EP0667459B1 - Electro-proportional solenoid-valve unit - Google Patents

Electro-proportional solenoid-valve unit Download PDF

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Publication number
EP0667459B1
EP0667459B1 EP95100336A EP95100336A EP0667459B1 EP 0667459 B1 EP0667459 B1 EP 0667459B1 EP 95100336 A EP95100336 A EP 95100336A EP 95100336 A EP95100336 A EP 95100336A EP 0667459 B1 EP0667459 B1 EP 0667459B1
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EP
European Patent Office
Prior art keywords
piston
valve unit
electromagnet
hydraulic
unit according
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 - Lifetime
Application number
EP95100336A
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German (de)
French (fr)
Other versions
EP0667459A1 (en
Inventor
Bernd Niethammer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
HYDRAULIK-RING ANTRIEBS- und STEUERUNGSTECHNIK GmbH
Hilite Germany GmbH
Original Assignee
HYDRAULIK-RING ANTRIEBS- und STEUERUNGSTECHNIK GmbH
Hydraulik Ring GmbH
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Publication of EP0667459A1 publication Critical patent/EP0667459A1/en
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Publication of EP0667459B1 publication Critical patent/EP0667459B1/en
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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
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
    • F15B13/0442—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors with proportional solenoid allowing stable intermediate positions
    • 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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool 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
    • Y10T137/86622—Motor-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
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86694—Piston valve
    • Y10T137/86702—With internal flow passage

Definitions

  • the invention relates to an electro-proportional solenoid valve unit according to the preamble of claim 1.
  • the invention is based, the generic electro-proportional solenoid valve unit the task to train so that the Flow rate of the hydraulic medium depending on the Current with which the electromagnet is applied, steadily changed.
  • the invention is illustrated by one in the drawing Embodiment explained in more detail.
  • the Drawing shows partly in longitudinal section and partly in view an electro-proportional solenoid valve unit according to the invention.
  • the piston of the valve unit in its initial position and in the lower half in one by a pestle shown an electromagnet shifted position.
  • the electro proportional solenoid valve unit has one Electromagnet 1, the plunger 2 of which rests on a piston 3. It is under the force of a compression spring 4, which pushes the piston 3 against the plunger 2.
  • the electromagnet 1 is designed in a known manner, so that it is not described in detail. It is on an installation housing 5 attached, which a receptacle 6 for has a valve housing 7. In it is the piston 3 longitudinally displaceable.
  • the valve housing 7 has connections 8 to 10, via which, controlled by the piston 3, hydraulic medium to or from a consumer in known Way is promoted.
  • On the installation housing 5 are the corresponding consumers and the hydraulic medium containing tank also connected in a known manner.
  • the compression spring 4 is supported on one in the valve housing 7 screwed adjusting screw 11. By different screwing in the adjusting screw 11 in the valve housing 7, the biasing force the compression spring 4 and thus the position of the piston 3 Infinitely adjustable magnetic force.
  • the adjusting screw 11 has a through opening through which the hydraulic medium can flow back to the tank.
  • the piston 3 is facing the adjusting screw 11 Side provided with a recess 12 on the Bottom 13 the compression spring 4 is supported.
  • the piston has a central one that extends in its axial direction Bore 14 in the direction of the plunger 2 of the electromagnet 1 is closed by a floor 15. On the plunger 2 of the electromagnet 1 lies on this base 15 on. A opens radially into the bore 14 of the piston 3 Opening 16 through which the hydraulic medium into the bore 14 of the piston 3 can reach.
  • the outside of the piston has an annular channel 17 which closed against the electromagnet 1 by an annular web 18 is.
  • the piston 3 has another ring channel 19, which is much longer than the ring channel 17 and opposite this ring channel 17 by a Ring web 20 is separated.
  • Shown in the top half of the drawing left end position of the piston 3 is the working connection 10 open to a hydraulic chamber 21 in which the compression spring 4 lies and in which the central bore 14 of the piston 3 opens.
  • Via the radial opening 16 is the central bore 14 with the annular channel 17 of the Piston 3 connected, in which the opening 16 opens.
  • In this left end position of the piston 3 is also the Working port 8 with the ring channel 19 of the piston 3rd connected. Since also the connection 9, which with the (not shown) pump of the hydraulic system via a connection 27 of the built-in housing 5 is connected to the Ring channel 19 is connected, is thus a connection between the working port 8 and the pressure port 9 available.
  • the other working connection 10 of the valve housing 7 is in this left end position of the piston 3 not closed, so that a connection to the hydraulic room 21 exists.
  • the piston 3 has in the left End position distance from the bottom 22 of the valve housing 7. This is a between the piston 3 and the bottom 22 further hydraulic space 23 formed by at least a bore 24 axially penetrating the piston 3, the must not come into contact with the opening 16 with the opposite hydraulic chamber 21 is connected.
  • the piston 3 a further, axially penetrating bore 25, which connects the two hydraulic spaces 21 and 23 with each other.
  • valve unit Unit connected, for example a piston-cylinder unit. If this unit is to be operated, the electromagnet 1 is switched on, causing the plunger 2 is extended. It moves the piston 3 against the force of the compression spring 4. When moving the piston 3 is the connection between the pressure port 9 and the working port 8 closed while the connection between the working connection 10 and the pressure connection 9 is opened. So that can be under pressure Hydraulic medium via the pressure connection 9 and the Ring channel 19 flow to the working connection 10, from which it via a connection 28 of the installation housing 5 to be driven Flow aggregate and put it in the desired one Press way.
  • the holes 24, 25 have in the illustrated embodiment smaller cross section than the central hole 14.
  • the holes 14 and 24, 25 can also be the same Diameter. It is also possible that the Compensating holes 24, 25 larger diameter than that have central bore 14 of the piston 3.
  • the piston 3 designed as a hollow piston Insert socket.
  • the outer wall of one Bush and / or in the inner wall of the bore of the piston can at least one each over the piston or Throughout the socket length can be provided.

