EP0047885B1 - Flow control valve arrangement - Google Patents

Flow control valve arrangement Download PDF

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Publication number
EP0047885B1
EP0047885B1 EP81106571A EP81106571A EP0047885B1 EP 0047885 B1 EP0047885 B1 EP 0047885B1 EP 81106571 A EP81106571 A EP 81106571A EP 81106571 A EP81106571 A EP 81106571A EP 0047885 B1 EP0047885 B1 EP 0047885B1
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EP
European Patent Office
Prior art keywords
pressure
valve
line
inlet
pilot
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.)
Expired
Application number
EP81106571A
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German (de)
French (fr)
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EP0047885A1 (en
Inventor
Walter Wohlrab
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Mannesmann Demag Krauss Maffei GmbH
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Krauss Maffei AG
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Publication date
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Priority to AT81106571T priority Critical patent/ATE6168T1/en
Publication of EP0047885A1 publication Critical patent/EP0047885A1/en
Application granted granted Critical
Publication of EP0047885B1 publication Critical patent/EP0047885B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2579—Flow rate responsive
    • Y10T137/2589—Pilot valve operated
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2579—Flow rate responsive
    • Y10T137/2594—Choke

Definitions

  • the invention relates to a three-way flow control valve arrangement according to the preamble of the main claim.
  • the flow rate in the throttle valve is determined by the pressure drop between its inlet and outlet, which in turn corresponds to the pressure force of the spring, which acts on the control surface of the pressure compensator acts, which is also acted upon by the pressure from the control line connected to the output of the throttle valve.
  • this valve arrangement has the disadvantage that with different delivery capacities for the inlet flow, such as result, for example, from the connection of a further delivery pump, the pressure drop, in particular in the line leading to the overflow valve, changes greatly, and thus the flow through the throttle valve and its supply and discharge line acting pressure drop is raised. The result is a larger flow rate caused by the higher pressure drop.
  • the invention is therefore based on the object to provide a three-way flow control valve arrangement with simple means, which ensures the constancy of the flow rate regardless of external operating and interference.
  • the known three-way flow control valve arrangement according to FIG. 1 has a throttle valve 1 designed as a 2/2-way valve, which is connected to an inlet line 2 carrying an inlet flow and to an outlet line 3 carrying a constant current.
  • the inflow flow is conveyed from a tank 4 by a first pump 5 into the inflow line 2, the delivery rate of a second pump 6 also being able to be switched on as required.
  • a branch 7 of the inlet line 2 is connected to an overflow valve 8 with a pressure compensator 9 which, in the position shown, blocks the flow of an excess flow into an overflow line 10 leading to the tank 4.
  • the pressure compensator 9 has two control surfaces 11 and 12 of the same size, of which one control surface 11 is acted upon by the inlet flow and the other control surface 12 by the pressure medium of a control line 13, which is led from the outlet line 3 to the overflow valve 8, and by the pressure of a spring 14, whose pressure force determines the pressure drop in the throttle valve 1.
  • an input pressure measuring line 16 is connected directly to the inlet 15 of the throttle valve 1 and an output pressure measuring line 18 is connected directly to the outlet 17.
  • the input pressure measurement line 16 branches into a branch line 19, an input line 20 and into the control line 13 leading to the control surface 12 of the pressure compensator 9.
  • the input pressure measurement lines 16 have their branches and the output pressure measuring line 18 are only measuring lines with a small cross-section.
  • the pressure compensator 9 is designed as a 2/2 slide valve or 2/2 seat valve with an area ratio of 1: 1.
  • the input line 20 is connected to a pilot valve 21, also designed as a 2/2-way valve, which has a double-acting control piston with two pilot valves 22 and 23 of the same size, one pilot valve 22 to the branch pipe 19 and the other pilot valve 23 to the output Pressure measuring line 18 are connected.
  • the pilot control surface 23 is also acted upon by a pilot control spring 24, the compressive force of which determines the pressure drop that occurs in the throttle valve 1.
  • An outlet line 25 leads from the pilot valve 21 to a container with a low pressure level, for example into the outlet pressure measuring line 18. However, the outlet line 25 can also open into the tank 4.
  • orifices 26 are arranged in the branch line 19, in the input line 20 leading to the pilot valve 21 and in the control line 13.
  • the pressure compensator 9 is controlled via the control line 13 branching off from the input pressure measurement line 16 so that the pressure difference at the connections of the input and output pressure measurement lines 16 and 18 at the throttle valve 1 is the value specified by the pilot spring 24 of the pilot valve 21 corresponds. Due to the fact that the connections are located directly at the inlet 15 and outlet 17 of the throttle valve 1, interference can occur in the inlet line 2 and its branch 7 to the overflow valve 8 and in the outlet line 3, as they result from the throttling action of these lines especially when switching on additional delivery quantities (pumps 5 and 6), no longer adversely affect the constancy of the flow rate through the throttle valve 1. The pressure difference between inlet 15 and outlet 17 is thus maintained within narrow limits, as a result of which a constant flow rate can be guaranteed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Flow Control (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Servomotors (AREA)

