EP0527393B1 - Solenoid valve apparatus - Google Patents

Solenoid valve apparatus Download PDF

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Publication number
EP0527393B1
EP0527393B1 EP92112951A EP92112951A EP0527393B1 EP 0527393 B1 EP0527393 B1 EP 0527393B1 EP 92112951 A EP92112951 A EP 92112951A EP 92112951 A EP92112951 A EP 92112951A EP 0527393 B1 EP0527393 B1 EP 0527393B1
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EP
European Patent Office
Prior art keywords
valve
armature
magnet
solenoid valve
valve apparatus
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
EP92112951A
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German (de)
French (fr)
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EP0527393A1 (en
Inventor
Rudolf Brunner Obering
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Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
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Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
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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
    • 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
    • F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet valves
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/16—Rectilinearly-movable armatures
    • H01F7/1607—Armatures entering the winding

Definitions

  • the invention relates to a solenoid valve device specified in the preamble of claim 1.
  • the two valve tappets are acted upon by a transverse yoke lying on the valve tappet ends, on which the shaft, which is structurally separate from the transverse yoke, engages in a central recess.
  • the shaft is pressurized by a spring over the armature and guided in the magnetic core. Since the transverse yoke can tip over, the times at which the two seat valves are actuated during an anchor stroke cannot be set.
  • the poppet valve that is currently providing the lower resistance is actuated first, if necessary completely. This can also result in an undesirable transverse load on the shaft.
  • the armature for each pair of poppet valves is designed as an armature disk, which is guided in the valve housing with an integrally molded shaft and with an axially spaced armature disk of a further pair of Seat valves form a unit.
  • the valve tappets of one pair of poppet valves engage with enlarged end plates in the cavities of the armature plate and are acted upon by the magnet by pulling.
  • one seat valve is in its shut-off position, the other, however, in its through position.
  • the open seat valve is opened further and the other seat valve is also opened.
  • the end plate of the valve tappet associated with the latter valve has a slight play in the central position relative to a counter surface of the armature plate. Because of the design, a very powerful and large-volume actuating magnet is required. In addition - since the armature disk is integrated with the shaft in the valve housing - the construction of the valve body is complex.
  • a plunger screwed into the armature penetrates the housing of the two seat valves.
  • a balance beam is provided, which acts on both valve tappets and is supported by a nut screwed onto the tappet. This results in sealing areas that are difficult to control and a large overall length.
  • the balance beam can tilt relative to the tappet, so that neither synchronous nor precisely timed actuation of the seat valves is guaranteed during an armature stroke.
  • the invention has for its object to provide a solenoid valve device of the type mentioned, which is compact and structurally simple and manages with a small and light actuating magnet, the times at which seat valves actuated during a magnetic stroke (opened or closed) be set exactly and reproducibly.
  • the transmission element integrated in the plunger magnet enables a compact and simple construction with resistant and simple sealing areas between the valve housing and the plunger magnet.
  • the one guided in the magnetic core against tilting The cross section actuates the two seat valves at precisely and reproducibly definable times during an anchor stroke, that is, regardless of whether the seat valves have different actuation resistances or not or whether a negative overlap is needed or not. It is also advantageous to avoid inhibiting forces during the movement of the transmission member, the tilt support of the cross member on the shaft between the free ends of the valve lifters and the armature.
  • a small, light and inexpensive plunger magnet can be used, because the lag means that the common plunger magnet provided for both seat valves only needs to actuate one seat valve after the other.
  • the lag in order to relieve the plunger magnet is achieved in a structurally simple manner in the embodiment according to claim 2.
  • the time or the position of the armature when the second seat valve is actuated can be precisely defined from the outset.
  • a rigid transmission member is provided, which is easy to manufacture (rotating part) and does not require rotation lock.
  • the embodiment according to claim 6 is useful.
  • the magnetic connection via the core is not impaired by the recess of the magnetic core.
  • the transmission member is mounted easily and still reliably secured against undesired tilting movements.
