EP0432606B1 - Proportional directional valve with position control - Google Patents

Proportional directional valve with position control Download PDF

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Publication number
EP0432606B1
EP0432606B1 EP19900123084 EP90123084A EP0432606B1 EP 0432606 B1 EP0432606 B1 EP 0432606B1 EP 19900123084 EP19900123084 EP 19900123084 EP 90123084 A EP90123084 A EP 90123084A EP 0432606 B1 EP0432606 B1 EP 0432606B1
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EP
European Patent Office
Prior art keywords
piston
valve
control
centring
main control
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Expired - Lifetime
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EP19900123084
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German (de)
French (fr)
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EP0432606A1 (en
Inventor
Hans Schwelm
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Hydrolux SARL
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Hydrolux SARL
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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
    • 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • F15B13/0435—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being sliding valves
    • 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • F15B13/0433—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being pressure control valves
    • 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
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • Y10T137/86614—Electric

Definitions

  • the invention relates to a position-controlled proportional directional control valve for use in hydraulic systems, in particular a proportional directional control valve with a main control piston and two coaxial piston collars connected in one piece with it for optionally controlling a first or second working line.
  • the conventional position-controlled proportional directional control valves for the stated purpose work with a direction sensor which continuously detects the position of a main control piston and converts it into a control voltage U x .
  • a setpoint value U w -actual value U x comparison is carried out externally by means of control electronics and a pilot valve is excited with a current signal corresponding to the control deviation and the main control piston is adjusted against the control deviation.
  • pilot servo valves which are not spring-centered. This means that their position is dependent on the current. In the event of a power failure, it is impossible to center the main spool in the middle position if control oil pressure is still available. In the event of a power failure, a connected hydraulic device would not be able to be stopped.
  • a regulatable or controllable hydraulic servo valve according to the preamble of claims 1 and 6 is known.
  • Two-piece servo control pistons controlled by control magnets are each mechanically connected to a spring plate in an actuation chamber by means of feedback springs.
  • the spring plates are drilled axially, so that the hydraulic fluid in the actuation chambers acts directly on the two equally large piston faces of the main control piston.
  • Spring centering of the main control piston is achieved by means of two additional centering springs, which are each clamped between the spring plate and a fixed abutment in the actuation chambers.
  • the main control piston is centered if the electronic control fails due to the spring forces.
  • valve according to the invention according to claim 1 or 6 is always pressure-centered in the middle position when the electronic control fails and spring-centered when the pilot pressure fails (all connections, P, T, A and B being closed in this middle position of the main control piston, so that no movement of connected hydraulic cylinders or hydraulic motors, which is very important for hydraulic presses, for example).
  • a valve according to the invention is also extremely robust, insensitive to malfunctions and reliable in operation and it is also almost impossible to adjust the functioning of the valve due to external use of force or incorrect start-up or installation.
  • the reliability for such applications is decisively improved in that the described two additional valve functions between the pilot valve and the main control stage are designed as seat valves with higher switching reliability compared to piston spool valves.
  • the seat valves used for this in detail a 3/2-way seat valve hydraulically operated by the protective door valve and an electromagnetically operated 3/2-way seat valve are known.
  • valve 2 in FIG. 1 has the usual connections P (pump connection), T (tank connection), A (first working connection), B (second working connection, Y (control connection to the tank), as well as two electrical control magnets 4 and 6, with the working line A the left pilot valve side A 'is assigned and the working line B the right pilot valve side B'.
  • the working part of the valve has a main control piston 8 in the usual way, which with two coaxial Piston collars 10, 12 is in one piece, the piston collar 10 being assigned to the working line A and the piston collar 12 being assigned to the working line B.
  • the valve additionally has left and right centering pistons 22 and 24, which are each slidably fitted in the housing, and separate left and right actuating pistons 23 and 25.
  • the left actuating piston 23 is freely movable in the centering piston 22 and in one A-side pilot chamber 14 can be pressurized.
  • the right actuating piston 25 is freely movable in the centering piston 24 and can be pressurized in a B'-side pilot chamber 16.
  • the main control piston 8 is held in its neutral central position by means of springs 18, 20, which act on the centering pistons 22, 24, when the pilot spaces 14, 16 are depressurized in the system in the event of pressure loss (spring centering).
  • both pilot chambers 14, 16 With pressure in the system (port P) and non-energized control magnets 4, 6, both pilot chambers 14, 16 are pressurized, since they are connected to the pump port via the pilot spool valves 28, 29, the pistons of which are actuated by the preloaded springs 18, 20 P A and P B are connected.
  • the two pistons of the pilot spool valves 28, 29 are axially drilled through to allow pressure compensation on both sides when shifting.
  • the centering pistons 22, 24 are pressed by the pressure in the pilot control rooms 14, 16 against their stops in the valve housing 3 with great forces, since on their rear side the annular surface 34 is relieved of pressure to the respective T-connection.
  • the main control piston 8 is thus pressure centered indirectly in a central position via the centering piston 22, 24.
  • the control magnet 4 actuates the piston of the pilot valve 28 against the restoring force of the spring 18 with its plunger 26.
  • the pilot chamber 14 is connected to Y and thus to the tank via an annular channel 32.
  • the pilot control chamber 16 is pressurized by the restoring force of the spring 20 on the piston of the pilot control slide valve 29 via an annular channel 33 connected to P B.
  • the actuating piston 25 therefore displaces the main control piston 8 against the centering flange 22 and the spring 18 supported thereon.
  • Proportional to the stroke of the main control piston 8 an additional return force is generated in the spring 18, which is returned to the pilot valve 28 via the spring plate 30 and with the tappet force of the Control magnet 4 is compared.
  • the ram force is in turn proportional to the given magnetic current.
  • the position of the main control piston 8 as a function of the magnetic current (or the magnetic force) in a closed position control loop with spring return and force comparison on the pilot valve 28 is thus reached very precisely.
  • the biasing force of the spring 18 predominates and the pilot control chamber 14 is pressurized again via the annular channel 32 of the pilot control slide valve 28. Since the total pressure force exerted on the main control piston 8 by the centering piston 22 with the actuating piston 23 contained therein is greater than the compressive force portion of the annular surface 34 by the compressive force of the sole actuating piston 25 on the opposite B ′ side (the centering piston 24 is in the housing stop), the main control piston becomes corresponding the reduction in force of the control magnet 4 is reset to a maximum of the housing stop of the centering piston 22.
  • FIG. 2 shows an embodiment of a proportional directional control valve according to the invention with a single electrical control magnet for actuating the main control piston from the central position on only one side.
  • This version is often used as a proportional throttle valve with only one flow direction.
  • the B'-side pilot valve 29 is replaced by an end cap 38 which clamps the centering piston 24.
  • the actuating piston 25 is constantly connected to the pilot control chamber 16 Pressure applied.
  • the pilot control chamber 14 is pressurized via the pilot control valve 28 which is actuated by the prestressed spring 18 to the pressure connection P A.
  • a centering piston 36 is slidably fitted in the valve housing and has a larger pressure area in the pilot control chamber 14 in relation to the actuating piston 25.
  • FIG 3 shows a longitudinal section through the proportional directional control valve according to the invention with two additional 3/2-way seat valves integrated into the hydraulic pilot control of a valve side A 'or B', which are controlled by a higher-level machine control system in accordance with the safety requirements of the machine for releasing the main control piston position specified by the control magnet must be operated.
  • a press closing movement can be carried out by opening the main control piston 8 in proportion to the actuation of the control magnet 4, a 3/2-way seat valve 39 must be actuated hydraulically with pressure via a relieved protective door valve 49 when the protective door 47 is closed.
  • an electromagnet must have switched a 3/2-way seat valve 43 so that the tank port 35 of the pilot valve 28 is depressurized through the lines 40, 41 to the tank. Only then can the main control piston 8 move through the Take the control magnet 4 in the specified position and control the closing speed of the press cylinder.
  • the safety valve which is additionally designed as an electromagnetically actuated 3/2-way seat valve 43, is connected in series with the valve 39.
  • the tank connection 35 of the pilot valve 28 is also pressurized via connection 46 even when the 3/2-way seat valve 39 is actuated, so that the main control piston in the middle layer is pressure centered.