Abstract

A three-way or three-ported flow-regulating valve for use in a hydraulic system comprises a two-position two-ported throttle valve inserted between an inflow conduit and an outflow conduit and a pressure-relief valve connected to the inflow conduit at an upstream point thereof and at a downstream point proximate to an intake port of the throttle valve. A servovalve is connected in parallel to the throttle valve via small-diameter pressure-transmission channels extending to the intake port and to an output port of the throttle valve. Upon a jump in the pressurization of the inflow conduit, for example due to the activation of an auxiliary pump, the pressure-relief valve opens; it closes again only upon an equalization of the pressure throughout the inflow conduit. The servovalve has a biasing spring which exerts a force determining the maximum pressure drop across the throttle valve.

Description

Die Erfindung bezieht sich auf eine Drei-Wege-Stromregelventilanordnung nach dem Oberbegriff des Hauptanspruchs.The invention relates to a three-way flow control valve arrangement according to the preamble of the main claim.

Bei einer derartigen Stromregelventilanordnung (siehe z. B. DE-A-2 049 884) bestimmt sich die Durchflußmenge im Drosselventil nach dem Druckgefälle, das zwischen dessen Eingang und Ausgang herrscht und das wiederum der Druckkraft der Feder entspricht, die auf die Steuerfläche der Druckwaage wirkt, die auch vom Druck aus der an den Ausgang des Drosselventils angeschlossenen Steuerleitung beaufschlagt wird.With such a flow control valve arrangement (see e.g. DE-A-2 049 884), the flow rate in the throttle valve is determined by the pressure drop between its inlet and outlet, which in turn corresponds to the pressure force of the spring, which acts on the control surface of the pressure compensator acts, which is also acted upon by the pressure from the control line connected to the output of the throttle valve.

Diese Ventilanordnung hat jedoch den Nachteil, daß sich bei unterschiedlichen Förderleistungen für den Zulaufstrom, wie sie sich beispielsweise durch das Zuschalten einer weiteren Förderpumpe ergeben, das Druckgefälle insbesondere in der zum Überströmventil führenden Leitung stark ändert und somit das zum Durchströmen des Drosselventils und dessen Zu- und Abführleitung wirkende Druckgefälle angehoben wird. Die Folge ist eine durch das höhere Druckgefälle hervorgerufene größere Durchflußmenge.However, this valve arrangement has the disadvantage that with different delivery capacities for the inlet flow, such as result, for example, from the connection of a further delivery pump, the pressure drop, in particular in the line leading to the overflow valve, changes greatly, and thus the flow through the throttle valve and its supply and discharge line acting pressure drop is raised. The result is a larger flow rate caused by the higher pressure drop.

Der Erfindung liegt daher die Aufgabe zugrunde, mit einfachen Mitteln eine Drei-Wege-Stromregelventilanordnung zu schaffen, die unabhängig von äußeren Betriebs- und Störeinflüssen die Konstanz der Durchflußmenge gewährleistet.The invention is therefore based on the object to provide a three-way flow control valve arrangement with simple means, which ensures the constancy of the flow rate regardless of external operating and interference.

