EP0241870A2 - Hydraulic control device - Google Patents

Hydraulic control device Download PDF

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Publication number
EP0241870A2
EP0241870A2 EP87105284A EP87105284A EP0241870A2 EP 0241870 A2 EP0241870 A2 EP 0241870A2 EP 87105284 A EP87105284 A EP 87105284A EP 87105284 A EP87105284 A EP 87105284A EP 0241870 A2 EP0241870 A2 EP 0241870A2
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EP
European Patent Office
Prior art keywords
pressure
pilot valve
outlet
line
control device
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
EP87105284A
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German (de)
French (fr)
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EP0241870A3 (en
EP0241870B1 (en
Inventor
Martin Dipl.-Ing. Heusser (eth.Zürich)
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Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
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Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
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Priority to AT87105284T priority Critical patent/ATE71191T1/en
Publication of EP0241870A2 publication Critical patent/EP0241870A2/en
Publication of EP0241870A3 publication Critical patent/EP0241870A3/en
Application granted granted Critical
Publication of EP0241870B1 publication Critical patent/EP0241870B1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors

Definitions

  • the invention relates to a hydraulic control device of the type specified in the preamble of claim 1.
  • control valves which are particularly suitable for speed and position control of movements in one direction against load.
  • a hydraulic control device is provided in the control circuit of which the orifice and the three-way pilot valve and the external actuator are contained.
  • the three-way pilot valve Depending on the actuating force of the actuator, the three-way pilot valve generates a pressure at its control connection which acts on the orifice element against the force of the spring and the pressure in the drain line in order to maintain a certain preselected orifice size.
  • the second outlet of the three-way pilot valve is connected to the tank so that pressure medium can be released to lower the pressure at the control connection.
  • a displacement pickup device for position control of the orifice element is required, with which the respective position of the orifice element is sensed and communicated to the actuator, which retroactively changes the actuating force to hold the previously selected aperture size hydraulically via the pilot valve.
  • the displacement device is structurally complex and expensive. Furthermore, the three-way pilot valve complex and expensive to manufacture because it has to process the full working pressure compared to the discharge pressure to the tank. Furthermore, a complex electrical control circuit is necessary.
  • the invention has for its object to provide a control device of the type mentioned, with which a selected aperture size is maintained in a structurally simple manner and with a simple and inexpensive pilot valve in the event of pressure changes in the inlet and / or in the outlet line.
  • the pressure in the drain line in the pilot valve linearly overlaps the pressure at the control connection of the pilot valve, so that the pressure difference between the pressure in the control connection of the pilot valve and the discharge pressure is always proportional to the force of the actuator.
  • the pilot valve only needs to cope with the relatively small pressure difference between the pressure in its control connection and the discharge pressure, which has the advantage that the pilot valve can be simple and inexpensive and still forms an extremely effective reinforcement for the external adjusting member. This results in the particular advantage of the control device, because an actuator with a relatively weak actuating force is sufficient to easily process even high pressures and large delivery rates. If the actuator is, for example, a proportional magnet, it can be weak and therefore small and inexpensive.
  • the high forces which may be present at a high working pressure, are generated by the pilot valve with the help of the pressure in the control connection built up from the pressure in the supply line, which pressure can be relatively high, but is nevertheless compensated by the pressure in the discharge line to such an extent that the actuator despite the high processed pressures, only a small actuating force needs to be applied and the pilot valve only has to cope with the aforementioned relatively small pressure difference.
  • the only basic requirement for the correct operation of the hydraulic control device is that the pressure prevailing in the inlet line is always greater than the pressure in the outlet line, so that the pressure required at the control connection of the pilot valve, which must be greater than the pressure in the outlet line, is generated and that the pressure in the drain line also loads the orifice element against the pressure from the control connection of the pilot valve.
  • the aperture size in the blend selected with the adjusted actuating force of the actuator is thus automatically held without a separate displacement pick-up device in the event of pressure changes in the inlet and / or outlet line. Because the pilot valve only the low Has to process pressure difference, it can work practically with zero coverage and regulate the pressure fluctuations very sensitively and still respond quickly when switching the control device on and off.
  • the most fundamental advantages of this training are the possibility of using a relatively weak actuator even at high pressures and large delivery rates, and the possibility of using a simple and therefore inexpensive pilot valve without an expensive displacement device.
  • a useful embodiment is further evident from claim 2.
  • a commercially available pressure reducing valve can be used in a particularly useful and cost-saving manner; it only needs to be connected to the tank line with the drain line.
  • the embodiment of claim 3 is also expedient because the zero position spring ensures that the pilot valve automatically assumes its zero position when the device is switched off and its valve element does not get caught in an intermediate position.
  • the features of claim 6 are important since the orifice then automatically assumes its full open position when the pilot valve is in the zero position.
  • control device creates a load-compensated flow control valve device with the pressure compensator, which is characterized by compact external dimensions and only a few individual parts.
  • the diaphragm with the control device forms the regulating diaphragm of the pressure compensator in this embodiment.
  • the pressure compensator also ensures that the pressure in the supply line is always higher.
  • an aperture 1 is shown schematically, which is housed in a housing, not shown.
  • An annular channel 2 is provided in the housing as part of an orifice chamber 6, from which an outlet channel 3 is led downward.
  • An inlet line 4 leads to the ring channel 2.
  • An outlet line 5 leads away from the outlet channel 3.
  • a diaphragm element 7 in the form of an diaphragm piston is slidably guided, which has radially distributed passages 8.
  • the diaphragm element 7 is urged upwards by a spring 9 in FIG. 1.
  • the diaphragm element 7 divides the diaphragm chamber 6 into an upper chamber 10 and a lower chamber 11.
  • the passages 8 define with their edges, together with boundary edges 13 of the ring channel 2, an diaphragm opening 14, the size of which can be changed depending on the stroke position of the diaphragm element 7.
  • a channel 15 opens into the chamber 10.
  • a control line 16 is connected to the inlet line 4, which leads into a hydraulic control device 17, indicated by dashed lines, which is connected via a line 18 to the channel 15 and via a line 19 to the outlet line 5.
  • a separate and externally supplied control line could also be provided.
  • the size of the diaphragm opening 14 is reduced. In the lower end position of the panel element 7, the panel opening 14 is closed. In the upper end position of the panel element 7, however, the full size of the panel opening is open.
  • the hydraulic control device 17 includes a three-way pilot valve 20, which can be a conventional pressure reducing valve of simple design.
  • a valve element of the three-way pilot valve 20, designated 23, is acted upon in the upward direction by a weak zero-setting spring 21 and by pressure derived from the line 18 by means of a pilot line 22. This action is counteracted by the pressure derived from line 19 via a control line 25 at the upper end of valve element 23.
  • an actuator 24 acts on the valve element 23, which can be actuated externally to adjust its actuating force, which is directed downward, for example.
  • the actuator 24 is expediently a proportional magnet, the magnetic force of which changes in proportion to the current applied.
  • a pressure compensator 26 which ensures that the pressure in the inlet line 4 is always higher than in the outlet line 5. In this way, a total load-compensated flow control valve device created.
  • the hydraulic control device works as follows:
  • the spring 9 Before starting operation, the spring 9 has moved the diaphragm element 7 into the upper end position; the aperture 14 has its full size.
  • the actuator 24 has no actuating force.
  • the zero position spring 21 has shifted the valve element 23 into its upper end position (corresponding to the symbolic representation in FIG. 2); the connection from line 18 to line 19 is open.
  • the actuator 24 also sets a predetermined actuating force which corresponds to a certain size of the aperture 14.
  • the valve element 23 of the pilot valve 20 has moved downward, so that a pressure P X is built up from the line 16 with its pressure P A in the control connection of the pilot valve 20, which loads the orifice element 7 via the line 18 and moves it downward, so that the aperture 14 is gradually closed.
  • the pressure B building up until then in the discharge line 5 generates in the line 19 the pressure P B which , via the control line 25 together with the actuating force of the actuator 24, loads the valve element 23 downward, so that there is between the pressure P X and the Pressure P B sets a pressure difference that is exactly proportional to the actuating force of the actuator 24.
  • the diaphragm element 7 Under the force of the spring 9 and with the pressure B in the line L, the diaphragm element 7 is held in a predetermined lifting position in which the predetermined diaphragm opening size is set. There is an equilibrium state.
  • valve element 23 is also moved slightly downward via the control line 25, so that the pressure P X in the pressure P A Line 18 is increased accordingly until the set size of the aperture 14 is held again.
  • control device 17 determines whether the amount of pressure medium flowing through the orifice 14 is kept constant or the pressure drop. This is also irrelevant for many applications, but what is crucial is maintaining a certain size Diaphragm opening 14. If the quantity should also be kept constant, the pressure compensator 26 can be used in the usual way.
  • FIG. 3 and 4 show two ways of forming the aperture.
  • Fig. 3 shows the aperture shown in Fig. 1 in a symbolic representation, wherein the spring 9 ensures that the aperture 1 assumes its full open position in the zero position.
  • the orifice assumes its full closed position in the zero position, in which the connection from the inlet line to the outlet line is interrupted.
  • the basic prerequisite for the proper functioning of the control device is that the pressure P A and thus the pressure in the inlet line 4 is greater than or equal to the sum of the pressure P B corresponding to the pressure B in the outlet line 5 plus the maximum pressure difference that the three-way Pilot valve 20 can process.
  • the pressure P X prevailing in the line 18 results from the sum of the pressure P B in the line 19 (corresponding to the pressure B in the discharge line 5) and the respective pressure difference of the three-way pilot valve 20, ie the pressure difference between the pressure P. X and the pressure P B.
  • the three-way pilot valve works practically without leakage losses in the zero position, so that it e.g. can easily be used with forklifts or forklifts.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Fluid Pressure (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Fluid-Driven Valves (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