Abstract

The main control piston (8) is controlled hydraulically by pilot control slide valves, operated in each case via two control magnets (4, 6) with force build-up proportional to the control current. In the case of failure of the electrical activation, the valve is always positioned in the center position by pressure centering and in the case of failure of the pilot control pressure it is positioned in the center position by spring centering.

Description

Die Erfindung betrifft ein lagegeregeltes Proportionalwegeventil für die Verwendung in hydraulischen Anlagen, insbesondere ein Proportionalwegeventil mit einem Hauptsteuerkolben und zwei damit einstückig verbundenen koaxialen Kolbenbünden zur wahlweisen Ansteuerung einer ersten oder zweiten Arbeitsleitung.The invention relates to a position-controlled proportional directional control valve for use in hydraulic systems, in particular a proportional directional control valve with a main control piston and two coaxial piston collars connected in one piece with it for optionally controlling a first or second working line.

Die herkömmlichen lagegeregelten Proportionalwegeventile für den genannten Zweck arbeiten mit einem Wegeaufnehmer, welcher die Stellung eines Hauptsteuerkolbens stetig erfasst und in eine Steuerspannung Ux umwandelt. Mittels einer Regelelektronik wird extern ein Sollwert Uw -Istwert Ux Vergleich durchgeführt und ein Vorsteuerventil mit einem der Regelabweichung entsprechenden Stromsignal erregt und der Hauptsteuerkolben entgegen der Regelabweichung verstellt.The conventional position-controlled proportional directional control valves for the stated purpose work with a direction sensor which continuously detects the position of a main control piston and converts it into a control voltage U x . A setpoint value U w -actual value U x comparison is carried out externally by means of control electronics and a pilot valve is excited with a current signal corresponding to the control deviation and the main control piston is adjusted against the control deviation.

Diese herkömmlichen Proportionalventile weisen, je nach Bauart, mehr oder weniger gravierende Mängel, insbesondere unter dem Sicherheitsaspekt (fail safe), auf. Da die Stellung des Hauptkolbens elektrisch überwacht wird, wird die Regelstrecke bei Leitungsbruch, Installationsfehler oder Beschädigung unterbrochen und der Hauptkolben läuft in eine der beiden Endpositionen. Erfolgt keine zusätzliche Überwachung des Wegeaufnehmers auf Kabelbruch, so nimmt der Hauptkolben somit eine unbestimmte Position ein, und eine automatische Zentrierung in Mittelstellung ist nicht sichergestellt (angeschlossene Zylinder können nicht gestoppt werden).These conventional proportional valves have, depending on the design, more or less serious defects, especially with regard to the safety aspect (fail safe). As the position of the main spool is monitored electrically, the controlled system is interrupted in the event of a line break, installation error or damage and the main spool runs in one of the two end positions. If there is no additional monitoring of the position transducer for a cable break, the main piston therefore assumes an indefinite position and automatic centering in the central position is not ensured (connected cylinders cannot be stopped).