Diese Aufgabe wird durch eine gemäß dem Kennzeichen des Hauptanspruchs ausgestaltete Drei-Wege-Stromregelventilanordnung gelöst, wobei sich der besondere Vorteil ergibt, daß zum Aufbau des Stromreglers handelsübliche 2/2-Wegeventile verwendet werden können.This object is achieved by a three-way flow control valve arrangement designed in accordance with the characterizing part of the main claim, with the particular advantage that commercially available 2/2-way valves can be used to construct the flow controller.

Weitere Vorteile und Merkmale ergeben sich aus der nachfolgenden Beschreibung eines Ausführungsbeispiels an Hand der Zeichnung und in Verbindung mit dem Anspruch.Further advantages and features emerge from the following description of an exemplary embodiment using the drawing and in conjunction with the claim.

Es zeigen

  • Figur 1 ein Blockschaltbild einer Drei-Wege-Stromregelventilanordnung nach dem Stande der Technik,
  • Figur 2 ein die Wirkungsweise der Drei-Wege-Stromregelventilanordnung nach Fig. 1 veranschaulichendes Diagramm,
  • . Figur 3 ein Blockschaltbild einer erfindungsgemäßen Ausführungsform einer Drei-Wege-Stromregelventilanordnung und
  • Figur 4 ein die Wirkungsweise der Drei-Wege-Stromregelventilanordnung nach Fig.3 veranschaulichendes Diagramm.
Show it
  • FIG. 1 shows a block diagram of a three-way flow control valve arrangement according to the prior art,
  • FIG. 2 shows a diagram illustrating the mode of operation of the three-way flow control valve arrangement according to FIG. 1,
  • . Figure 3 is a block diagram of an embodiment of a three-way flow control valve arrangement and
  • 4 shows a diagram illustrating the mode of operation of the three-way flow control valve arrangement according to FIG.

Die bekannte Drei-Wege-Stromregelventilanordnung nach Fig. 1 weist ein als 2/2-Wegeventil ausgebildetes Drosselventil 1 auf, das an eine, einen Zulaufstrom führende Zulaufleitung 2 und an eine, einen Konstantstrom führende Ablaufleitung 3 angeschlossen ist. Der Zulaufstrom wird aus einem Tank 4 von einer ersten Pumpe 5 in die Zulaufleitung 2 gefördert, wobei noch die Fördermenge einer zweiten Pumpe 6 bedarfsweise zuschaltbar ist. Eine Abzweigung 7 der Zulaufleitung 2 ist an ein Überströmventil 8 mit einer Druckwaage 9 angeschlossen, die in der dargestellten Position den Durchfluß eines Überschußstromes in eine zum Tank 4 führende Überströmleitung 10 sperrt. Die Druckwaage 9 weist zwei gleichgroße Steuerflächen 11 und 12 auf, von denen die eine Steuerfläche 11 vom Zulaufstrom beaufschlagt wird und die andere Steuerfläche 12 vom Druckmedium einer Steuerleitung 13, die von der Ablaufleitung 3 zum Überströmventil8 geführt ist, sowie vom Druck einer Feder 14, deren Druckkraft das im Drosselventil 1 sich einstellende Druckgefälle bestimmt.The known three-way flow control valve arrangement according to FIG. 1 has a throttle valve 1 designed as a 2/2-way valve, which is connected to an inlet line 2 carrying an inlet flow and to an outlet line 3 carrying a constant current. The inflow flow is conveyed from a tank 4 by a first pump 5 into the inflow line 2, the delivery rate of a second pump 6 also being able to be switched on as required. A branch 7 of the inlet line 2 is connected to an overflow valve 8 with a pressure compensator 9 which, in the position shown, blocks the flow of an excess flow into an overflow line 10 leading to the tank 4. The pressure compensator 9 has two control surfaces 11 and 12 of the same size, of which one control surface 11 is acted upon by the inlet flow and the other control surface 12 by the pressure medium of a control line 13, which is led from the outlet line 3 to the overflow valve 8, and by the pressure of a spring 14, whose pressure force determines the pressure drop in the throttle valve 1.

