represent simple means which can easily be implemented in hydraulic circuits.
  • the feature of claim 4, 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 action 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 acts on the piston rod side 7 of the working piston 4 with a volume flow of the hydraulic pressure generator (pump or accumulator) indicated at 6, while the piston side 9 of the piston 4 acts on the working cylinder 1 via the line 8 becomes.
  • the hydraulic pressure generator pump or accumulator
  • the reversing valve S3 is a 4/2-way valve of a 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 connected to the oil tank 10 without pressure.
  • 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 is located in the pilot control paths 11, 12 between the pilot control valve A and the reversing valve S3 built in the form of a pilot-operated control valve B. 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. Two ways switch the drain from the drive cylinder to the tank. Two intermediate paths 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 in succession.
  • 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.

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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)
  • Sliding Valves (AREA)
  • Actuator (AREA)
  • Fluid-Driven Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Valve Device For Special Equipments (AREA)
  • Reciprocating Pumps (AREA)
  • Control Of Presses (AREA)
  • Lifting Devices For Agricultural Implements (AREA)
  • Harvester Elements (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. Eine solche Schiebersteuerung ist aus US-A-4 125 844 bekannt.The invention relates to a hydraulic slide control for working cylinders according to the preamble of claim 1. Such a slide control is known from US-A-4 125 844.

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, bezieht sich die Erfindung auf hydraulische Arbeitszylinder, deren Kolben auf wenigstens einer seiner beiden Wege mit unterschiedlichen Geschwindigkeiten anzutreiben ist. 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 supplied 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 relates to hydraulic working cylinders, the pistons of which are 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 movements can be required for which must be accelerated and decelerated in a freely selectable sequence of the pistons.

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 volume-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 is to switch on 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.

Eine dritte der bekannten Möglichkeiten (US-A-4 215 844), welche allerdings nur zwei unterschiedliche Kolbengeschwindigkeiten ermöglicht, benutzt hierfür eine pneumatisch hydraulische Schiebersteuerung. Hierbei ist ein Zweiwege-Zweistellungsventil in einen By-Pass eines der beiden Volumenströme des hydraulischen Arbeitsmediums des Umsteuerventils vorgeschaltet. Die pneumatische Vorsteuerung beider Wegeventile erfolgt durch einen Sollwert-Istwert-Vergleicher, der mit Steuerimpulsen für den Arbeitszylinder beaufschlagt ist. Der By-Pass überbrückt eine Drosselanordnung, die dem Druckerzeuger des hydraulischen Arbeitsmediums nachgeschaltet ist. Das im By-Pass liegende Wegeventil ist über die pneumatische Vorsteuerung mit dem Umsteuerventil derart verknüpft, daß bei großen Regelabweichungen der Kolben mit großer Geschwindigkeit über den By-Pass angetrieben wird, während die geringere Kolbengeschwindigkeit über das reduzierte Volumen der Drosselanordnung erreicht wird, die bei geringen Regelabweichungen durchgeschaltet wird.A third of the known possibilities (US-A-4 215 844), which, however, only allows two different piston speeds, uses a pneumatic-hydraulic slide control for this. Here is a two-way, two-position valve in one By-pass upstream of one of the two volume flows of the hydraulic working medium of the reversing valve. The pneumatic pilot control of both directional control valves is carried out by a setpoint-actual value comparator, which is acted upon by control pulses for the working cylinder. The by-pass bridges a throttle arrangement, which is connected downstream of the pressure generator of the hydraulic working medium. The directional valve located in the by-pass is linked via the pneumatic pilot control to the reversing valve in such a way that in the event of large control deviations, the piston is driven at high speed via the by-pass, while the lower piston speed is achieved via the reduced volume of the throttle arrangement, which is at small control deviations is switched through.

Die Erfindung geht demgegenüber einen anderen Weg, dessen Grundgedanke im Anspruch 1 wiedergegeben ist.In contrast, the invention takes a different path, the basic idea of which is given in claim 1.

Weitere Merkmale der Erfindung sind Gegenstand der Unteransprüche.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 Wegeventiles 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 Wegeventil liegt mit beiden Seiten seines Ventilkolbens an je einer Steuerleitung der Vorsteuerung und ist durch die Druckdifferenz der beiden Steuerleitungen selbst vorgesteuert. Durch die eingebauten Drosseln 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 desired switching state, which is determined by the higher-level control. The piston speed is determined by the control of a directional 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 directional valve is in contact with both sides of its valve piston a control line of the pilot control and is itself piloted by the pressure difference between the two control lines. With the built-in throttles, 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.