The invention relates to a hydraulic control apparatus comprising a hydraulically adjustable throttle opening between an inlet passage and an outlet passage, a three-way pilot valve connected to an external actuator and having its inlet connected to a control pressure inlet passage, its control outlet being connected to the throttle valve in such a manner that the throttle valve element thereof is adapted to be biased in opposition to the pressure in the outlet passage and to the force of a spring. Known control apparatus require the employ of a displacement sensor for sensing the position or displacement of the throttle valve element and for correspondingly acting on the actuator to thereby vary the actuating force thereof for maintaining the opening degree of the throttle opening. This construction involves considerable complications. It is also disadvantageous that the pilot valve is subjected to the full operating pressure, requiring it to be of a highly accurate and therefor expensive construction. According to the invention the second outlet of the three-way pilot valve is connected to the outlet passage, and the valve element of the pilot valve is subjected to the pressure at the control outlet in opposition to the actuating force and to the pressure at the second outlet, and the inlet pressure supplied to the pilot valve is higher than the outlet pressure at least by the maximum possible pressure difference over the pilot valve.

Description

Die Erfindung betrifft eine hydraulische Steuervorrichtung der im Gattungsbegriff des Patentanspruchs 1 angegebenen Art.The invention relates to a hydraulic control device of the type specified in the preamble of claim 1.