Andere Ventilbauarten besitzen sogenannte Vorsteuerservoventile, welche nicht federzentriert sind. Das heisst, deren Position ist stromabhängig. Bei Stromausfall ist es hierbei unmöglich, den Hauptkolben in Mittelstellung zu zentrieren, falls noch Steueröldruck zur Verfügung steht. Bei Stromausfall würde ein angeschlossenes Hydraulikgerät nicht gestoppt werden können.Other valve types have so-called pilot servo valves, which are not spring-centered. This means that their position is dependent on the current. In the event of a power failure, it is impossible to center the main spool in the middle position if control oil pressure is still available. In the event of a power failure, a connected hydraulic device would not be able to be stopped.

Bei anderen Proportionalventilen sind weder Vorsteuerstufen- noch Hauptstufenkolben federkraftzentriert, so dass sie nur bei Steueröl- und gleichzeitiger Lageregelung sicher funktionstüchtig sind. Fällt nur eine von beiden Voraussetzungen aus, ist das Ventil nicht kontrollierbar in Mittelstellung zu positionieren.In the case of other proportional valves, neither the pilot stage piston nor the main stage piston are spring-force-centered, so that they can only function reliably with control oil and simultaneous position control. If only one of the two conditions fails, the valve cannot be positioned in the center position in a controllable manner.

Aus DE-A-2926547 ist ein regel- oder steuerbares hydraulisches Servoventil gemäß Oberbegriff der Ansprüche 1 und 6 bekannt. Durch Regelmagnete angesteuerte, zweiteilige Servoregelkolben sind jeweils mittels Rückführungsfedern mit einem Federteller in einer Betätigungskammer mechanisch verbunden. Die Federteller sind axial durchbohrt, so dass die Hydraulik-Flüssigkeit in den Betätigungskammern unmittelbar auf die beiden gleichgrossen Kolbenstirnflächen des Hauptsteuerkolbens wirkt. Eine Federzentrierung des Hauptsteuerkolbens wird mittels zwei zusätzlicher Zentrierfedern erreicht, welche jeweils zwischen dem Federteller und einem festen Widerlager in den Betätigungskammern eingespannt sind.From DE-A-2926547 a regulatable or controllable hydraulic servo valve according to the preamble of claims 1 and 6 is known. Two-piece servo control pistons controlled by control magnets are each mechanically connected to a spring plate in an actuation chamber by means of feedback springs. The spring plates are drilled axially, so that the hydraulic fluid in the actuation chambers acts directly on the two equally large piston faces of the main control piston. Spring centering of the main control piston is achieved by means of two additional centering springs, which are each clamped between the spring plate and a fixed abutment in the actuation chambers.

Aus DE-A-3708570 ist eine elektrohydraulische Einrichtung zum Betätigen eines Kolbens gemäß Oberbegriff der Ansprüche 1 und 6 bekannt. Ein durch einen Proportionalmagneten angesteuerten Steuerschieber ist mittels einer Messfeder mit einem Federteller in einer Steuerkammer mechanisch verbunden. Der Federteller ist mit einer Bohrung versehen, so dass die Hydraulik-Flüssigkeit in dieser Steuerkammer unmittelbar auf die Stirnfläche des Kolbens wirkt. Eine Federzentrierung des Kolbens wird mittels einer zusätzlichen Zentrierfedern erreicht, welche zwischen dem Federteller und einem festen Widerlager in der Steuerkammer eingespannt ist.From DE-A-3708570 an electro-hydraulic device for actuating a piston according to the preamble of claims 1 and 6 is known. A control slide controlled by a proportional magnet is mechanically connected to a spring plate in a control chamber by means of a measuring spring. The spring plate is provided with a hole so that the hydraulic fluid in this control chamber acts directly on the end face of the piston. Spring centering of the piston is achieved by means of an additional centering spring which is clamped between the spring plate and a fixed abutment in the control chamber.

Sowohl beim Ventil aus DE-A-2926547 als auch bei der elotrohydraulischen Stelleinrichtung aus DE-A-3708570 erfolgt die Zentrierung des Haupsteurkolbens bei Ausfall der elektronischen Ansteuerung durch die Federkräfte.Both in the valve from DE-A-2926547 and in the electro-hydraulic actuating device from DE-A-3708570, the main control piston is centered if the electronic control fails due to the spring forces.

Das erfindunsgemässe Ventil nach Anspruch 1 oder 6 ist bei Ausfall der elektronischen Ansteuerung immer druckzentriert in Mittelstellung positioniert und bei Ausfall des Vorsteuerdruckes federzentriert (wobei in dieser Mittelstellung des Hauptsteuerkolbens alle Anschlüsse, P, T, A und B verschlossen sind, so dass keine Bewegung von angeschlossenen Hydraulikzylindern oder Hydraulikmotoren erfolgen kann, was beispielsweise bei hydraulischen Pressen sehr wichtig ist). Ein erfindungsgemässes Ventil ist zudem äusserst robust, störungsunanfällig und betriebssicher und es ist auch durch äussere Gewaltanwendung, beziehungsweise, falsche Inbetriebnahme oder Installation nahezu unmöglich die Funktionsweise des Ventils zu verstellen.The valve according to the invention according to claim 1 or 6 is always pressure-centered in the middle position when the electronic control fails and spring-centered when the pilot pressure fails (all connections, P, T, A and B being closed in this middle position of the main control piston, so that no movement of connected hydraulic cylinders or hydraulic motors, which is very important for hydraulic presses, for example). A valve according to the invention is also extremely robust, insensitive to malfunctions and reliable in operation and it is also almost impossible to adjust the functioning of the valve due to external use of force or incorrect start-up or installation.