Description

Die Erfindung betrifft eine Elektroproportionalmagnet-Ventileinheit nach dem Oberbegriff des Anspruches 1.The invention relates to an electro-proportional solenoid valve unit according to the preamble of claim 1.

Wird der Elektromagnet bei dieser bekannten Ventileinheit (WO-A-93/18327) erregt, dann wird der als Hohlkolben ausgebildete Kolben gegen die Kraft einer Druckfeder verschoben. Dabei wird der eine Arbeitsanschluß zum zu betätigenden Aggregat geöffnet, so daß das Hydraulikmedium über diesen geöffneten Arbeitsanschluß zum Aggregat strömen kann. Das aus dem Aggregat verdrängte Hydraulikmedium gelangt zum anderen Arbeitsanschluß und von dort in den Hohlraum des Kolbens. Von dort aus strömt das Hydraulikmedium zum Tank zurück. Auf der dem Elektromagneten zugewandten Kolbenseite bildet sich in Abhängigkeit des Volumens des Hydraulikmediums, welches durch den im Durchmesser begrenzten Hohlraum des Kolbens fließt, ein hydraulischer Staudruck, der größer ist als der Druck, der auf die gegenüberliegende Kolbenseite wirkt. Dadurch ändert sich mit zunehmender Stromstärke, mit welcher der Elektromagnet die beteiligten Steuerkanten beaufschlagt, die Lage des Kolbens und der Durchfluß des Hydraulikmediums. Sobald ein kritischer Durchflußwert überschritten wird, tritt infolge der wirkenden Druckkräfte auf der Magnetseite des Kolbens, die sich zu den Magnetkräften addieren, eine schlagartige Veränderung der Kolbenposition ein. Unterhalb dieses kritischen Durchflußwertes verläuft die Durchfluß-Strom-Kennlinie noch im gewünschten Maß. Oberhalb dieses kritischen Durchflußwertes tritt jedoch eine unerwünschte schlagartige Änderung des Durchflußvolumens auf.The electromagnet in this known valve unit (WO-A-93/18327) excited, then the one designed as a hollow piston Piston moved against the force of a compression spring. The opened a working connection to the unit to be operated, so that the hydraulic medium via this open working connection to Unit can flow. The hydraulic medium displaced from the unit gets to the other work connection and from there to the Cavity of the piston. The hydraulic medium flows from there back to the tank. On the piston side facing the electromagnet forms depending on the volume of the hydraulic medium, which is due to the cavity of the Piston flows, a hydraulic dynamic pressure that is greater than that Pressure that acts on the opposite side of the piston. This changes with increasing current with which the electromagnet acted on the control edges involved, the position of the piston and the flow of the hydraulic medium. Once a critical Flow rate is exceeded, occurs due to the acting pressure forces on the magnetic side of the piston, which is related to the magnetic forces add a sudden change in the piston position. The flow-current characteristic curve runs below this critical flow value still in the desired measure. Above this critical However, the flow rate occurs an undesirable sudden Change in flow volume.