In der Praxis sind Regelventile bekannt, die besonders geeignet sind für Geschwindigkeits- und Lageregelungen von Bewegungen in einer Richtung gegen Last. Dabei ist eine hydraulische Steuervorrichtung vorgesehen, in deren Steuerkreis die Blende und das Dreiwege-Vorsteuer­ventil sowie das externe Stellglied enthalten sind. Das Dreiwege-Vorsteuerventil erzeugt in Abhängigkeit von der Stellkraft des Stellgliedes an seinem Steueranschluß einen Druck, der das Blendenelement gegen die Kraft der Feder und den Druck in der Ablaufleitung beaufschlagt, um eine bestimmte vorgewählte Blendenöffnungsgröße aufrechtzuerhalten. Der zweite Ausgang des Dreiwege-Vor­steuerventils ist mit dem Tank verbunden, um zum Senken des Drucks am Steueranschluß Druckmittel ablassen zu können. Damit die Steuervorrichtung auf sich ändernde Drücke in der Zulauf- und/oder in der Ablaufleitung reagieren kann, ist eine Wegaufnahmevorrichtung zur Lageregelung des Blendenelementes erforderlich, mit der die jeweilige Lage des Blendenelementes abgetastet und dem Stellglied mitgeteilt wird, das rückwirkend die Stellkraft verändert, um über das Vorsteuerventil die vorher gewählte Blendenöffnungsgröße hydraulisch zu halten. Die Wegaufnahmeeinrichtung ist baulich aufwendig und teuer. Ferner ist das Dreiwege-Vorsteuerventil aufwendig und teuer in der Herstellung, weil es im wesentlichen den vollen Arbeitsdruck gegenüber dem Ablaufdruck zum Tank verarbeiten muß. Ferner ist ein aufwendiger elektrischer Steuerkreis notwendig.In practice, control valves are known which are particularly suitable for speed and position control of movements in one direction against load. A hydraulic control device is provided in the control circuit of which the orifice and the three-way pilot valve and the external actuator are contained. Depending on the actuating force of the actuator, the three-way pilot valve generates a pressure at its control connection which acts on the orifice element against the force of the spring and the pressure in the drain line in order to maintain a certain preselected orifice size. The second outlet of the three-way pilot valve is connected to the tank so that pressure medium can be released to lower the pressure at the control connection. So that the control device can react to changing pressures in the inlet and / or in the outlet line, a displacement pickup device for position control of the orifice element is required, with which the respective position of the orifice element is sensed and communicated to the actuator, which retroactively changes the actuating force to hold the previously selected aperture size hydraulically via the pilot valve. The displacement device is structurally complex and expensive. Furthermore, the three-way pilot valve complex and expensive to manufacture because it has to process the full working pressure compared to the discharge pressure to the tank. Furthermore, a complex electrical control circuit is necessary.

Aus der Zeitschrift Ölhydraulik + Pneumatik, 25 (1981) Nr. 8, Seiten 617 bis 624, sind elektrisch geregelte Zweiwege-Einbauventile bekannt, die einem neuen Konzept entsprechend entwickelt wurden. Auf Seite 618, oben, sind unterschiedliche Möglichkeiten für die Wegrückführung gezeigt, unter anderem auch mit sogenannten Folge-Kolbensystemen. Das letztgenannte Prinzip ist jedoch für eingangs genannte Steuervorrichtungen nur bedingt brauchbar, da es für verschiedene Anwendungszwecke unzulässige Leckverluste in der Nullstellung sowie ein Arbeitsverhalten bedingt, dessen Regelkennung erst bei einem bestimmten Druck mit einem stufenförmigen Übergang beginnt.From the magazine Ölhydraulik + Pneumatik, 25 (1981) No. 8, pages 617 to 624, electrically controlled two-way cartridge valves are known which have been developed in accordance with a new concept. On page 618, above, different possibilities for the return are shown, including with so-called follower piston systems. However, the latter principle can only be used to a limited extent for the control devices mentioned at the outset, since it requires inadmissible leakage losses in the zero position for various purposes and a working behavior whose control identification only begins with a step-like transition at a certain pressure.

Der Erfindung liegt die Aufgabe zugrunde, eine Steuervorrichtung der eingangs genannten Art zu schaffen, mit der eine gewählte Blendenöffnungsgröße auf baulich einfache Weise und mit einem einfachen und preiswerten Vorsteuerventil bei Druckänderungen in der Zulauf- und/oder in der Ablaufleitung beibehalten wird.The invention has for its object to provide a control device of the type mentioned, with which a selected aperture size is maintained in a structurally simple manner and with a simple and inexpensive pilot valve in the event of pressure changes in the inlet and / or in the outlet line.

Die gestellte Aufgabe wird erfindungsgemäß durch die im kennzeichnenden Teil des Patentanspruchs 1 angegebenen Merkmale gelöst.The object is achieved according to the invention by the features specified in the characterizing part of patent claim 1.

Bei dieser Ausbildung überlagert sich der Druck in der Ablaufleitung im Vorsteuerventil linear dem Druck am Steueranschluß des Vorsteuerventils, so daß die Druckdifferenz zwischen dem Druck im Steueranschluß des Vorsteuerventils und dem Ablaufdruck stets der Kraft des Stellgliedes proportional ist. Das Vorsteuerventil braucht nur die verhältnismäßig kleine Druckdifferenz zwischen dem Druck in seinem Steueranschluß und dem Ablaufdruck zu verkraften, was den Vorteil bringt, daß das Vorsteuerventil einfach und preiswert ausgebildet sein kann und trotzdem eine außerordentlich wirksame Verstärkung für das externe Verstellglied bildet. Daraus resuliert der besondere Vorteil der Steuervorrichtung, weil nämlich ein Stellglied mit verhältnismäßig schwacher Stellkraft ausreicht, auch hohe Drücke und große Fördermengen problemlos zu verarbeiten. Ist das Stellglied beispielsweise ein Proportionalmagnet, so kann dieser schwach und damit klein und preiswert ausgelegt sein. Die hohen Kräfte, die bei gegebenenfalls hohem Arbeitsdruck vorliegen, erzeugt das Vorsteuerventil mit Hilfe des aus dem Druck in der Zulaufleitung aufgebauten Drucks im Steueranschluß, der verhältnismäßig hoch sein kann, aber trotzdem durch den Druck in der Ablaufleitung so weit kompensiert wird, daß das Stellglied trotz der hohen verarbeiteten Drücke nur geringe Stellkräfte aufzubringen braucht und auch das Vorsteuerventil nur die vorerwähnte relativ kleine Druckdifferenz zu verkraften hat. Einzige grundsätzliche Voraussetzung für das ordnungsgemäße Arbeiten der hydraulischen Steuervorrichtung ist, daß der in der Zulaufleitung herrschende Druck stets größer als der Druck in der Ablaufleitung ist, damit der am Steueranschluß des Vorsteuerventils benötigte Druck, der größer als der Druck in der Ablaufleitung sein muß, erzeugt werden kann, und daß ferner der Druck in der Ablaufleitung das Blendenelement entgegen dem Druck vom Steueranschluß des Vorsteuerventils belastet. Die mit der eingestellten Stellkraft des Stellgliedes gewählte Blendenöffnungsgröße in der Blend wird somit ohne gesonderte Wegaufnehmeeinrichtung bei Druckänderungen in der Zulauf- und/oder der Ablaufleitung selbsttätig gehalten. Da das Vorsteuerventil nur die geringe Druckdifferenz zu verarbeiten hat, kann es praktisch mit Null-Überdeckung arbeiten und die Druckschwankungen sehr feinfühlig ausregeln und trotzdem beim Ein- und Ausschalten der Steuervorrichtung rasch ansprechen. Die grundlegendsten Vorteile dieser Ausbildung sind die Möglichkeit, auch bei hohen Drücken und großen Fördermengen ein verhältnismäßig schwaches Stellglied zu benutzen, und die Möglichkeit, ohne eine teure Wegaufnehmeeinrichtung ein einfaches und deshalb preiswertes Vorsteuerventil einzusetzen.In this configuration, the pressure in the drain line in the pilot valve linearly overlaps the pressure at the control connection of the pilot valve, so that the pressure difference between the pressure in the control connection of the pilot valve and the discharge pressure is always proportional to the force of the actuator. The pilot valve only needs to cope with the relatively small pressure difference between the pressure in its control connection and the discharge pressure, which has the advantage that the pilot valve can be simple and inexpensive and still forms an extremely effective reinforcement for the external adjusting member. This results in the particular advantage of the control device, because an actuator with a relatively weak actuating force is sufficient to easily process even high pressures and large delivery rates. If the actuator is, for example, a proportional magnet, it can be weak and therefore small and inexpensive. The high forces, which may be present at a high working pressure, are generated by the pilot valve with the help of the pressure in the control connection built up from the pressure in the supply line, which pressure can be relatively high, but is nevertheless compensated by the pressure in the discharge line to such an extent that the actuator despite the high processed pressures, only a small actuating force needs to be applied and the pilot valve only has to cope with the aforementioned relatively small pressure difference. The only basic requirement for the correct operation of the hydraulic control device is that the pressure prevailing in the inlet line is always greater than the pressure in the outlet line, so that the pressure required at the control connection of the pilot valve, which must be greater than the pressure in the outlet line, is generated and that the pressure in the drain line also loads the orifice element against the pressure from the control connection of the pilot valve. The aperture size in the blend selected with the adjusted actuating force of the actuator is thus automatically held without a separate displacement pick-up device in the event of pressure changes in the inlet and / or outlet line. Because the pilot valve only the low Has to process pressure difference, it can work practically with zero coverage and regulate the pressure fluctuations very sensitively and still respond quickly when switching the control device on and off. The most fundamental advantages of this training are the possibility of using a relatively weak actuator even at high pressures and large delivery rates, and the possibility of using a simple and therefore inexpensive pilot valve without an expensive displacement device.