Die dazu erforderlichen und in die Vorsteuerwege des Steuerventiles eingebauten Drosseln stellen einfache Mittel dar, die sich in hydraulischen Schaltungen leicht verwirklichen lassen.The chokes required for this purpose and built into the pilot control paths of the control valve represent simple means which can easily be implemented in hydraulic circuits.

Mit den Merkmalen des Anspruches 2 wird die Möglichkeit verwirklicht, den Kolben auf seinem Wege im hydraulischen Zylinder bedarfsweise anzuhalten.With the features of claim 2, the possibility is realized to stop the piston on its way in the hydraulic cylinder if necessary.

Das Merkmal des Anspruchs 4, 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 4, 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 action 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 acts on the piston rod side 7 of the working piston 4 with a volume flow of the hydraulic pressure generator (pump or accumulator) indicated at 6, while the piston side 9 of the piston 4 acts on the working cylinder 1 via the line 8 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. Im Ausführungsbeispiel ist die Kolbenseite 9 auf den Öltank 10 geschaltet.The reversing valve S3 is a 4/2-way valve of a 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 connected to the oil tank 10 without pressure. 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.A third directional valve is located in the pilot control paths 11, 12 between the pilot control valve A and the reversing valve S3 built in the form of a pilot-operated control valve B. 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. Two ways switch the drain from the drive cylinder to the tank. Two intermediate paths 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 in succession. 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 (4)

  1. An hydraulic valve spool control for actuators (1) with uneven piston velocities, in which a control transfer duct valve (B), through which one of the two volume streams of hydraulic operating medium passes, adapts the piston actuating volume stream of the hydraulic operating medium to the piston velocity and adjusts the direction of movement of the piston (4) by means of a superposed duct valve (S3) that is pre-activated by control pulses for the actuator (4), wherein the duct valve (B) is mounted in a position upstream of the superposed duct valve (S3), characterised in that a superposed control valve (A) is adjustable by the control pulses for the actuator (4) and that the superposed control ducts (11, 12) leading to the superposed control duct valve (S3) pre-activate the control transfer duct valve (B) which comprises a series of activating ducts that in each case determine a piston velocity, said series of activating ducts passing through the control transfer duct valve (B) in sequence with the aid of throttle valves (14, 15) mounted in the superposed control ducts of the control transfer duct valve (B).
  2. An hydraulic valve spool control according to claim 1, characterised in that, in at least one position of the control transfer duct valve (B), a retention stop is provided in the duct associated with said position.
  3. An hydraulic valve spool control according to one of claims 1 and 2, characterised in that the piston of the control transfer duct valve (B) comprises a series of conducting apertures, throttle apertures and retention stops.
  4. An hydraulic valve spool control according to one of claims 1 to 3, characterised in that an accumulator reservoir is provided as a pressure generator for the linear drive of an hydraulic actuator.
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

Publications (2)

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

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EP93102909A Expired - Lifetime EP0561185B1 (en) 1992-03-19 1993-02-25 Hydraulic valve spool control for actuators with uneven piston velocities

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US (1) US5353684A (en)
EP (1) EP0561185B1 (en)
JP (1) JPH0610904A (en)
KR (1) KR100280255B1 (en)
CN (1) CN1036730C (en)
AT (1) ATE152502T1 (en)
BR (1) BR9301230A (en)
CA (1) CA2092657A1 (en)
DE (2) DE4208755A1 (en)
ES (1) ES2103390T3 (en)
GR (1) GR3024142T3 (en)
RU (1) RU2134363C1 (en)

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Also Published As

Publication number Publication date
JPH0610904A (en) 1994-01-21
KR930020037A (en) 1993-10-19
BR9301230A (en) 1993-09-21
US5353684A (en) 1994-10-11
CA2092657A1 (en) 1993-09-20
KR100280255B1 (en) 2001-02-01
CN1036730C (en) 1997-12-17
DE59306308D1 (en) 1997-06-05
ES2103390T3 (en) 1997-09-16
GR3024142T3 (en) 1997-10-31
DE4208755A1 (en) 1993-09-23
ATE152502T1 (en) 1997-05-15
CN1078542A (en) 1993-11-17
RU2134363C1 (en) 1999-08-10
EP0561185A1 (en) 1993-09-22

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