Der Erfindung liegt die Aufgabe zugrunde, die gattungsgemäße Elektroproportionalmagnet-Ventileinheit so auszubilden, daß sich die Durchflußmenge des Hydraulikmediums in Abhängigkeit von der Stromstärke, mit welcher der Elektromagnet beaufschlagt wird, stetig verändert.The invention is based, the generic electro-proportional solenoid valve unit the task to train so that the Flow rate of the hydraulic medium depending on the Current with which the electromagnet is applied, steadily changed.

Diese Aufgabe wird bei der gattungsgemäßen Elektroproportionalmagnet-Ventileinheit erfindungsgemäß mit den kennzeichnenden Merkmalen des Anspruches 1 gelöst.This task is performed in the generic electro-proportional solenoid valve unit according to the invention with the characteristic features of claim 1 solved.

Bei der erfindungsgemäßen Ventileinheit ist der elektromagnetseitige Hydraulikraum vom benachbarten Ringkanal des Kolbens und dessen Hohlraum getrennt. Dadurch kann sich in diesem Hydraulikraum ein hydraulischer Staudruck nicht bilden. Das vom zu steuernden Aggregat kommende Hydraulikmedium gelangt bei entsprechender Stellung des Kolbens in den Ringkanal und von dort über die Öffnung in den Hohlraum des Kolbens. Dieser Hohlraum ist gegenüber dem elektromagnetseitigen Hydraulikraum abgetrennt, so daß das verdrängte Medium nicht in diesen Hydraulikraum gelangen kann. Somit wird in konstruktiv einfacher Weise ein hydraulischer Staudruck in diesem Hydraulikraum vermieden. Dadurch ändert sich die Durchflußmenge-Strom-Kennlinie der Ventileinheit in gewünschtem Maße stetig; eine schlagartige Änderung der Durchflußmenge tritt nicht auf. Dadurch ist sichergestellt, daß über den gesamten Kennlinienverlauf das zu steuernde oder zu regelnde Aggregat zuverlässig betätigt wird. Über die Ausgleichsleitung wird in einfacher Weise ein Druckausgleich in den beiden Hydraulikräumen zu beiden Seiten des Kolbens erreicht, so daß auf beiden Seiten des Kolbens Druckgleichheit herrscht. Der Elektromagnet kann klein ausgelegt sein, weil es nur zu geringen Verschiebekräften am Kolben kommt. In the valve unit according to the invention, the electromagnetic side Hydraulic space from the adjacent ring channel of the piston and its Cavity separated. This can result in this hydraulic room Do not build up hydraulic back pressure. That of the unit to be controlled coming hydraulic medium arrives at the appropriate position of the piston in the ring channel and from there via the opening in the Cavity of the piston. This cavity is opposite to the electromagnetic side Hydraulic space separated, so that the displaced Medium cannot get into this hydraulic room. Thus in constructive simple hydraulic back pressure in this Hydraulic room avoided. This changes the flow rate-current characteristic the valve unit continuously to the desired extent; a abrupt change in the flow rate does not occur. This is ensures that over the entire course of the characteristic controlling or regulating unit is operated reliably. over the compensation line is a pressure equalization in a simple manner reached the two hydraulic chambers on both sides of the piston, so that pressure is equal on both sides of the piston. Of the Electromagnet can be designed small because it is too small Displacement forces on the piston comes.