Beim Einbau dieser Proportionalwegeventilen zum Beispiel in hydraulischen Pressensteuerungen wird zwecks Unfallverhütung gefordert, dass bei Öffnen der Schutztür zum Pressenraum ein hydraulischer Steuervorgang über ein separates Schutztürventil erfolgt. Dieser Steuervorgang soll den Druckölzufluss zum Pressenzylinder durch Zurückschalten des Hauptsteuerkolbens in die Mittellage unterbrechen, so dass die Zufahrbewegung der Presse gestoppt wird. Desweiteren soll ein Zufahren der Presse nur möglich sein, wenn ein weiteres zusätzliches Elektromagnetventil durch die übergeordnete elektrische Steuerung zur Freigabe der Zufahrbewegung geschaltet wird. Nur unter diesen Umständen soll, bei gleichzeitiger Ansteuerung des Proportionalwegeventils, das Aufsteuern des Hauptsteuerkolbens möglich sein.When installing these proportional directional control valves, for example in hydraulic press controls, in order to prevent accidents, it is required that when the protective door to the press room is opened, a hydraulic control process takes place via a separate protective door valve. This control process is intended to interrupt the pressure oil flow to the press cylinder by switching the main control piston back to the central position, so that the closing movement of the press is stopped. Furthermore, it should only be possible to close the press if a further additional solenoid valve is switched by the higher-level electrical control to release the closing movement. Only under these circumstances should it be possible to open the main control spool while simultaneously controlling the proportional directional control valve.

Bisher wurden diese Forderungen durch den Einbau zusätzlicher Kolbenschieberventile zwischen Vorsteuerventil und Hauptsteuerstufe erfüllt.So far, these requirements have been met by installing additional spool valves between the pilot valve and the main control stage.

In einer besonderen Ausführungsform mit der erfindungsgemässen Lösung wird die Zuverlässigkeit für derartige Anwendungen entscheidend dadurch verbessert, dass die beschriebenen zwei zusätzlichen Ventilfunktionen zwischen Vorsteuerventil und Hauptsteuerstufe als Sitzventil mit höherer Schaltsicherheit gegenüber Kolbenschieberventilen ausgeführt sind. Die hierfür im einzelnen verwendeten Sitzventile, ein hydraulisch von dem Schutztürventil betätigtes 3/2-Wege-Sitzventil sowie ein elektromagnetisch betätigtes 3/2-Wege-Sitzventil, sind bekannt.In a special embodiment with the solution according to the invention, the reliability for such applications is decisively improved in that the described two additional valve functions between the pilot valve and the main control stage are designed as seat valves with higher switching reliability compared to piston spool valves. The seat valves used for this in detail, a 3/2-way seat valve hydraulically operated by the protective door valve and an electromagnetically operated 3/2-way seat valve are known.

Technisch neu ist erfindungsgemäss die hier dargestellte Einbindung dieser Ventile in die hydraulische Ansteuerung des druck- und federzentrierten Proportionalwegeventils so, dass mit einem Höchstmass an Funktionszuverlässigkeit die Schliessbewegung in hydraulischen Pressensteuerungen nur durch zusätzliche hydraulische und elektrische Betätigung von zwei Sitzventilen erfolgen kann.Technically new according to the invention is the integration of these valves shown here in the hydraulic control of the pressure and spring-centered proportional directional control valve in such a way that the closing movement in hydraulic press controls can only be carried out with additional hydraulic and electrical actuation of two poppet valves with maximum reliability.

Ausführungsbeispiele der Erfindung ist in der Zeichnung dargestellt und werden im folgenden näher beschrieben. Es zeigen:

  • Fig.1 : einen Längsschnitt durch ein erfindungsgemässes Ventil mit zwei elektrischen Steuermagneten.
  • Fig.2 : einen Längsschnitt durch ein erfindungsgemässes Ventil mit einem einzigen elektrischen Steuermagneten.
  • Fig.3 : Eine Ausführung eines Proportionalwegeventils mit integrierten 3/2-Wege-Sitzventilen.
Embodiments of the invention are shown in the drawing and are described in more detail below. Show it:
  • 1 shows a longitudinal section through a valve according to the invention with two electrical control magnets.
  • 2 shows a longitudinal section through a valve according to the invention with a single electrical control magnet.
  • Fig. 3: A version of a proportional directional control valve with integrated 3/2-way seat valves.

Das Ventil 2 in Figur 1 ist in seinem wesentlichen Aufbau vollkommen symmetrisch aufgebaut. Es weist die üblichen Anschlüsse P (Pumpanschluss), T (Tankanschluss), A (erster Arbeitsanschluss), B (zweiter Arbeitsanschluss, Y (Steueranschluss zum Tank), sowie zwei elektrische Steuermagnete 4 und 6 auf, wobei in der Figur 1 der Arbeitsleitung A die linke Vorsteuerventilseite A' zugeordnet ist und der Arbeitsleitung B die rechte Vorsteuerventilseite B'.The essential structure of valve 2 in FIG. 1 is completely symmetrical. It has the usual connections P (pump connection), T (tank connection), A (first working connection), B (second working connection, Y (control connection to the tank), as well as two electrical control magnets 4 and 6, with the working line A the left pilot valve side A 'is assigned and the working line B the right pilot valve side B'.

Der Arbeitsteil des Ventils besitzt in üblicher Weise einen Hauptsteuerkolben 8, welcher mit zwei koaxialen Kolbenbünden 10, 12 einstückig ist, wobei der Kolbenbund 10 der Arbeitsleitung A zugeordnet ist und der Kolbenbund 12 der Arbeitsleitung B.The working part of the valve has a main control piston 8 in the usual way, which with two coaxial Piston collars 10, 12 is in one piece, the piston collar 10 being assigned to the working line A and the piston collar 12 being assigned to the working line B.