  • an inexpensive plunger magnet can be used which only needs to be liquid-tight and therefore does not require thick or heavy housing walls or housing parts. It is also corrosion-resistant. Instead of a liquid-tight immersion anchor magnet, a pressure-resistant one could also be used, which is to be exposed to the full working pressure.
  • a hydraulic control H according to FIG. 1 has a consumer V, for example a double-acting hydraulic cylinder 5.
  • the consumer V is connected to a solenoid valve device M via working lines 3, 4, to which a pressure line 1 and a return line 2 are connected.
  • the solenoid valve device M has two 4/2-way seat valves S, each of which has an actuating magnet 7, 7 '(plunger armature magnet) on its housing 6, 6'. In the illustrated shut-off positions, the valves are held by springs 8 when the actuating magnets 7, 7 'are not energized (position of the consumer V).
  • the actuating magnet 7 When the actuating magnet 7 is energized, the pressure line 1 is connected to the working line 3, while at the same time the working line 4 is connected to the return line 2.
  • the cylinder 5 is adjusted downwards. If, on the other hand, the actuating magnet 7 'is excited when the actuating magnet 7 is de-energized, then the pressure line 1 is connected to the working line 4 and the return line 2 to the working line 3. The cylinder 5 is after adjusted above. In both valves S, the actuating magnets are connected to the return line 2 via relief connections 2a.
  • FIG. 2 shows the structure of the left 4/2-way seat valve S from FIG. 1.
  • Two adjacent chambers 9, 10 are provided in the housing 6.
  • the return line is connected to a chamber part 31 of the left chamber 9, the working line 3 to the chamber part 31 of the right chamber 10.
  • the working line 4 is connected to the chamber 9, while the pressure line 1 is connected directly to the chamber 10.
  • Valve cartridges P are inserted (indicated by dashed lines) in the chambers 9, 10, the detailed structure of which will be explained with reference to FIG. 3.
  • Two parallel valve tappets 11, 12 protrude from the cartridges P on a housing side 13.
  • the actuating magnet 7 is fixed in a sealed manner with its housing 18.
  • the actuating magnet 7 is a commercially available pressure-tight or liquid-tight wet plunger magnet.
  • a transmission member G is guided linearly, which consists of a shaft 23 and a lower cross part 24, which overlaps both valve lifters 11, 12.
  • the transmission member G can be mushroom-shaped as a rotating part.
  • the shaft 23 is slidably guided in a bore 21 of the core 17 by means of slide bearings 22 and is supported against tilting.
  • the cross part 24 is seated in the recess 20 of the core 17, into which the valve lifters 11, 12 also protrude.
  • Each cartridge P in FIG. 2 is a 2/2-way seat valve according to FIG. 3, the cartridge P being screwed into an internal thread 25 provided in the chamber 9 or 10.
  • the cartridge P has an upper part 26a and a lower part 26b.
  • a circumferential groove 27 is provided in the lower part 26b and is connected via a channel 28 to an internal valve chamber 29.
  • a valve element 32 is displaceable in the valve chamber 29, which carries a closing element 34 which cooperates with the valve seat 30 on a neck 33, expediently with a conical or spherical sealing surface.
  • the valve element 32 is acted upon by a closing spring 38 in the chamber part 31 via a ball 36 and a spring abutment 37.
  • the return line 2 is connected to the circumferential groove 27 of the working line 4 (see FIGS. 1 and 2).
  • a longitudinal channel 35 connects the chamber part 31 to a chamber 39 which contains a sealing insert 40 in the upper part 26a.
  • the valve tappet 11 passes through the sealing insert 40 and projects through a bore 41 in the upper part 26 and with its free end over the housing side 13.
  • valve is statically largely pressure-balanced, so that the valve element 32 is kept closed only by the force of the closing spring 38.
  • the valve is opened by pressing the valve tappet 11 from above.
  • the other cartridge P is of the same design.
  • Its valve lifter 12 also protrudes with its free end. In the embodiment shown, the valve tappet 12 protrudes by an amount X less than the valve tappet 11, which, if applicable, bears directly on the transverse part 24 (negative coverage).
  • the solenoid valve device M (Fig. 4), e.g. 1, has two 4/2-way seat valves in a common housing 42, to which the actuating magnets 7, 7 'housed in a common magnetic block 44 are fastened to the side of the housing to which the four Valve tappets 11, 12 are accessible.
  • the magnetic block 44 has relatively thin outer walls 43 and a thin partition 45 between the two actuating magnets 7, 7 '. Both actuating magnets 7, 7 'have in the core 17 a recess 20 for the transverse part 24 of the transmission member G, which acts on both valve lifters 11, 12 of a pair of the 4/2-way seat valves when the armature 15 is pulled down.
  • Fig. 2 can be viewed as a section in the plane II-II of Fig. 4.
  • each actuating magnet 7, 7 ' can be considered cheaper liquid-tight wet plunger magnet can be designed, the moderate pressures up to 10 bar without complaint coped with.
  • pressure-tight magnets that are exposed to the working pressure.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