Eine zweckmäßige Ausführungsform geht weiterhin aus Anspruch 2 hervor. Ein handelsübliches Druckminderventil läßt sich besonders nutzbringend und kostensparend einsetzen, es braucht nur sein Tankanschluß mit der Ablaufleitung verbunden zu werden.A useful embodiment is further evident from claim 2. A commercially available pressure reducing valve can be used in a particularly useful and cost-saving manner; it only needs to be connected to the tank line with the drain line.

Zweckmäßig ist ferner die Ausführungsform von Anspruch 3, weil mit der Nullstellungsfeder erreicht wird, daß das Vorsteuerventil beim Ausschalten der Vorrichtung selbsttätig seine Nullstellung einnimmt und sein Ventilelement nicht in einer Zwischenstellung hängenbleibt.The embodiment of claim 3 is also expedient because the zero position spring ensures that the pilot valve automatically assumes its zero position when the device is switched off and its valve element does not get caught in an intermediate position.

Ein weiterer, wichtiger Gedanke geht aus Anspruch 4 hervor. Da die Druckdifferenz stets der Stellkraft des Proportionalmagneten proportional bleibt, wird neben dem Vorteil, daß die mit einer bestimmten Stellkraft gewählte Blendenöffnungsgröße bei Druckschwankungen selbsttätig gehalten wird, eine exakt proportionale Veränderung der Blendenöffnungsgröße in Abhängigkeit von der Strombeaufschlagung des Proportionalmagneten erreicht. Der Proportionalmagnet kann verhältnismäßig schwach ausgelegt sein, so daß er kostengünstig ist und kompakte Abmessungen erreicht werden.Another important idea emerges from claim 4. Since the pressure difference always remains proportional to the actuating force of the proportional magnet, in addition to the advantage that the aperture size selected with a certain actuating force is automatically maintained in the event of pressure fluctuations, an exactly proportional change in the aperture size depending on the current applied to the proportional magnet is achieved. The proportional magnet can be designed relatively weak, so that it is inexpensive and compact dimensions can be achieved.

Eine weitere, vorteilhafte Ausführungsform geht aus Anspruch 5 hervor. In der Nullstellung des Vorsteuerventils nimmt die Blende selbsttätig ihre Schließstellung ein, wie es für bestimmte Anwendungsfälle erforderlich ist. Die das Blendenelement beaufschlagende Feder bestimmt im übrigen die Druckdifferenz zwischen dem Druck im Steueranschluß des Vorsteuerventils und dem Druck in der Ablaufleitung.Another advantageous embodiment is set out in claim 5. In the zero position of the pilot valve, the orifice automatically assumes its closed position, as is required for certain applications. The spring acting on the orifice element also determines the pressure difference between the pressure in the control connection of the pilot valve and the pressure in the drain line.

Bei einer anderen, für andere Anwendungszwecke geeigneten Ausführungsform sind die Merkmale von Anspruch 6 wichtig, da dann die Blende in der Nullstellung des Vorsteuerventils selbsttätig ihre volle Öffnungsstellung einnimmt.In another embodiment suitable for other applications, the features of claim 6 are important since the orifice then automatically assumes its full open position when the pilot valve is in the zero position.

Wichtig ist schließlich auch das Merkmal von Anspruch 7, weil die Steuervorrichtung mit der Druckwaage eine lastkompensierte Stromregelventileinrichtung schafft, die sich durch kompakte Außenabmessungen und nur wenige Einzelteile auszeichnet. Die Blende mit der Steuervorrichtung bildet bei dieser Ausbildung die Regelblende der Druckwaage. Die Druckwaage sorgt im übrigen für den stets höheren Druck in der Zulaufleitung.Finally, the feature of claim 7 is important because the control device creates a load-compensated flow control valve device with the pressure compensator, which is characterized by compact external dimensions and only a few individual parts. The diaphragm with the control device forms the regulating diaphragm of the pressure compensator in this embodiment. The pressure compensator also ensures that the pressure in the supply line is always higher.