Erfindungsgemäss weist das Ventil zusätzlich einen linken und einen rechten Zentrierkolben 22 und 24 auf, welche jeweils verschiebbar im Gehäuse eingepasst sind, sowie einen separaten linken und einen rechten Betätigungskolben 23 und 25. Der linke Betätigungskolben 23 ist frei beweglich im Zentrierkolben 22 durchgeführt und in einem A'-seitigen Vorsteuerraum 14 druckbeaufschlagbar. Der rechte Betätigungskolben 25 ist frei beweglich im Zentrierkolben 24 geführt und in einem B'-seitigen Vorsteuerraum 16 druckbeaufschlagbar. Der Hauptsteuerkolben 8 wird mittels Federn 18, 20, welche auf die Zentrierkolben 22, 24 wirken in seiner neutralen Mittellage gehalten, wenn bei Druckausfall im System die Vorsteuerräume 14, 16 drucklos sind (Federzentrierung). Bei Druck im System (Anschluss P) und nicht erregten Steuermagneten 4, 6 sind beide Vorsteuerräume 14, 16 druckbeaufschlagt, da sie über die Vorsteuerschieberventile 28, 29, deren Kolben durch die vorgespannten Federn 18, 20 jeweils nach aussen betätigt sind, mit dem Pumpenanschluss PA bzw. PB verbunden sind. Die beiden Kolben der Vorsteuerschieberventile 28, 29 sind axial durchbohrt um einen beidseitigen Druckausgleich beim Verschieben zu ermöglichen.According to the invention, the valve additionally has left and right centering pistons 22 and 24, which are each slidably fitted in the housing, and separate left and right actuating pistons 23 and 25. The left actuating piston 23 is freely movable in the centering piston 22 and in one A-side pilot chamber 14 can be pressurized. The right actuating piston 25 is freely movable in the centering piston 24 and can be pressurized in a B'-side pilot chamber 16. The main control piston 8 is held in its neutral central position by means of springs 18, 20, which act on the centering pistons 22, 24, when the pilot spaces 14, 16 are depressurized in the system in the event of pressure loss (spring centering). With pressure in the system (port P) and non-energized control magnets 4, 6, both pilot chambers 14, 16 are pressurized, since they are connected to the pump port via the pilot spool valves 28, 29, the pistons of which are actuated by the preloaded springs 18, 20 P A and P B are connected. The two pistons of the pilot spool valves 28, 29 are axially drilled through to allow pressure compensation on both sides when shifting.

Die Zentrierkolben 22, 24 werden durch den Druck in den Vorsteuerräumen 14, 16 gegen ihre Anschläge im Ventilgehäuse 3 mit grossen Kräften gedrückt, da auf ihrer Rückseite die Ringfläche 34 zum jeweiligen T-Anschluss druckentlastet ist. Der Hauptsteuerkolben 8 wird somit in einer Mittellage indirekt über die Zentrierkolben 22, 24 druckzentriert.The centering pistons 22, 24 are pressed by the pressure in the pilot control rooms 14, 16 against their stops in the valve housing 3 with great forces, since on their rear side the annular surface 34 is relieved of pressure to the respective T-connection. The main control piston 8 is thus pressure centered indirectly in a central position via the centering piston 22, 24.

Da die Funktionsweise für beide Ventilseiten A' und B' identisch ist, können die nachfolgenden Ausführungen sich im wesentlichen auf eine dieser beiden Seiten, zum Beispiel die Seite A', beschränken.Since the mode of operation is identical for both valve sides A 'and B', the following explanations may differ restrict essentially to one of these two sides, for example side A '.

Der Steuermagnet 4 betätigt mit seinem Stössel 26 den Kolben des Vorsteuerschieberventils 28 gegen die Rückstellkraft der Feder 18. Dadurch wird über einen Ringkanal 32 der Vorsteuerraum 14 mit Y und damit mit dem Tank verbunden. Der Vorsteuerraum 16 ist, durch die Rückstellkraft der Feder 20 auf den Kolben des Vorsteuerschieberventils 29, über einen mit PB verbundenen Ringkanal 33, druckbeaufschlagt. Der Betätigungskolben 25 verschiebt daher den Hauptsteuerkolben 8 gegen den Zentrierflansch 22 und die sich darauf abstützende Feder 18. Proportional zum Hub des Hauptsteuerkolbens 8 entsteht in der Feder 18 eine zusätzliche Rückführungskraft, die über den Federteller 30 auf das Vorsteuerschieberventil 28 zurückgeführt und mit der Stösselkraft des Steuermagneten 4 verglichen wird. Die Stösselkraft ist ihrerseits proportional zu dem vorgegebenen Magnetstrom. Somit wird die Position des Hauptsteuerkolbens 8 in Abhängigkeit zum Magnetstrom (bzw. zur Magnetkraft) in einem geschlossenen Lageregelkreis mit Federrückführung und Kraftvergleich am Vorsteuerschieberventil 28 sehr genau erreicht.The control magnet 4 actuates the piston of the pilot valve 28 against the restoring force of the spring 18 with its plunger 26. As a result, the pilot chamber 14 is connected to Y and thus to the tank via an annular channel 32. The pilot control chamber 16 is pressurized by the restoring force of the spring 20 on the piston of the pilot control slide valve 29 via an annular channel 33 connected to P B. The actuating piston 25 therefore displaces the main control piston 8 against the centering flange 22 and the spring 18 supported thereon. Proportional to the stroke of the main control piston 8, an additional return force is generated in the spring 18, which is returned to the pilot valve 28 via the spring plate 30 and with the tappet force of the Control magnet 4 is compared. The ram force is in turn proportional to the given magnetic current. The position of the main control piston 8 as a function of the magnetic current (or the magnetic force) in a closed position control loop with spring return and force comparison on the pilot valve 28 is thus reached very precisely.