In a solenoid valve apparatus (M) comprising at least two directional seat valves, lying side-by-side in a housing (6, 6', 42) and having one valve lifter (11, 12) each, and a plunger-type armature magnet (7, 7'), which is fastened to the housing with an armature stroke movement parallel to the direction of movement of the valve lifters (11, 12) parallel to one another, and the armature (15) of which can act upon both valve lifters (11, 12) together by means of a transverse part (24) to which the armature stroke movement can be transmitted by means of a stem (23) guided in the magnet core (17), the stem (23) forms with the transverse part (24) a one-piece, inverted-T-shaped transmission member (G) which is supported in a stable manner in the magnet core (17) and whose stem (23) can be acted upon directly by the armature (15). To relieve the magnet, one valve lifter (12) can be acted upon with a time-lag relative to the other valve lifter (11). <IMAGE>

Description

Die Erfindung betrifft eine Magnetventil-Vorrichtung der im Oberbegriff des Patentanspruchs 1 angegebenen Art.The invention relates to a solenoid valve device specified in the preamble of claim 1.

Bei einer aus DE-B-10 85 736 bekannten Magnetventil-Vorrichtung gemäß Oberbegriff des Anspruchs 1 werden die beiden Ventilstößel über ein auf den Ventilstößelenden liegendes Querjoch beaufschlagt, an dem in einer mittigen Mulde der baulich vom Querjoch getrennte Schaft angreift. Der Schaft wird von einer Feder über den Anker druckbeaufschlagt und im Magnetkern geführt. Da das Querjoch kippen kann, lassen sich die Zeitpunkte nicht einstellen, zu denen während eines Ankerhubs die beiden Sitzventile betätigt werden. Das Sitzventil, das gerade den geringeren Widerstand leistet, wird zuerst, gegebenenfalls vollständig, betätigt. Daraus kann auch eine unerwünschte Querbelastung für den Schaft resultieren.In a solenoid valve device known from DE-B-10 85 736 according to the preamble of claim 1, the two valve tappets are acted upon by a transverse yoke lying on the valve tappet ends, on which the shaft, which is structurally separate from the transverse yoke, engages in a central recess. The shaft is pressurized by a spring over the armature and guided in the magnetic core. Since the transverse yoke can tip over, the times at which the two seat valves are actuated during an anchor stroke cannot be set. The poppet valve that is currently providing the lower resistance is actuated first, if necessary completely. This can also result in an undesirable transverse load on the shaft.

Bei einer Magnetventil-Vorrichtung gemäß FR-A-23 67 972 (Fig. 3) ist der Anker für je ein Paar Sitzventile als Ankerscheibe ausgebildet, die mit einem einstückig angeformten Schaft im Ventilgehäuse geführt ist und mit einer axial beabstandeten Ankerscheibe eines weiteren Paares von Sitzventilen eine Einheit bildet. Die Ventilstößel des einen Paares an Sitzventilen greifen mit vergrößerten Endscheiben in Hohlräume der Ankerscheibe ein und werden vom Magneten durch Ziehen beaufschlagt. In einer durch eine Feder eingestellten mittleren Hubstellung der Ankerscheibe ist das eine Sitzventil in seiner Absperrstellung, das andere hingegen in seiner Durchangsstellung. Bei Erregen des Betätigungsmagneten wird das offene Sitzventil weiter und das andere Sitzventil ebenfalls geöffnet. Die Endscheibe des dem letztgenannten Ventil zugeordneten Ventilstößels weist in der Mittelstellung relativ zu einer Gegenfläche der Ankerscheibe ein geringes Spiel auf. Es wird wegen der Bauweise ein sehr kräftiger und großvolumiger Betätigungsmagnet benötigt. Außerdem ist - da die Ankerscheibe mit dem Schaft in das Ventilgehäuse integriert ist - die Konstruktion des Ventilkörpers aufwendig.In a solenoid valve device according to FR-A-23 67 972 (FIG. 3), the armature for each pair of poppet valves is designed as an armature disk, which is guided in the valve housing with an integrally molded shaft and with an axially spaced armature disk of a further pair of Seat valves form a unit. The valve tappets of one pair of poppet valves engage with enlarged end plates in the cavities of the armature plate and are acted upon by the magnet by pulling. In a middle stroke position of the armature disk set by a spring, one seat valve is in its shut-off position, the other, however, in its through position. When the actuating magnet is excited, the open seat valve is opened further and the other seat valve is also opened. The end plate of the valve tappet associated with the latter valve has a slight play in the central position relative to a counter surface of the armature plate. Because of the design, a very powerful and large-volume actuating magnet is required. In addition - since the armature disk is integrated with the shaft in the valve housing - the construction of the valve body is complex.