Weitere Merkmale der Erfindung ergeben sich aus den weiteren Ansprüchen, der Beschreibung und der Zeichnung.Further features of the invention result from the others Claims, the description and the drawing.

Die Erfindung wird anhand eines in der Zeichnung dargestellten Ausführungsbeispieles näher erläutert. Die Zeichnung zeigt teilweise im Längsschnitt und teilweise in Ansicht eine erfindungsgemäße Elektroproportionalmagnet-Ventileinheit. In der oberen Hälfte der Zeichnung ist der Kolben der Ventileinheit in seiner Ausgangsstellung und in der unteren Hälfte in einer durch einen Stößel eines Elektromagneten verschobenen Lage dargestellt.The invention is illustrated by one in the drawing Embodiment explained in more detail. The Drawing shows partly in longitudinal section and partly in view an electro-proportional solenoid valve unit according to the invention. In the top half of the drawing is the piston of the valve unit in its initial position and in the lower half in one by a pestle shown an electromagnet shifted position.

Die Elektroproportionalmagnet-Ventileinheit hat einen Elektromagneten 1, dessen Stößel 2 an einem Kolben 3 anliegt. Er steht unter der Kraft einer Druckfeder 4, welche den Kolben 3 gegen den Stößel 2 drückt.The electro proportional solenoid valve unit has one Electromagnet 1, the plunger 2 of which rests on a piston 3. It is under the force of a compression spring 4, which pushes the piston 3 against the plunger 2.

Der Elektromagnet 1 ist in bekannter Weise ausgebildet, so daß er nicht im einzelnen beschrieben wird. Er ist an einem Einbaugehäuse 5 befestigt, das eine Aufnahme 6 für ein Ventilgehäuse 7 aufweist. In ihm ist der Kolben 3 längsverschieblich gelagert. Das Ventilgehäuse 7 hat Anschlüsse 8 bis 10, über die, vom Kolben 3 gesteuert, Hydraulikmedium zu bzw. von einem Verbraucher in bekannter Weise gefördert wird. An das Einbaugehäuse 5 sind der entsprechende Verbraucher sowie der das Hydraulikmedium enthaltende Tank ebenfalls in bekannter Weise angeschlossen.The electromagnet 1 is designed in a known manner, so that it is not described in detail. It is on an installation housing 5 attached, which a receptacle 6 for has a valve housing 7. In it is the piston 3 longitudinally displaceable. The valve housing 7 has connections 8 to 10, via which, controlled by the piston 3, hydraulic medium to or from a consumer in known Way is promoted. On the installation housing 5 are the corresponding consumers and the hydraulic medium containing tank also connected in a known manner.

Die Druckfeder 4 stützt sich an einer in das Ventilgehäuse 7 geschraubten Einstellschraube 11 ab. Durch unterschiedlich weites Einschrauben der Einstellschraube 11 in das Ventilgehäuse 7 läßt sich die Vorspannkraft der Druckfeder 4 und somit die Lage des Kolbens 3 zur Magnetkraft stufenlos einstellen. Die Einstellschraube 11 hat eine Durchgangsöffnung, über die das Hydraulikmedium zum Tank zurückströmen kann.The compression spring 4 is supported on one in the valve housing 7 screwed adjusting screw 11. By different screwing in the adjusting screw 11 in the valve housing 7, the biasing force the compression spring 4 and thus the position of the piston 3 Infinitely adjustable magnetic force. The adjusting screw 11 has a through opening through which the hydraulic medium can flow back to the tank.

Der Kolben 3 ist an seiner der Einstellschraube 11 zugewandten Seite mit einer Vertiefung 12 versehen, an deren Boden 13 sich die Druckfeder 4 abstützt. Der Kolben hat eine zentrale, in seiner Achsrichtung sich erstreckende Bohrung 14, die in Richtung auf den Stößel 2 des Elektromagneten 1 durch einen Boden 15 geschlossen ist. An diesem Boden 15 liegt der Stößel 2 des Elektromagneten 1 an. In die Bohrung 14 des Kolbens 3 mündet radial eine Öffnung 16, durch welche das Hydraulikmedium in die Bohrung 14 des Kolbens 3 gelangen kann.The piston 3 is facing the adjusting screw 11 Side provided with a recess 12 on the Bottom 13 the compression spring 4 is supported. The piston has a central one that extends in its axial direction Bore 14 in the direction of the plunger 2 of the electromagnet 1 is closed by a floor 15. On the plunger 2 of the electromagnet 1 lies on this base 15 on. A opens radially into the bore 14 of the piston 3 Opening 16 through which the hydraulic medium into the bore 14 of the piston 3 can reach.