Beim Entlasten des Steuermagneten 4 überwiegt die Vorspannkraft der Feder 18 und der Vorsteuerraum 14 wird über den Ringkanal 32 des Vorsteuerschieberventils 28 wieder mit Druck beaufschlagt. Da die vom Zentrierkolben 22 mit dem darin enthaltenen Betätigungskolben 23 auf den Hauptsteuerkolben 8 ausgeübte Gesamtdruckkraft um den Druckkraftanteil der Ringfläche 34 grösser als die Druckkraft des alleinigen Betätigungskolbens 25 der gegenüberliegenden B' Seite ist (der Zentrierkolben 24 ist in Gehäuseanschlag), wird der Hauptsteuerkolben entsprechend der Kraftverringerung des Steuermagneten 4 bis maximal zum Gehäuseanschlag des Zentrierkolbens 22 zurückgestellt.When the control magnet 4 is relieved, the biasing force of the spring 18 predominates and the pilot control chamber 14 is pressurized again via the annular channel 32 of the pilot control slide valve 28. Since the total pressure force exerted on the main control piston 8 by the centering piston 22 with the actuating piston 23 contained therein is greater than the compressive force portion of the annular surface 34 by the compressive force of the sole actuating piston 25 on the opposite B ′ side (the centering piston 24 is in the housing stop), the main control piston becomes corresponding the reduction in force of the control magnet 4 is reset to a maximum of the housing stop of the centering piston 22.

Für eine Bewegung des Hauptsteuerkolbens 8 nach der B' Seite bei Betätigung des Steuermagneten 6 laufen die für die A' Seite beschriebenen Vorgänge analog ab.For a movement of the main control piston 8 to the B 'side when the control magnet 6 is actuated, the processes described for the A' side proceed analogously.

Aus der Zeichnung ist leicht zu ersehen, dass bei Druckausfall im Vorsteuerraum 14, 16 die beiden Federn 18, 10 den Hauptsteuerkolben 8 über die Zentrierkolben 22, 24 in seiner Mittellage zentrieren, so dass alle Anschlüsse P, T, A und B verschlossen sind. Bei Ausfall der elektrischen Ansteuerung werden, wie vorbeschrieben, die beiden Vorsteuerräume 14, 16 durch ihre Anschlüsse PA bzw. PB druckbeaufschlagt, so dass der Hauptsteuerkolben 8 in seiner Mittellage druckzentriert wird. In beiden Fällen erfolgt somit eine sichere Rückführung des Hauptsteuerkolbens in sein Mittellage, so dass in keinem dieser beiden Fälle eine ungewollte Bewegung angeschlossener Hydraulikkomponenten erfolgen kann.From the drawing it can easily be seen that, in the event of a pressure failure in the pilot control chamber 14, 16, the two springs 18, 10 center the main control piston 8 via the centering piston 22, 24 in its central position, so that all connections P, T, A and B are closed. If the electrical control fails, the two pilot control rooms 14, 16 are pressurized by their connections P A and P B , as described above, so that the main control piston 8 is pressure-centered in its central position. In both cases, the main control piston is reliably returned to its central position, so that in neither of these two cases can an unwanted movement of connected hydraulic components take place.

Da die Lageregelung des Hauptsteuerkolbens nur durch Federkraftvergleich erfolgt, ist das Ventil äusserst robust, störungsunanfällig und betriebssicher.Since the position control of the main control piston is only carried out by spring force comparison, the valve is extremely robust, insensitive to malfunctions and reliable in operation.

Durch äussere Gewaltanwendung, beziehungsweise falsche Inbetriebnahme oder Installation ist es nahezu unmöglich, die Funktionsweise des Ventils zu verstellen. Alle funktionsentscheidenden Elemente sind physisch im Ventil integriert.Due to the external use of force, incorrect commissioning or installation, it is almost impossible to change the way the valve works. All function-critical elements are physically integrated in the valve.

Wegen der internen Rückführung und Lageregelung beim erfindungsgemässen Ventil ist kein Wegeaufnehmer mit zugehöriger externer elektronischer Regelung mehr nötig.Because of the internal feedback and position control in the valve according to the invention, a position transducer with associated external electronic control is no longer necessary.

Figur 2 zeigt eine Ausführung eines erfindungsgemässen Proportionalwegeventils mit einem einzigen elektrischen Steuermagneten für die Ansteuerung des Hauptsteurkolbens aus der Mittellage nach nur einer Seite. Diese Ausführung wird häufig als Proportional Drosselventil mit nur einer Durchflussrichtung eingesetzt. Das B'-seitige Vorsteuerschieberventil 29 ist durch eine Endkappe 38 ersetzt, die den Zentrierkolben 24 einspannt ist. Über den Vorsteuerraum 16 wird der Betätigungskolben 25 ständig mit Druck beaufschlagt. Bei nicht erregten Steuermagneten 4 ist der Vorsteuerraum 14, über das durch die vorgespannte Feder 18 zum Druckanschluss PA aufgesteuerte Vorsteuerschieberventil 28, druckbeaufschlagt. Ein Zentrierkolben 36 ist im Ventilgehäuse verschiebbar eingepasst und weist im Vorsteuerraum 14 eine im Verhältnis zum Betätigungskolben 25 grössere Druckfläche auf. Seine gegenüberliegende Druckfläche 37 ist zum Tank entlastet so dass der Hauptsteuerkolben 8 in seine Mittellage gegen den feststehenden Zentrierflansch 24 druckzentriert wird. Bei drucklosem System erfolgt die Zentrierung durch die Feder 18. Die Funktionsweise beim Ansteuern über Steuermagnet 4 ist die gleiche wie vorher bei der Ausführung nach Fig. 1 beschrieben.FIG. 2 shows an embodiment of a proportional directional control valve according to the invention with a single electrical control magnet for actuating the main control piston from the central position on only one side. This version is often used as a proportional throttle valve with only one flow direction. The B'-side pilot valve 29 is replaced by an end cap 38 which clamps the centering piston 24. The actuating piston 25 is constantly connected to the pilot control chamber 16 Pressure applied. When the control magnet 4 is not energized, the pilot control chamber 14 is pressurized via the pilot control valve 28 which is actuated by the prestressed spring 18 to the pressure connection P A. A centering piston 36 is slidably fitted in the valve housing and has a larger pressure area in the pilot control chamber 14 in relation to the actuating piston 25. Its opposite pressure surface 37 is relieved to the tank so that the main control piston 8 is pressure centered in its central position against the fixed centering flange 24. When the system is depressurized, centering is carried out by the spring 18. The mode of operation when actuated by control magnet 4 is the same as that previously described for the embodiment according to FIG. 1.