Bei einer aus US-A-24 76 519 bekannten Magnetventil-Vorrichtung durchsetzt ein in den Anker eingeschraubter Stößel das Gehäuse der beiden Sitzventile. Am dem Betätigungsmagneten gegenüberliegenden Ende des Stößels ist ein Waagebalken vorgesehen, der an beiden Ventilstößeln angreift und durch eine auf den Stößel aufgeschraubte Mutter abgestützt ist. Es ergeben sich schwierig zu beherrschende Dichtbereiche und eine große Baulänge. Der Waagebalken kann relativ zum Stößel kippen, so daß weder eine synchrone noch eine zeitlich genau festlegbare Betätigung der Sitzventile bei einem Ankerhub gewährleistet ist.In a solenoid valve device known from US-A-24 76 519, a plunger screwed into the armature penetrates the housing of the two seat valves. At the end of the tappet opposite the actuating magnet, a balance beam is provided, which acts on both valve tappets and is supported by a nut screwed onto the tappet. This results in sealing areas that are difficult to control and a large overall length. The balance beam can tilt relative to the tappet, so that neither synchronous nor precisely timed actuation of the seat valves is guaranteed during an armature stroke.

Der Erfindung liegt die Aufgabe zugrunde, eine Magnetventil-Vorrichtung der eingangs genannten Art zu schaffen, die kompakt und baulich einfach ist sowie mit einem kleinen und leichten Betätigungsmagneten auskommt, wobei sich die Zeitpunkte, an denen Sitzventile während eines Magnethubs betätigt (geöffnet oder geschlossen) werden, exakt und reproduzierbar einstellen lassen.The invention has for its object to provide a solenoid valve device of the type mentioned, which is compact and structurally simple and manages with a small and light actuating magnet, the times at which seat valves actuated during a magnetic stroke (opened or closed) be set exactly and reproducibly.

Die gestellte Aufgabe wird erfindungsgemäß mit den im Patentanspruch 1 angegebenen Merkmalen gelöst.The object is achieved according to the invention with the features specified in claim 1.

Das in den Tauchankermagneten integrierte Übertragungsglied ermöglicht eine kompakte und einfache Bauweise mit widerstandsfähigen und einfachen Dichtbereichen zwischen dem Ventilgehäuse und dem Tauchankermagneten. Der im Magnetkern kippsicher geführte Querteil betätigt die beiden Sitzventile zu genau und reproduzierbar festlegbaren Zeitpunkten während eines Ankerhubs, d.h., unabhängig davon, ob die Sitzventile unterschiedliche Betätigungswidestände haben oder nicht oder ob eine negative Überdeckung gebraucht wird oder nicht. Es ist ferner zur Vermeidung von Hemmkräften bei der Bewegung des Übertragungsgliedes vorteilhaft, die Kippabstützung des Querteils über den Schaft zwischen den freien Enden der Ventilstößel und dem Anker zu bewerkstelligen. Es läßt sich ein kleiner, leichter und kostengünstiger Tauchankermagnet verwenden, denn durch die Nacheilung braucht der für beide Sitzventile vorgesehene gemeinsame Tauchankermagnet jeweils nur ein Sitzventil nach dem anderen zu betätigen. Solche Standard-Tauchankermagneten haben eine relativ steile Kennlinie über den Hub. Die Kraft reicht dann gerade aus, das erste Sitzventil problemlos zu öffnen. Das zweite Sitzventil wird erst geöffnet, wenn die Magnetkraft nach anfänglichem Ankerhub schon erheblich angewachsen ist, so daß die für das zweite Sitzventil nötige zusätzliche Kraft für den Magneten keine Rolle mehr spielt. Zudem wird ein oftmals aus anderen Gründen erwünschte negative Überdeckung erzielt. Bei den üblichen Magnethüben von 1,1 - 1,5mm reicht eine Nacheilung von 0,1 - 0,3mm aus, ohne daß dies auf die Ventilfunktion einen spürbaren Einfluß hätte.The transmission element integrated in the plunger magnet enables a compact and simple construction with resistant and simple sealing areas between the valve housing and the plunger magnet. The one guided in the magnetic core against tilting The cross section actuates the two seat valves at precisely and reproducibly definable times during an anchor stroke, that is, regardless of whether the seat valves have different actuation resistances or not or whether a negative overlap is needed or not. It is also advantageous to avoid inhibiting forces during the movement of the transmission member, the tilt support of the cross member on the shaft between the free ends of the valve lifters and the armature. A small, light and inexpensive plunger magnet can be used, because the lag means that the common plunger magnet provided for both seat valves only needs to actuate one seat valve after the other. Such standard plunger magnets have a relatively steep characteristic curve over the stroke. The force is then just sufficient to open the first seat valve without any problems. The second seat valve is only opened when the magnetic force has already increased considerably after the initial armature stroke, so that the additional force required for the second seat valve no longer plays a role for the magnet. In addition, a negative coverage that is often desired for other reasons is achieved. With the usual magnetic strokes of 1.1 - 1.5mm, a lag of 0.1 - 0.3mm is sufficient without this having a noticeable influence on the valve function.