Der Kolben weist außenseitig einen Ringkanal 17 auf, der gegen den Elektromagneten 1 durch einen Ringsteg 18 geschlossen ist. Der Kolben 3 weist einen weiteren Ringkanal 19 auf, der wesentlich länger ist als der Ringkanal 17 und der gegenüber diesem Ringkanal 17 durch einen Ringsteg 20 getrennt ist.The outside of the piston has an annular channel 17 which closed against the electromagnet 1 by an annular web 18 is. The piston 3 has another ring channel 19, which is much longer than the ring channel 17 and opposite this ring channel 17 by a Ring web 20 is separated.

In der in der oberen Hälfte der Zeichnung dargestellten linken Endstellung des Kolbens 3 ist der Arbeitsanschluß 10 zu einem Hydraulikraum 21 offen, in dem die Druckfeder 4 liegt und in den die zentrale Bohrung 14 des Kolbens 3 mündet. Über die radial verlaufende Öffnung 16 ist die zentrale Bohrung 14 mit dem Ringkanal 17 des Kolbens 3 verbunden, in den die Öffnung 16 mündet. In dieser linken Endstellung des Kolbens 3 ist außerdem der Arbeitsanschluß 8 mit dem Ringkanal 19 des Kolbens 3 verbunden. Da auch der Anschluß 9, der mit der (nicht dargestellten) Pumpe des Hydrauliksystems über einen Anschluß 27 des Einbaugehäuses 5 verbunden ist, mit dem Ringkanal 19 verbunden ist, ist somit eine Verbindung zwischen dem Arbeitsanschluß 8 und dem Druckanschluß 9 vorhanden. Der andere Arbeitsanschluß 10 des Ventilgehäuses 7 ist in dieser linken Endstellung des Kolbens 3 nicht verschlossen, so daß eine Verbindung zum Hydraulikraum 21 besteht.Shown in the top half of the drawing left end position of the piston 3 is the working connection 10 open to a hydraulic chamber 21 in which the compression spring 4 lies and in which the central bore 14 of the piston 3 opens. Via the radial opening 16 is the central bore 14 with the annular channel 17 of the Piston 3 connected, in which the opening 16 opens. In this left end position of the piston 3 is also the Working port 8 with the ring channel 19 of the piston 3rd connected. Since also the connection 9, which with the (not shown) pump of the hydraulic system via a connection 27 of the built-in housing 5 is connected to the Ring channel 19 is connected, is thus a connection between the working port 8 and the pressure port 9 available. The other working connection 10 of the valve housing 7 is in this left end position of the piston 3 not closed, so that a connection to the hydraulic room 21 exists.

Wie die Zeichnung zeigt, hat der Kolben 3 in der linken Endstellung Abstand vom Boden 22 des Ventilgehäuses 7. Dadurch wird zwischen dem Kolben 3 und dem Boden 22 ein weiterer Hydraulikraum 23 gebildet, der durch mindestens eine den Kolben 3 axial durchsetzende Bohrung 24, die nicht mit der Öffnung 16 in Verbindung kommen darf, mit dem gegenüberliegenden Hydraulikraum 21 verbunden ist. Im dargestellten Ausführungsbeispiel hat der Kolben 3 eine weitere, ihn axial durchsetzende Bohrung 25, welche die beiden Hydraulikräume 21 und 23 miteinander verbindet.As the drawing shows, the piston 3 has in the left End position distance from the bottom 22 of the valve housing 7. This is a between the piston 3 and the bottom 22 further hydraulic space 23 formed by at least a bore 24 axially penetrating the piston 3, the must not come into contact with the opening 16 with the opposite hydraulic chamber 21 is connected. In the illustrated embodiment, the piston 3 a further, axially penetrating bore 25, which connects the two hydraulic spaces 21 and 23 with each other.