Anhand der Zeichnung werden nachstehend Ausführungsbeispiele des Erfindungsgegenstandes erläutert. Es zeigen:

  • Fig. 1 eine Blende mit einer schematisch angedeuteten hydraulischen Steuervorrichtung,
  • Fig. 2 als Blockschaltbild eine lastkompensierte Stromregeleinrichtung, und
  • Fig. 3 + 4 zwei Ausführungsvarianten der Blende.
Exemplary embodiments of the subject matter of the invention are explained below with the aid of the drawing. Show it:
  • 1 is an aperture with a schematically indicated hydraulic control device,
  • Fig. 2 shows a block diagram of a load-compensated current control device, and
  • Fig. 3 + 4 two variants of the panel.

In Fig. 1 ist eine Blende 1 schematisch dargestellt, die in einem nicht näher gezeigten Gehäuse untergebracht ist. Im Gehäuse ist ein Ringkanal 2 als Teil einer Blendenkammer 6 vorgesehen, aus der nach unten ein Ablaufkanal 3 herausgeführt ist. Zum Ringkanal 2 führt eine Zulaufleitung 4. Vom Ablaufkanal 3 Führt eine Ablaufleitung 5 weg. In der Blendenkammer 6 ist ein Blendenelement 7 in Form eines Blendenkolbens verschiebbar geführt, das radial verteilte Durchgänge 8 aufweist. Das Blendenelement 7 wird durch eine Feder 9 in Fig. 1 nach oben beaufschlagt. Das Blendenelement 7 teilt die Blendenkammer 6 in eine obere Kammer 10 und eine untere Kammer 11. Die Durchgänge 8 definieren mit ihren Rändern zusammen mit Begrenzungskanten 13 des Ringkanals 2 eine Blendenöffnung 14, deren Größe in Abhängigkeit von der Hubstellung des Blendenelementes 7 veränderbar ist. In die Kammer 10 mündet ein Kanal 15. An die Zulaufleitung 4 ist eine Steuerleitung 16 angeschlossen, die in eine strichliert angedeutete hydraulische Steuervorrichtung 17 führt, die über eine Leitung 18 mit dem Kanal 15 und über eine Leitung 19 mit der Ablaufleitung 5 verbunden ist. Anstelle der von der Zulaufleitung 4 abzweigenden Steuerleitung 16 könnte auch eine getrennte und extern versorgte Steuerleitung vorgesehen sein.In Fig. 1, an aperture 1 is shown schematically, which is housed in a housing, not shown. An annular channel 2 is provided in the housing as part of an orifice chamber 6, from which an outlet channel 3 is led downward. An inlet line 4 leads to the ring channel 2. An outlet line 5 leads away from the outlet channel 3. In the diaphragm chamber 6, a diaphragm element 7 in the form of an diaphragm piston is slidably guided, which has radially distributed passages 8. The diaphragm element 7 is urged upwards by a spring 9 in FIG. 1. The diaphragm element 7 divides the diaphragm chamber 6 into an upper chamber 10 and a lower chamber 11. The passages 8 define with their edges, together with boundary edges 13 of the ring channel 2, an diaphragm opening 14, the size of which can be changed depending on the stroke position of the diaphragm element 7. A channel 15 opens into the chamber 10. A control line 16 is connected to the inlet line 4, which leads into a hydraulic control device 17, indicated by dashed lines, which is connected via a line 18 to the channel 15 and via a line 19 to the outlet line 5. Instead of the control line 16 branching off from the supply line 4, a separate and externally supplied control line could also be provided.

Wird das Blendenelement 7 in Fig. 1 nach unten bewegt, so wird die Größe der Blendenöffnung 14 verkleinert. In der unteren Endstellung des Blendenelementes 7 ist die Blendenöffnung 14 verschlossen. In der oberen Endstellung des Blendenelementes 7 ist hingegen die Blendenöffnung mit voller Größe geöffnet.If the diaphragm element 7 is moved downward in FIG. 1, the size of the diaphragm opening 14 is reduced. In the lower end position of the panel element 7, the panel opening 14 is closed. In the upper end position of the panel element 7, however, the full size of the panel opening is open.

Aus Fig. 2 ist erkennbar, daß die hydraulische Steuervorrichtung 17 ein Dreiwege-Vorsteuerventil 20 enthält, das ein übliches Druckminderventil einfacher Bauart sein kann. Ein mit 23 bezeichnetes Ventilelement des Dreiwege-Vorsteuerventils 20 wird durch eine schwache Nullstellungsfeder 21 und durch mittels einer Vorsteuerleitung 22 von der Leitung 18 abgeleiteten Druck in Richtung nach oben beaufschlagt. Dieser Beaufschlagung wirkt der über eine Stuerleitung 25 von der Leitung 19 abgeleitete Druck am oberen Ende des Ventilelementes 23 entgegen. Ferner greift am Ventilelement 23 ein Stellglied 24 an, das zur Verstellung seiner beispielweise nach unten gerichteten Stellkraft extern betätigbar ist. Zweckmäßigerweise ist das Stellglied 24 ein Proportionalmagnet, dessen Magnetkraft sich proportional zur Strombeaufschlagung verändert.From Fig. 2 it can be seen that the hydraulic control device 17 includes a three-way pilot valve 20, which can be a conventional pressure reducing valve of simple design. A valve element of the three-way pilot valve 20, designated 23, is acted upon in the upward direction by a weak zero-setting spring 21 and by pressure derived from the line 18 by means of a pilot line 22. This action is counteracted by the pressure derived from line 19 via a control line 25 at the upper end of valve element 23. Furthermore, an actuator 24 acts on the valve element 23, which can be actuated externally to adjust its actuating force, which is directed downward, for example. The actuator 24 is expediently a proportional magnet, the magnetic force of which changes in proportion to the current applied.