Fig. 3 zeigt einen Längschnitt durch das erfindungsgemässe Proportionalwegeventil mit zwei zusätzlichen in die hydraulische Vorsteuerung einer Ventilseite A' oder B' integrierte 3/2-Wege-Sitzventilen, die von einer übergeordneten Maschinensteuerung entsprechend den Sicherheitsanforderungen der Maschine zur Freigabe der vom Steuermagneten vorgegebenen Hauptsteuerkolbenposition betätigt werden müssen.3 shows a longitudinal section through the proportional directional control valve according to the invention with two additional 3/2-way seat valves integrated into the hydraulic pilot control of a valve side A 'or B', which are controlled by a higher-level machine control system in accordance with the safety requirements of the machine for releasing the main control piston position specified by the control magnet must be operated.

Die nachfolgenden Ausführungen beziehen sich auf die Anordnung dieser zusätzlichen Sicherheitsfunktionen auf der A' Seite. Die Funktionen bei Anordnung auf der B' Seite oder auf beiden Seiten A' und B' sind entsprechend.The following explanations refer to the arrangement of these additional safety functions on the A 'side. The functions when arranged on the B 'side or on both sides A' and B 'are corresponding.

Damit beispielsweise eine Pressen-Schliessbewegung durch Aufsteuern des Hauptsteuerkolbens 8 proportional zur Ansteuerung des Steuermagneten 4 erfolgen kann, muss bei geschlossener Schutztür 47 ein 3/2-Wege-Sitzventil 39 über ein entlastetes Schutztürventil 49 hydraulisch mit Druck betätigt werden. Gleichzeitig muss ein Elektromagnet ein 3/2-Wege-Sitzventil 43 geschaltet haben, damit der Tankanschluss 35 des Vorsteuerschieberventils 28 drucklos durch die Leitungen 40, 41 zum Tank entlastet ist. Erst dann kann der Hauptsteuerkolben 8 die durch den Steuermagneten 4 vorgegebene Position einnehmen und die Schliessgeschwindigkeit des Pressenzylinders steuern. Beim Öffnen der Schutztür 47 wird das Schutztürventil 49 betätigt und das 3/2-Wege-Sitzventil hydraulisch entlastet, wodurch der Tankanschluss 35 des Vorsteuerschieberventils 28 mit Druck über den Anschluss 42 beaufschlagt wird, und der Hauptsteuerkolben 8 unabhängig von der Ansteuerung des Steuermagneten 4 durch Druckaufbau im Vorsteuerraum 14 druckzentriert in die Mittellage fährt.So that, for example, a press closing movement can be carried out by opening the main control piston 8 in proportion to the actuation of the control magnet 4, a 3/2-way seat valve 39 must be actuated hydraulically with pressure via a relieved protective door valve 49 when the protective door 47 is closed. At the same time, an electromagnet must have switched a 3/2-way seat valve 43 so that the tank port 35 of the pilot valve 28 is depressurized through the lines 40, 41 to the tank. Only then can the main control piston 8 move through the Take the control magnet 4 in the specified position and control the closing speed of the press cylinder. When the protective door 47 is opened, the protective door valve 49 is actuated and the 3/2-way seat valve is hydraulically relieved, as a result of which pressure is exerted on the tank connection 35 of the pilot valve 28 via the connection 42, and the main control piston 8 independently of the control solenoid 4 being actuated Pressure build-up in the pilot control room 14 moves to the center position in a pressure-centered manner.

Das zusätzlich als elektromagnetisch betätigtes 3/2-Wege-Sitzventil 43 ausgebildete Sicherheitsventil ist mit dem Ventil 39 in Reihe geschaltet.The safety valve, which is additionally designed as an electromagnetically actuated 3/2-way seat valve 43, is connected in series with the valve 39.

Wird das elektromagnetisch betätigte 3/2-Wege-Sitzventil 43 nicht zur Freigabe der Pressen Schliessbewegung angesteuert, wird der Tankanschluss 35 des Vorsteuerschieberventils 28 ebenfalls auch bei betätigten 3/2-Wege-Sitzventil 39 mit Druck über Anschluss 46 beaufschlagt so dass der Hauptsteuerkolben in die Mittellage druckzentriert wird.If the electromagnetically actuated 3/2-way seat valve 43 is not activated to release the press closing movement, the tank connection 35 of the pilot valve 28 is also pressurized via connection 46 even when the 3/2-way seat valve 39 is actuated, so that the main control piston in the middle layer is pressure centered.

Durch diese Anordnung, die Verwendung von Sitzventilen und die hydraulische Druckzentrierung wird ein Höchstmass an Sicherheit beim Abstoppen der Pressen-Schliessbewegung durch die übergeordnete Maschinensteuerung erreicht.This arrangement, the use of poppet valves and the hydraulic pressure centering ensure maximum safety when stopping the press closing movement through the higher-level machine control.