An die Anschlüsse 8 und 10 des Ventilgehäuses 7 ist ein mittels der Ventileinheit zu steuerndes bzw. zu regelndes Aggregat angeschlossen, beispielsweise eine Kolben-Zylinder-Einheit. Soll dieses Aggregat betätigt werden, wird der Elektromagnet 1 eingeschaltet, wodurch der Stößel 2 ausgefahren wird. Er verschiebt den Kolben 3 gegen die Kraft der Druckfeder 4. Beim Verschieben des Kolbens 3 wird die Verbindung zwischen dem Druckanschluß 9 und dem Arbeitsanschluß 8 geschlossen, während die Verbindung zwischen dem Arbeitsanschluß 10 und dem Druckanschluß 9 geöffnet wird. Damit kann das unter Druck stehende Hydraulikmedium über den Druckanschluß 9 und den Ringkanal 19 zum Arbeitsanschluß 10 strömen, von dem es über einen Anschluß 28 des Einbaugehäuses 5 zum anzutreibenden Aggregat strömen und es in der gewünschten Weise betätigen. Das aus dem anzutreibenden Aggregat verdrängte Hydraulikmedium kann über den Arbeitsanschluß 8, den Ringkanal 17, die Öffnung 16, die Bohrung 14 des Kolbens 3, den Hydraulikraum 21 und die Durchgangsöffnung der Einstellschraube 11 zurück zum Tank gelangen. Wenn die Steuerelektronik erkennt, daß die Position der Stelleinheit des anzutreibenden Aggregates erreicht ist, wird der Steuerstrom zurückgefahren. Dadurch wird die Magnetkraft verringert und der Kolben 3 unter der Kraft der Druckfeder 5 in eine Mittelstellung zurückgeführt, in der die beiden Ringstege 20 und 26 des Kolbens 3 die beiden Anschlüsse 8 und 10 verschließen. Dadurch bleibt der Hydraulikdruck im anzutreibenden Aggregat aufrechterhalten.At the connections 8 and 10 of the valve housing 7 is a to be controlled or regulated by means of the valve unit Unit connected, for example a piston-cylinder unit. If this unit is to be operated, the electromagnet 1 is switched on, causing the plunger 2 is extended. It moves the piston 3 against the force of the compression spring 4. When moving the piston 3 is the connection between the pressure port 9 and the working port 8 closed while the connection between the working connection 10 and the pressure connection 9 is opened. So that can be under pressure Hydraulic medium via the pressure connection 9 and the Ring channel 19 flow to the working connection 10, from which it via a connection 28 of the installation housing 5 to be driven Flow aggregate and put it in the desired one Press way. That from the aggregate to be driven displaced hydraulic medium can over the working connection 8, the ring channel 17, the opening 16, the bore 14 of the Piston 3, the hydraulic chamber 21 and the through hole the adjusting screw 11 back to the tank. When the control electronics detects that the position of the Actuating unit of the unit to be driven is reached, the control current is reduced. This will make the Magnetic force is reduced and the piston 3 under the force the compression spring 5 is returned to a central position, in which the two ring webs 20 and 26 of the piston 3 Close both connections 8 and 10. This leaves maintain the hydraulic pressure in the unit to be driven.

Wird der Elektromagnet 1 abgeschaltet, wird der Kolben 3 unter der Kraft der Druckfeder 4 wieder in seine in der Zeichnung linke Endstellung zurückgeführt, wobei der Stößel 2 entsprechend in das Gehäuse des Elektromagneten 1 zurückgeschoben wird. Dabei wird die Verbindung zwischen dem Anschluß 10 und dem Druckanschluß 9 geschlossen, während die Verbindung zwischen dem Anschluß 8 und dem Druckanschluß 9 durch den Kolben 3 geöffnet wird. Dadurch kann das unter Druck stehende Hydraulikmedium über den Anschluß 10 zum Kolben des anzutreibenden Aggregates gelangen und diesen Kolben wieder zurückschieben.If the electromagnet 1 is switched off, the piston 3 under the force of the compression spring 4 again in its in the Drawing left end position returned, the Tappet 2 accordingly in the housing of the electromagnet 1 is pushed back. The connection between the port 10 and the pressure port 9 closed, while the connection between port 8 and the pressure port 9 is opened by the piston 3. Thereby can the pressurized hydraulic medium the connection 10 to the piston of the unit to be driven get and push this piston back.