Ferner ist in Fig. 2 angedeutet, daß die Zulaufleitung 4 und die Ablaufleitung 5 durch eine Druckwaage 26 geführt sind, die dafür sorgt, daß der Druck in der Zulaufleitung 4 stets höher ist, als in der Ablaufleitung 5. Auf diese Weise wird insgesamt eine lastkompensierte Stromregelventileinrichtung geschaffen.Furthermore, it is indicated in Fig. 2 that the inlet line 4 and the outlet line 5 are guided by a pressure compensator 26, which ensures that the pressure in the inlet line 4 is always higher than in the outlet line 5. In this way, a total load-compensated flow control valve device created.

Die hydraulische Steuervorrichtung arbeitet wie folgt:The hydraulic control device works as follows:

Vor Betriebsaufnahme hat die Feder 9 das Blendenelement 7 in die obere Endstellung verschoben; die Blendenöffnung 14 hat ihr volle Größe. Das Stellglied 24 bringt keine Stellkraft auf. Die Nullstellungsfeder 21 hat das Ventilelement 23 in seine obere Endstellung verschoben (entsprechend der symbolischen Darstellung in Fig. 2); die Verbindung von der Leitung 18 zur Leitung 19 ist offen.Before starting operation, the spring 9 has moved the diaphragm element 7 into the upper end position; the aperture 14 has its full size. The actuator 24 has no actuating force. The zero position spring 21 has shifted the valve element 23 into its upper end position (corresponding to the symbolic representation in FIG. 2); the connection from line 18 to line 19 is open.

Wird nun Druck eingespeist, so wird auch mit dem Stellglied 24 eine vorbestimmte Stellkraft eingestellt, die einer bestimmten Größe der Blendenöffnung 14 entspricht. Das Ventilelement 23 des Vorsteuerventils 20 hat sich nach unten bewegt, so daß aus der Leitung 16 mit ihrem Druck PA im Steueranschluß des Vorsteuerventils 20 ein Druck PX aufgebaut wird, der über die Leitung 18 das Blendenelement 7 oben belastet und nach unten verschiebt, so daß die Blendenöffnung 14 allmählich geschlossen wird. Der sich bis dahin in der Ablaufleitung 5 aufbauende Druck B erzeugt in der Leitung 19 den Druck PB, der über die Steuerleitung 25 zusammen mit der Stellkraft des Stellgliedes 24 das Ventilelement 23 nach unten belastet, so daß sich zwischen dem Druck PX und dem Druck PB eine Druckdifferenz einstellt, die exakt der Stellkraft des Stellgliedes 24 proportional ist. Unter der Kraft der Feder 9 und mit dem Druck B in der Leitung L wird das Blendenelement 7 in einer vorbestimmten Hubstellung gehalten, in der die vorbestimmte Blendenöffnungsgröße eingestellt ist. Es ergibt sich ein Gleichgewichtszustand.If pressure is now fed in, the actuator 24 also sets a predetermined actuating force which corresponds to a certain size of the aperture 14. The valve element 23 of the pilot valve 20 has moved downward, so that a pressure P X is built up from the line 16 with its pressure P A in the control connection of the pilot valve 20, which loads the orifice element 7 via the line 18 and moves it downward, so that the aperture 14 is gradually closed. The pressure B building up until then in the discharge line 5 generates in the line 19 the pressure P B which , via the control line 25 together with the actuating force of the actuator 24, loads the valve element 23 downward, so that there is between the pressure P X and the Pressure P B sets a pressure difference that is exactly proportional to the actuating force of the actuator 24. Under the force of the spring 9 and with the pressure B in the line L, the diaphragm element 7 is held in a predetermined lifting position in which the predetermined diaphragm opening size is set. There is an equilibrium state.

Steigt bei einer Anwendung der Blende 1 in Verbindung mit einer Druckwaage 26 (wie in Fig. 1 angedeutet) der Druck A in der Zulaufleitung 4, so steigt auch der Druck PB in der Leitung 19 und der Steuerleitung 25, die das Ventilelement 23 geringfügig nach unten verlagert, so daß auch der Druck PX in der Leitung 18 und in der Steuerleitung 22 steigt, der wegen des ebenfalls steigenden Druckes PB der Tendenz des Blendenelementes 7, sich nach oben zu bewegen, entgegenwirkt und das Blendenelement in der Hubstellung festhält, die der vorgewählten Größe der Blendenöffnung 14 entspricht.If the pressure A in the inlet line 4 rises when the orifice 1 is used in conjunction with a pressure compensator 26 (as indicated in FIG. 1), then the pressure P B in the line 19 and the control line 25, which the valve element 23 slightly increases shifted downwards, so that the pressure P X in the line 18 and in the control line 22 also increases, which counteracts the tendency of the orifice element 7 to move upwards because of the likewise increasing pressure P B and holds the orifice element in the lifting position , which corresponds to the preselected size of the aperture 14.

Sinkt oder steigt hingegen bei einer Anwendung der Blende 1 ohne eine Druckwaage der Druck A, so ändert sich die Stellung des Blendenelementes 7 nicht, da der Druck A sowohl beim Blendenelement 7 als auch im Vorsteuerventil 20 radial eingespeist wird, darart, daß er keine Kraft in axialer Richtung erzeugen kann.On the other hand, if the pressure A drops or rises when the orifice 1 is used without a pressure compensator, the position of the orifice element 7 does not change, since the pressure A is fed radially to both the orifice element 7 and the pilot valve 20, so that it does not exert any force can generate in the axial direction.

Steigt hingegen der Druck B in der Ablaufleitung 5, was über die Steuerleitung 11 ein Anheben des Blendenelementes 7 bewirken möchte, so wird auch das Ventilelement 23 über die Steuerleitung 25 geringfügig nach unten bewegt, damit aus dem Druck PA der Druck PX in der Leitung 18 entsprechend erhöht wird, bis wieder die eingestellte Größe der Blendenöffnung 14 gehalten ist.If, on the other hand, the pressure B in the discharge line 5 rises, which would like to raise the orifice element 7 via the control line 11, the valve element 23 is also moved slightly downward via the control line 25, so that the pressure P X in the pressure P A Line 18 is increased accordingly until the set size of the aperture 14 is held again.