Die Wirkungsweise der bekannten Drei-Wege-Stromregelventilanordnung geht aus dem Diagramm aus Fig. 2 hervor, in dem die Durchflußmenge Y durch das Drosselventil 1 in Abhängigkeit von der Öffnung X des Drosselventils 1 aufgetragen ist. Daraus wird deutlich, daß sich zum Zeitpunkt Z, an dem zu der von der ersten Pumpe 5 geförderten Fördermenge Qi noch die Fördermenge Q2 der zweiten Pumpe 6 in die Zulaufleitung 2 eingeleitet wird, der Mengendurchsatz durch das Drosselventil in unerwünschter Weise sprunghaft erhöht. Diese Erhöhung des Durchsatzes rührt von einem starken Druckanstieg her, der sich insbesondere in der Abzweigung 7 der Zulaufleitung 2 einstellt, wodurch das zum Durchströmen der zum Drosselventil 1 führenden Zulaufleitung 2, des Drosselventils 1 und der Ablaufleitung 3 wirkende Druckgefälle angehoben wird. Die Konstanz der Durchflußmenge ist nicht mehr gegeben.The mode of operation of the known three-way flow control valve arrangement can be seen from the diagram in FIG. 2, in which the flow rate Y through the throttle valve 1 is plotted as a function of the opening X of the throttle valve 1. It is clear from this that at the time Z, at which the delivery rate Q 2 of the second pump 6 is introduced into the feed line 2 at the delivery rate Q i delivered by the first pump 5, the flow rate through the throttle valve increases in an undesirable manner. This increase in the throughput stems from a sharp rise in pressure which occurs in particular in the branch 7 of the inlet line 2, as a result of which the pressure drop acting to flow through the inlet line 2 leading to the throttle valve 1, the throttle valve 1 and the outlet line 3 is increased. The flow rate is no longer constant.

In der in Fig. 3 dargestellten Ausführungsform der Erfindung sind unmittelbar am Eingang 15 des Drosselventils 1 eine Eingangs-Druckmeßleitung 16 und unmittelbar am Ausgang 17 eine Ausgangs-Druckmeßleitung 18 angeschlossen. Die Eingangs-Druckmeßleitung 16 verzweigt sich in eine Zweigleitung 19, eine Eingangsleitung 20 und in die zur Steuerfläche 12 der Druckwaage 9 führende Steuerleitung 13. Im Gegensatz zu den leistungsführenden Zulauf- und Ablaufleitungen 2 bzw. 3 stellen die Eingangs-Druckmeßleitungen 16 mit ihren Verzweigungen und die Ausgangs-Druckmeßleitung 18 lediglich Meßleitungen mit niedrigem Querschnitt dar.In the embodiment of the invention shown in FIG. 3, an input pressure measuring line 16 is connected directly to the inlet 15 of the throttle valve 1 and an output pressure measuring line 18 is connected directly to the outlet 17. The input pressure measurement line 16 branches into a branch line 19, an input line 20 and into the control line 13 leading to the control surface 12 of the pressure compensator 9. In contrast to the power supply and discharge lines 2 and 3, the input pressure measurement lines 16 have their branches and the output pressure measuring line 18 are only measuring lines with a small cross-section.