Über die beiden Bohrungen 24 und 25 im Kolben 3 wird in einfacher Weise ein Druckausgleich in den beiden Hydraulikräumen 21, 23 zu beiden Seiten des Kolbens 3 erreicht. Dadurch herrscht auf beiden Seiten des Kolbens 3 Druckgleichheit. Das Hydraulikmedium strömt in den beiden Bohrungen 24, 25 des Kolbens 3 praktisch nicht, vielmehr bildet sich hier ein statischer Druck aus. Das vor dem Kolben 3 befindliche Hydraulikmedium wird beim Verschieben des Kolbens über die Bohrungen 24, 25 lediglich verdrängt. Hierbei kann auch eine gewisse Dämpfung des Kolbens 3 bei seiner Verschiebebewegung erreicht werden.About the two holes 24 and 25 in the piston 3 is in pressure equalization in the two hydraulic rooms 21, 23 reached on both sides of the piston 3. As a result, the piston 3 prevails on both sides Equal pressure. The hydraulic medium flows in the two Bores 24, 25 of the piston 3 practically not rather, a static pressure forms here. The hydraulic medium located in front of the piston 3 is at Moving the piston over the bores 24, 25 only repressed. This can also have some damping of the piston 3 reached in its displacement movement become.

Die Bohrungen 24, 25 haben im dargestellten Ausführungsbeispiel kleineren Querschnitt als die zentrale Bohrung 14. Die Bohrungen 14 und 24, 25 können aber auch gleichen Durchmesser haben. Ebenso ist es möglich, daß die Ausgleichsbohrungen 24, 25 größeren Durchmesser als die zentrale Bohrung 14 des Kolbens 3 haben.The holes 24, 25 have in the illustrated embodiment smaller cross section than the central hole 14. The holes 14 and 24, 25 can also be the same Diameter. It is also possible that the Compensating holes 24, 25 larger diameter than that have central bore 14 of the piston 3.

Um die Bohrungen 24, 25 zu erhalten, ist es auch möglich, in den als Hohlkolben ausgebildeten Kolben 3 eine Buchse einzusetzen. In der Außenwandung einer solchen Buchse und/oder in der Innenwandung der Bohrung des Kolbens kann jeweils mindestens eine über die Kolben- bzw. Buchsenlänge durchgehende Vertiefung vorgesehen sein.In order to obtain the bores 24, 25, it is also possible to in the piston 3 designed as a hollow piston Insert socket. In the outer wall of one Bush and / or in the inner wall of the bore of the piston can at least one each over the piston or Throughout the socket length can be provided.

Da der Hydraulikraum 23 durch den Ringsteg 18 des Kolbens 3 vom Ringkanal 17 getrennt ist, kann das über den Anschluß 8 aus dem anzutreibenden Aggregat verdrängte Hydraulikmedium nur über diesen Ringkanal 17 und die Öffnung 16 in die Bohrung 14 des Kolbens 3 und von dort zum Tank zurückfließen. Die zentrale Bohrung 14 des Kolbens 3 ist durch den Boden 15 vom Hydraulikraum 23 getrennt. Dadurch wirken sich die beim Verschieben des Kolbens 3 auftretenden Druckdifferenzen nicht auf das Schaltverhalten des Ventiles aus, so daß der gewünschte Kennlinienverlauf erreicht wird. Die Durchflußmenge des Hydraulikmediums ändert sich in Abhängigkeit von der Stromstärke, mit welcher der Elektromagnet 1 beaufschlagt wird, im erforderlichen Maße stetig.Since the hydraulic chamber 23 through the annular web 18 of the piston 3 is separated from the ring channel 17, this can be done via the Connection 8 displaced from the unit to be driven Hydraulic medium only through this ring channel 17 and the Opening 16 in the bore 14 of the piston 3 and from there flow back to the tank. The central bore 14 of the piston 3 is separated from the hydraulic space 23 by the floor 15. This affects when you move the Piston 3 occurring pressure differences not on that Switching behavior of the valve, so that the desired Characteristic curve is reached. The flow rate of the Hydraulic medium changes depending on the Current with which the electromagnet 1 acts becomes steady to the extent necessary.