Sinkt der Druck B in der Ablaufleitung 5, möchte der Druck PX in der Leitung 18 das Blendenelement 7 nach unten bewegen. Da gleichzeitig der Druck PB in der Leitung 19 und in der Steuerleitung 25 sinkt, ist das Ventilelement 23 unter dem noch hohen Druck in der Steuerleitung 22 geringfügig nach oben verlagert, so daß der Druck PX in der Leitung 18 über die Leitung 19 entsprechend abgesenkt wird, damit die Größe der Blendenöffnung 14 gehalten wird.If the pressure B in the drain line 5 drops, the pressure P X in the line 18 would like to move the orifice element 7 downward. Since the pressure P B in the line 19 and in the control line 25 drops at the same time, the valve element 23 is displaced slightly upwards under the still high pressure in the control line 22, so that the pressure P X in line 18 via line 19 correspondingly is lowered so that the size of the aperture 14 is maintained.

Auf diese Weise wird die durch das Stellglied 24 vorgegebene Größe der Blendenöffnung 14 bei Druckschwankungen selbsttätig eingehalten.In this way, the size of the orifice 14 predetermined by the actuator 24 is automatically maintained in the event of pressure fluctuations.

Ob die Menge des über die Blendenöffnung 14 strömenden Druckmittels konstant gehalten wird, oder das Druckgefälle, ist für die Steuervorrichtung 17 ohne Bedeutung. Dies spielt auch für viele Anwendungsfälle keine Rolle, sondern entscheidend ist das Aufrechterhalten einer bestimmten Größe der Blendenöffnung 14. Soll auch die Menge konstant gehalten werden, so kann dazu die Druckwaage 26 in üblicher Weise benutzt werden.It is irrelevant for the control device 17 whether the amount of pressure medium flowing through the orifice 14 is kept constant or the pressure drop. This is also irrelevant for many applications, but what is crucial is maintaining a certain size Diaphragm opening 14. If the quantity should also be kept constant, the pressure compensator 26 can be used in the usual way.

Fig. 3 und 4 zeigt zwei Möglichkeiten zur Ausbildung der Blende. Fig. 3 zeigt die in Fig. 1 gezeigte Blende in symbolhafter Darstellung, wobei die Feder 9 dafür sorgt, daß in Nullstellung die Blende 1 ihre volle Öffnungsstellung einnimmt.3 and 4 show two ways of forming the aperture. Fig. 3 shows the aperture shown in Fig. 1 in a symbolic representation, wherein the spring 9 ensures that the aperture 1 assumes its full open position in the zero position.

Bei der Ausführungsform der Blende 1ʹ gemäß Fig. 4 ist hingegen vorgesehen, daß die Blende in Nullstellung ihre volle Schließstellung einnimmt,in der die Verbindung von der Zulaufleitung zur Ablaufleitung unterbrochen ist. Grundvoraussetzung für das einwandfreie Funktionieren der Steuervorrichtung ist es, daß der Druck PA und somit der Druck in der Zulaufleitung 4 größer oder gleich ist der Summe aus dem Druck PB entsprechend dem Druck B in der Ablaufleitung 5 zuzüglich der maximalen Druckdifferenz, die das Dreiwege-Vorsteuerventil 20 zu verarbeiten vermag. Der in der Leitung 18 herrschende Druck PX ergibt sich aus der Summe des Druckes PB in der Leitung 19 (entsprechend dem Druck B in der Ablaufleitung 5) und der jeweiligen Druckdifferenz des Dreiwege-Vorsteuerventils 20, d.h., der Druckdifferenz zwischen dem Druck PX und dem Druck PB.In the embodiment of the orifice 1ʹ according to FIG. 4, on the other hand, it is provided that the orifice assumes its full closed position in the zero position, in which the connection from the inlet line to the outlet line is interrupted. The basic prerequisite for the proper functioning of the control device is that the pressure P A and thus the pressure in the inlet line 4 is greater than or equal to the sum of the pressure P B corresponding to the pressure B in the outlet line 5 plus the maximum pressure difference that the three-way Pilot valve 20 can process. The pressure P X prevailing in the line 18 results from the sum of the pressure P B in the line 19 (corresponding to the pressure B in the discharge line 5) and the respective pressure difference of the three-way pilot valve 20, ie the pressure difference between the pressure P. X and the pressure P B.

Wichtig ist auch, daß das Dreiwege-Vorsteuerventil in der Nullstellung praktisch ohne Leckverluste arbeitet, so daß es z.B. bei Gabel- oder Hubstaplern problemlos eingesetzt werden kann.It is also important that the three-way pilot valve works practically without leakage losses in the zero position, so that it e.g. can easily be used with forklifts or forklifts.

Claims (7)