Claims (8)

  1. Proportional directional valve with position control, with a main control piston (8), which can be hydraulically controlled by means of two pilot control slide valves (28, 29), controlled by proportional magnets (4, 6), with mechanical feedback of the position of the main control piston (8) to the actuated pilot control slide valve (28, 29), the main control piston exhibiting a spring-centred central location in a valve housing (3),
       characterised
       in that the main control piston (8) can be axially positioned in the housing (3) by means of two centring pistons (22, 24), each of which can slide in its respective housing guide, and each of annular cross-section, and by means of two actuation pistons (23, 25), each fitted so that they can slide inside the centring pistons (22, 24),
       in that each of the two centring pistons (22, 24) exhibits an axial end stop in the housing (3), these being configured in the housing (3) so that the main control piston (8) is in its central location, if both centring pistons (22, 24) are against their end stops,
       in that springs (18, 20) are associated with the two centring pistons (22, 24), acting in the direction of their end stops, and
       in that the two centring pistons (22, 24) form, as do the two actuation pistons (23, 25), pressure actuation surfaces acting in the direction of their end stops, in a first or second pilot control space (14, 16) respectively, that is hydraulically connected to a first or second pilot control slide valve (28, 29) respectively.
  2. Proportional directional valve with position control in accordance with claim 1, characterised in that the total effective pressure actuation surface of centring piston (22, 24) and actuation piston (23, 25) in a pilot control space (14, 16) is in each case larger than the effective pressure actuation surface of the actuation piston (23, 25) in the other pilot control space (14, 16), if the main control piston is out of its central location.
  3. Proportional directional valve with position control in accordance with claim 1 or 2, characterised in that a spring (18, 20) is in each case loaded between the pilot control slide valve (22, 29) and the centring piston (22, 24), with the result that the position of the main control piston (8) is fed back to the pilot control slide valve (28, 29) in such a way that, by means of a force comparison between spring force, proportional to position, and the positioning force of the proportional magnet (4, 6), the pilot control slide valve regulates the position of the main control piston (8) proportionally to the magnet force, via the pilot control pressure in the pilot control space (14, 16).
  4. Proportional directional valve with position control in accordance with claim 3, characterised in that for a proportional magnet (4, 6) without a control input, the spring (18, 20) associated with the pilot control valve (28, 29) defines a spring-centred idle position for the pilot control valve (28, 29) in which the pilot control space (14, 16) associated with the pilot control valve is connected to a pressure port.
  5. Proportional directional valve with position control in accordance with one of claims 1 to 4, characterised
       by a hydraulically actuated 3/2-way seat valve (39), with a first outlet (40), a first tank interconnection (41) and a first pressure interconnection (42), and
       by a preconnected electromagnetically actuated 3/2-way seat valve (43), with a second outlet (44), a second tank interconnection (45) and a second pressure interconnection (46),
       the first outlet (40) being connected to a tank interconnection (35) of the pilot control slide valve, the first tank interconnection (41) being connected to the second outlet (44), the second tank interconnection (45) being connected to a non-pressurised tank interconnection, and the second pressure interconnection (46) and the first pressure interconnection (42) being connected to a pressurised pump interconnection.
  6. Proportional directional valve with position control with a main control piston (8), that can be hydraulically controlled by means of a pilot control slide valve (28, 29), command-controlled by a proportional magnet (4), with mechanical feedback of the position of the main control piston (8) onto the actuated pilot control slide valve (28, 29),
       characterised
       in that the main control piston (8) in the housing (3) can be positioned by means of an centring piston (36) that can slide axially, and by means of an axially-opposed actuation piston (25), the main control piston being associated with an axial end stop in the housing (3),
       in that the centring piston (36) is associated with a spring (18) acting in the direction of this end stop,
       in that the centring piston (36) forms a first pressure actuation surface area, acting in the direction of the end stop, in a first pilot control space (14) that is hydraulically connected to the pilot control valve (28), and
       in that the actuation piston (25) forms a second pressure actuation surface area, significantly smaller and acting in an opposing direction, in a second pilot control space (16), so that when these pilot control volumes are pressurised, a pressure-centring of the main control piston (8) against the axial end stop is effected by means of the centring piston (36).
  7. Proportional directional valve with position control in accordance with claim 6, characterised in that the actuation piston (25) is fitted into a centring flange (24) so that it can slide, this centring flange (24) being securely clamped by means of an end cap (38) onto the housing and forming the axial end stop for the main control piston (8).
  8. Proportional directional valve with position control in accordance with claim 6 or 7, characterised in that the centring piston (36) is of one piece with the main control piston (8)
EP19900123084 1989-12-13 1990-12-03 Proportional directional valve with position control Expired - Lifetime EP0432606B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
LU87640 1989-12-13
LU87640A LU87640A1 (en) 1989-12-13 1989-12-13 POSITION-CONTROLLED PROPORTIONAL DIRECTIONAL VALVE

Publications (2)

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EP0432606A1 EP0432606A1 (en) 1991-06-19
EP0432606B1 true EP0432606B1 (en) 1995-08-09

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EP (1) EP0432606B1 (en)
JP (1) JP3193729B2 (en)
AT (1) ATE126325T1 (en)
CA (1) CA2031770C (en)
DE (1) DE59009502D1 (en)
ES (1) ES2077005T3 (en)
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Publication number Publication date
DE59009502D1 (en) 1995-09-14
EP0432606A1 (en) 1991-06-19
FI905981A (en) 1991-06-14
JPH05312202A (en) 1993-11-22
FI98240C (en) 1997-05-12
FI98240B (en) 1997-01-31
ES2077005T3 (en) 1995-11-16
JP3193729B2 (en) 2001-07-30
LU87640A1 (en) 1990-03-13
US5144983A (en) 1992-09-08
ATE126325T1 (en) 1995-08-15
FI905981A0 (en) 1990-12-04
CA2031770A1 (en) 1991-06-14
CA2031770C (en) 2001-05-01

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