Claims (5)

  1. An electroproportional solenoid-valve unit with a valve housing (7), in which a piston (3) is displaceable by a tappet (2) of the electromagnet (1) against spring force (4), the piston (3) being constructed in the form of a hollow piston which is provided with two annular ducts (17, 19), of which one annular duct (19) is separated from an hydraulic chamber (21) situated at the spring end and connected to a tank connexion and the other annular duct (17) is connected by at least one opening (16) to the hollow space (14) of the piston (3) and which - when current flows and ceases to flow through the electromagnet (1) - are alternately connected to two operating connexions (8, 10), of which one operating connexion (8, 10) can be connected in each case to a pressure connexion (9) and the other operating connexion (10, 8) can be connected to a tank, characterized in that the hydraulic chamber (21) situated at the spring end is connected by way of at least one compensating line (24, 25) to an hydraulic chamber (23) which is situated at the electromagnet end and which is separated by a base (15) of the piston (3) from the hollow space (14) of the said piston (3).
  2. A valve unit according to Claim 1, characterized in that the tappet (2) of the electromagnet (1) rests against the base (15) of the hollow space (14) of the piston (3).
  3. A valve unit according to Claim 1 or 2, characterized in that the compensating line (24, 25) is provided in the piston (3).
  4. A valve unit according to one of Claims 1 to 3, characterized in that the compensating line (24, 25) is a bore extending axially in the piston (3).
  5. A valve unit according to one of Claims 1 to 4, characterized in that the piston (3) has a depression (12) on its end face, into which a compression spring (4) projects.
EP95100336A 1994-02-10 1995-01-12 Electro-proportional solenoid-valve unit Expired - Lifetime EP0667459B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9402206U 1994-02-10
DE9402206U DE9402206U1 (en) 1994-02-10 1994-02-10 Electro proportional solenoid valve unit

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EP0667459A1 EP0667459A1 (en) 1995-08-16
EP0667459B1 true EP0667459B1 (en) 1999-11-03

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EP95100336A Expired - Lifetime EP0667459B1 (en) 1994-02-10 1995-01-12 Electro-proportional solenoid-valve unit

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US (1) US5592972A (en)
EP (1) EP0667459B1 (en)
JP (1) JPH07224965A (en)
DE (2) DE9402206U1 (en)

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US5894860A (en) * 1997-06-12 1999-04-20 General Motors Corporation Proportional pressure control solenoid valve
DE19727180C2 (en) * 1997-06-26 2003-12-04 Hydraulik Ring Gmbh Hydraulic valve, in particular for controlling a camshaft adjustment in a motor vehicle
DE19853670C5 (en) * 1998-11-20 2019-01-10 Hilite Germany Gmbh Camshaft adjustment device
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DE10006784A1 (en) * 2000-02-18 2001-08-23 Bosch Gmbh Robert Electromagnet for actuating the actuator of a valve
AU2002211524B2 (en) * 2000-10-04 2007-03-22 The Trustees Of The University Of Pennsylvania Highly expressible genes
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DE102005037480A1 (en) * 2005-08-09 2007-02-15 Schaeffler Kg Control valve and method of making the same
US8127786B2 (en) * 2008-04-03 2012-03-06 Hamilton Sundstrand Corporation Proportional selector valve for selecting between two pressure sources
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DE59507148D1 (en) 1999-12-09
DE9402206U1 (en) 1994-05-05
EP0667459A1 (en) 1995-08-16
JPH07224965A (en) 1995-08-22
US5592972A (en) 1997-01-14

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