1. Hydraulische Steuervorrichtung mit einer Blende (1) mit einer hydraulisch verstellbaren Blendenöffnung (14) zwischen einer Zulauf- und einer Ablaufleitung (4,5), mit einem Dreiwege-Vorsteuerventil (20), dessen Ventilelement (23) mit einem externen Stellglied (24) in Verbindung steht, und das mit seinem Eingang an eine Zulaufsteuerdruckleitung (16) und mit seinem Steueranschluß an eine Kammer (10) der Blende (1) angeschlossen ist, in der ein Blendenelement (7) entgegen dem Druck in der Ablaufleitung (5) und der Kraft einer Feder (9) beaufschlagbar ist, dadurch gekennzeichnet, daß der zweite Ausgang des Dreiwege-Vorsteuerventils (20) mit der Ablaufleitung (5) verbunden ist, daß das Ventilelement (23) des Dreiwege-Vorsteuerventils (20) entgegen der Stellkraft des externen Stellgliedes (24) vom Druck im Steueranschluß und in der entgegengesetzten Richtung vom Druck im zweiten Ausgang des Dreiwege-Vorsteuerventils (20) beaufschlagt wird, und daß der Druck in der Zulaufleitung (4) um mindestens den maximalen Wert der möglichen Druckdifferenz zwischen dem Druck im Steueranschluß und dem Druck im zweiten Ausgang größer ist als der Druck in der Ablaufleitung (5). 1. Hydraulic control device with an orifice (1) with a hydraulically adjustable orifice (14) between an inlet and an outlet line (4,5), with a three-way pilot valve (20), the valve element (23) with an external actuator ( 24) is connected, and which is connected with its input to an inlet control pressure line (16) and with its control connection to a chamber (10) of the orifice (1), in which an orifice element (7) counteracts the pressure in the outlet line (5 ) and the force of a spring (9) can be applied, characterized in that the second outlet of the three-way pilot valve (20) is connected to the drain line (5), that the valve element (23) of the three-way pilot valve (20) counteracts the Actuating force of the external actuator (24) from the pressure in the control connection and in the opposite direction from Pressure in the second outlet of the three-way pilot valve (20) is applied, and that the pressure in the feed line (4) is greater than the pressure in the by at least the maximum value of the possible pressure difference between the pressure in the control connection and the pressure in the second outlet Drain pipe (5). 2. Hydraulische Steuervorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß das Dreiwege-Vorsteuerventil (20) ein Druckminderventil ist, dessen Tankausgang mit der Ablaufleitung (5) verbunden ist. 2. Hydraulic control device according to claim 1, characterized in that the three-way pilot valve (20) is a pressure reducing valve, the tank outlet of which is connected to the drain line (5). 3. Hydraulische Steuervorrichtung nach den Ansprüchen 1 und 2, dadurch gekennzeichnet, daß am Ventilelement (23) des Dreiwege-Vorsteuerventils (20) parallel zum Druck im Steueranschluß eine schwache Nullstellungsfeder (21) wirksam ist. 3. Hydraulic control device according to claims 1 and 2, characterized in that a weak zero position spring (21) is effective on the valve element (23) of the three-way pilot valve (20) parallel to the pressure in the control connection. 4. Hydraulische Steuervorrichtung nach wenigstens einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß das externe Stellglied (24) ein Proportionalmagnet mit zur Strombeaufschlagung proportionaler Stellkraft ist, und daß die Druckdifferenz zwischen dem Druck im Steueranschluß und dem Druck im zweiten Ausgang des Dreiwege-Vorsteuerventils (20) der jeweiligen Stellkraft des Proportionalmagneten proportional ist. 4. Hydraulic control device according to at least one of claims 1 to 3, characterized in that the external actuator (24) is a proportional magnet with actuating force proportional to the current applied, and that the pressure difference between the pressure in the control connection and the pressure in the second output of the three-way Pilot valve (20) of the respective actuating force of the proportional magnet is proportional. 5. Hydraulische Steuervorrichtung nach wenigstens einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß das Blendenelement (7) unter der Kraft der Feder (9) in eine Schließstellung der Blendenöffnung (14) bewegbar ist. 5. Hydraulic control device according to at least one of claims 1 to 4, characterized in that the diaphragm element (7) under the force of the spring (9) is movable into a closed position of the diaphragm opening (14). 6. Hydraulische Steuervorrichtung nach wenigstens einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß das Blendenelement (7) unter der Kraft der Feder (9) in eine volle Öffnungsstellung der Blendenöffnung (14) bewegbar ist. 6. Hydraulic control device according to at least one of claims 1 to 4, characterized in that the diaphragm element (7) under the force of the spring (9) in a fully open position of the diaphragm opening (14) movable is. 7. Hydraulische Steuervorrichtung nach wenigstens einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die Blende (1) die Regelblende einer Druckwaage (26) ist. 7. Hydraulic control device according to at least one of claims 1 to 6, characterized in that the diaphragm (1) is the regulating diaphragm of a pressure compensator (26).
EP87105284A 1986-04-15 1987-04-09 Hydraulic control device Expired - Lifetime EP0241870B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87105284T ATE71191T1 (en) 1986-04-15 1987-04-09 HYDRAULIC CONTROL DEVICE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863612684 DE3612684A1 (en) 1986-04-15 1986-04-15 HYDRAULIC CONTROL DEVICE
DE3612684 1986-04-15

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EP0241870A2 true EP0241870A2 (en) 1987-10-21
EP0241870A3 EP0241870A3 (en) 1989-10-25
EP0241870B1 EP0241870B1 (en) 1992-01-02

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US (1) US4744542A (en)
EP (1) EP0241870B1 (en)
JP (1) JP2667827B2 (en)
AT (1) ATE71191T1 (en)
DE (2) DE3612684A1 (en)
ES (1) ES2029234T3 (en)
GR (1) GR3003832T3 (en)

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US5097857A (en) * 1991-08-02 1992-03-24 John Mayhew Electro-hydraulic valve-actuator system
GB9420394D0 (en) * 1994-10-10 1994-11-23 Trinova Ltd An hydraulic circuit controlling an actuator
US5654885A (en) * 1995-03-28 1997-08-05 Virginia Valve Company Corporation Valve position controller
US6354327B1 (en) 2000-07-31 2002-03-12 Virginia Valve Company Automatic position-control valve assembly
EP1796948B1 (en) * 2004-09-28 2008-03-19 ixetic Bad Homburg GmbH Steering boost system
DE102014008648A1 (en) * 2014-06-13 2015-12-17 Hydac Technology Gmbh connection device
DE102016206092A1 (en) * 2016-04-12 2017-10-12 Robert Bosch Gmbh 3-way valve
CN110725823B (en) * 2019-10-11 2021-07-16 太原理工大学 Plug-in type two-stage proportional speed regulating valve based on pressure flying rate detector

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DE2914196A1 (en) * 1979-04-07 1980-10-23 Rexroth Gmbh G L Control valve for pressurised medium - has main piston controlling through-flow bore and servo piston pushing operating element
DE3047144A1 (en) * 1980-02-25 1981-09-10 Veb Kombinat Orsta-Hydraulik, Ddr 7010 Leipzig Hydraulically-controlled hydraulic system resistance - has valve spring chamber connected to inlet and to pilot valve chamber
DE3124904A1 (en) * 1980-07-04 1982-05-06 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Flow valve with a hydraulically adjustable choke valve

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Also Published As

Publication number Publication date
DE3612684C2 (en) 1988-09-29
JPS62269211A (en) 1987-11-21
GR3003832T3 (en) 1993-03-16
EP0241870A3 (en) 1989-10-25
ES2029234T3 (en) 1992-08-01
ATE71191T1 (en) 1992-01-15
DE3612684A1 (en) 1987-10-22
EP0241870B1 (en) 1992-01-02
JP2667827B2 (en) 1997-10-27
US4744542A (en) 1988-05-17
DE3775594D1 (en) 1992-02-13

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