Die Druckwaage 9 ist als 2/2 Schieber- bzw. 2/2 Sitzventil mit einem Flächenverhältnis von 1 : 1 ausgebildet. Die Eingangsleitung 20 ist an ein ebenfalls als 2/2-Wegeventil ausgebildetes Vorsteuerventil 21 angeschlossen, das einen doppeltwirkenden Steuerkolben mit zwei gleichgroßen Vorsteuerflächen 22 und 23 aufweist, von denen die eine Vorsteuerfläche 22 an die Zweigieitung 19 und die andere Vorsteuerfläche 23 an die Ausgangs-Druckmeßleitung 18 angeschlossen sind. Die Vorsteuerfläche 23 ist ferner von einer Vorsteuerungsfeder 24 beaufschlagt, deren Druckkraft das im Drosselventil 1 sich einstellende Druckgefälle bestimmt. Im Gegensatz zu dem bekannten Stromregelventil nach Fig. erfordert die auf die Steuerfläche 12 der Druckwaage 9 wirkende Feder 14 nur noch eine geringe Druckkraft, die zur Rückstellung der Druckwaage 9 bei Druckgleichheit an den beiden Steuerflächen 11 und 12 ausreicht. Vom Vorsteuerventil 21 führt eine Ausgangsleitung 25 zu einem Behälter mit niedrigem Druckniveau, beispielsweise in die Ausgangs-Druckmeßleitung 18. Die Ausgangsleitung 25 kann jedoch auch in den Tank 4 einmünden. Zur Dämpfung der Hydraulikflüssigkeit sind in der Zweigleitung 19, in der zum Vorsteuerventil 21 führenden Eingangsleitung 20 und in der Steuerleitung 13 Blenden 26 angeordnet.The pressure compensator 9 is designed as a 2/2 slide valve or 2/2 seat valve with an area ratio of 1: 1. The input line 20 is connected to a pilot valve 21, also designed as a 2/2-way valve, which has a double-acting control piston with two pilot valves 22 and 23 of the same size, one pilot valve 22 to the branch pipe 19 and the other pilot valve 23 to the output Pressure measuring line 18 are connected. The pilot control surface 23 is also acted upon by a pilot control spring 24, the compressive force of which determines the pressure drop that occurs in the throttle valve 1. In Ge Contrary to the known flow control valve according to FIG. The spring 14 acting on the control surface 12 of the pressure compensator 9 only requires a small pressure force which is sufficient to reset the pressure compensator 9 when the pressure on the two control surfaces 11 and 12 is equal. An outlet line 25 leads from the pilot valve 21 to a container with a low pressure level, for example into the outlet pressure measuring line 18. However, the outlet line 25 can also open into the tank 4. To dampen the hydraulic fluid, orifices 26 are arranged in the branch line 19, in the input line 20 leading to the pilot valve 21 and in the control line 13.

Im Betrieb wird die Druckwaage 9 über die von der Eingangs-Druckmeßleitung 16 abzweigende Steuerleitung 13 so angesteuert, daß die Druckdifferenz an den Anschlüssen der Eingangs- und der Ausgangs-Druckmeßteitung 16 und 18 am Drosselventil 1 dem von der Vorsteuerfeder 24 des Vorsteuerventils 21 vorgegebenen Wert entspricht. Auf Grund der Tatsache, daß sich die Anschlüsse unmittelbar am Eingang 15 und am Ausgang 17 des Drosselventils 1 befinden, können sich Störeinflüsse in der Zulaufleitung 2 sowie deren Abzweigung 7 zum Überströmventil 8 und in der Ablaufleitung 3, wie sie sich infolge der Drosselwirkung dieser Leitungen insbesondere beim Zuschalten von zusätzlichen Fördermengen (Pumpen 5 und 6) einstellen, nicht mehr nachteilig auf die Konstanz des Mengendurchsatzes durch das Drosselventil 1 auswirken. Die Druckdifferenz zwischen Eingang 15 und Ausgang 17 wird somit in engen Grenzen eingehalten, wodurch ein konstanter Mengendurchsatz gewährleistet werden kann. Diese Betriebseigenschaft wird durch die Kennlinie des Diagramms nach der Fig. 4 verdeutlicht. Danach bleibt im Drosselventil 1 die Konstanz der Durchflußmenge erhalten, auch wenn zum Zeitpunkt Z' zu der von der ersten Pumpe 5 geförderten Fördermenge Q1 noch die Fördermenge Q2 der zweiten. Pumpe 6 in die Zulaufleitung 2 eingeleitet wird.In operation, the pressure compensator 9 is controlled via the control line 13 branching off from the input pressure measurement line 16 so that the pressure difference at the connections of the input and output pressure measurement lines 16 and 18 at the throttle valve 1 is the value specified by the pilot spring 24 of the pilot valve 21 corresponds. Due to the fact that the connections are located directly at the inlet 15 and outlet 17 of the throttle valve 1, interference can occur in the inlet line 2 and its branch 7 to the overflow valve 8 and in the outlet line 3, as they result from the throttling action of these lines especially when switching on additional delivery quantities (pumps 5 and 6), no longer adversely affect the constancy of the flow rate through the throttle valve 1. The pressure difference between inlet 15 and outlet 17 is thus maintained within narrow limits, as a result of which a constant flow rate can be guaranteed. This operating characteristic is illustrated by the characteristic curve of the diagram according to FIG. 4. Thereafter, the flow rate remains constant in the throttle valve 1, even if the delivery rate Q 2 of the second is still at the time Z ′ for the delivery rate Q 1 delivered by the first pump 5. Pump 6 is introduced into the feed line 2.

Claims (1)

  1. A three-way flow control valve arrangement comprising a choke valve (1) for supplying an adjustable but regular flow, said valve being acted upon by a variable rate system flow (2), and a pressure relief valve (8) driven by a pressure balance member (9) for producing an excess flow from the said system flow, wherein the pressure balance member (9) has two driving faces (11 and 12) acting in opposite directions, and of which the one (11) is acted upon by pressure from the system flow (2) and the other is acted upon by the pressing force of a spring (14) and by the pressure of a control line (13) joining up therewith, characterized by
    - a inlet pressure measuring line (16) that is joined up directly with the inlet (15) of the choke valve (1), more specially with its inlet control edge,
    - an outlet pressure measuring line (18) that-is joined up directly with the outlet (17) of the choke valve (1) and more specially with its outlet control edge,
    - a pilot control valve (21) with a double acting driving piston having pilot driving faces (22 and 23) of equal size, one pilot face (22) being acted upon by the pressure from the inlet pressure measuring line(16), said other driving face (22) being acted upon by the pressure from the outlet pressure measuring line (18) and by the pressing force of a pilot driving spring (24), said spring controlling in the choke valve (1) the pressure gradient coming into being between the inlet (15) and the outlet (17),
    - and a branch duct from the inlet pressure measuring line (16) running (a) into the branch duct (19) joining up with the pilot driving face (22), (b) into an inlet line (20) joined up with the pilot valve (21), said inlet line (20) opening downstream from the pilot driving valve (21) as an outlet line (25) into a vessel with a low pressure level, and more specially into the reservoir (4) of the hydraulic system, and (c) into the control line (13) running to the driving face (12) of the pressure balance member (9), wherein the pressing force of the spring (14) acting on the driving face (12) gives a returning force moving the pressure balance member (9) into the shut position when the pressure at the two driving faces (11 and 12) is equal.
EP81106571A 1980-09-12 1981-08-25 Flow control valve arrangement Expired EP0047885B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT81106571T ATE6168T1 (en) 1980-09-12 1981-08-25 FLOW CONTROL VALVE ARRANGEMENT.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3034377 1980-09-12
DE19803034377 DE3034377A1 (en) 1980-09-12 1980-09-12 FLOW CONTROL VALVE

Publications (2)

Publication Number Publication Date
EP0047885A1 EP0047885A1 (en) 1982-03-24
EP0047885B1 true EP0047885B1 (en) 1984-02-08

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EP81106571A Expired EP0047885B1 (en) 1980-09-12 1981-08-25 Flow control valve arrangement

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US (1) US4365645A (en)
EP (1) EP0047885B1 (en)
JP (1) JPS5779369A (en)
AT (1) ATE6168T1 (en)
DE (1) DE3034377A1 (en)

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JPH0423122B2 (en) 1992-04-21
DE3034377C2 (en) 1989-03-02
JPS5779369A (en) 1982-05-18
DE3034377A1 (en) 1982-04-22
EP0047885A1 (en) 1982-03-24
ATE6168T1 (en) 1984-02-15
US4365645A (en) 1982-12-28

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