Die Nacheilung zwecks Entlastung des Tauchankermagneten wird bei der Ausführungsform gemäß Anspruch 2 auf baulich einfache Weise erreicht. Der Zeitpunkt der oder die Position des Ankers bei der Betätigung des zweiten Sitzventils läßt sich von vornherein genau festlegen.The lag in order to relieve the plunger magnet is achieved in a structurally simple manner in the embodiment according to claim 2. The time or the position of the armature when the second seat valve is actuated can be precisely defined from the outset.

Aus den Ansprüchen 3 und 4 sind zwei Bauvarianten zu entnehmen, bei denen der Tauchankermagnet auf baulich einfache Weise durch die Nacheilung entlastet wird.From claims 3 and 4 two construction variants can be seen, in which the plunger magnet is relieved in a structurally simple manner by the lag.

Bei der Ausführungsform gemäß Anspruch 5 ist ein gestaltfestes Übertragungsglied vorgesehen, das einfach herstellbar (Drehteil) ist und keine Drehsicherung benötigt.In the embodiment according to claim 5, a rigid transmission member is provided, which is easy to manufacture (rotating part) and does not require rotation lock.

Im Hinblick auf eine möglichst kompakte Bauweise ist die Ausführungsform gemäß Anspruch 6 zweckmäßig. Durch die Ausnehmung des Magnetkerns wird der Magnetschluß über den Kern nicht beeinträchtigt.In view of the most compact possible construction, the embodiment according to claim 6 is useful. The magnetic connection via the core is not impaired by the recess of the magnetic core.

Bei der Ausführungsform gemäß Anspruch 7 ist das Übertragungsglied leichtgängig gelagert und trotzdem zuverlässig gegen unerwünschte Kippbewegungen gesichert.In the embodiment according to claim 7, the transmission member is mounted easily and still reliably secured against undesired tilting movements.

Bei der Ausführungsform gemäß Anspruch 8 läßt sich ein preiswerter Tauchankermagnet verwenden, der nur flüssigkeitsdicht zu sein braucht und deshalb keine dicken oder schweren Gehäusewände oder Gehäuseteile benötigt. Außerdem ist er korrosionsfest. Anstelle eines nur flüssigkeitsdichten Tauchankermagneten könnte auch ein druckfester verwendet werden, der dem vollen Arbeitsdruck auszusetzen ist.In the embodiment according to claim 8, an inexpensive plunger magnet can be used which only needs to be liquid-tight and therefore does not require thick or heavy housing walls or housing parts. It is also corrosion-resistant. Instead of a liquid-tight immersion anchor magnet, a pressure-resistant one could also be used, which is to be exposed to the full working pressure.

Anhand der Zeichnung wird eine Ausführungsform des Erfindungsgegenstandes erläutert. Es zeigt:

Fig.1
als Blockschaltbild eine hydraulische Steuerung,
Fig. 2
einen Teilschnitt einer Magnetventil-Vorrichtung,
Fig. 3
einen Detailschnitt zu Fig. 2, und
Fig. 4
einen Teilschnitt einer weiteren Ausführungsform, zu der auch Fig. 2 als Schnitt in der Schnittebene II-II paßt.
An embodiment of the subject matter of the invention is explained with the aid of the drawing. It shows:
Fig. 1
as a block diagram a hydraulic control,
Fig. 2
a partial section of a solenoid valve device,
Fig. 3
a detail section of Fig. 2, and
Fig. 4
a partial section of a further embodiment, to which Fig. 2 also fits as a section in the section plane II-II.

Eine hydraulische Steuerung H gemäß Fig. 1 weist einen Verbraucher V auf, beispielsweise einen doppeltwirkenden Hydraulikzylinder 5. Über Arbeitsleitungen 3, 4 ist der Verbraucher V mit einer Magnetventil-Vorrichtung M verbunden, an die eine Druckleitung 1 und eine Rücklaufleitung 2 angeschlossen ist. Die Magnetventil-Vorrichtung M weist zwei 4/2-Wege-Sitzventile S auf, deren jedes einen Betätigungsmagneten 7, 7' (Tauchankermagneten )an seinem Gehäuse 6, 6' besitzt. In den dargestellten Absperrstellungen werden die Ventile bei nicht erregten Betätigungsmagneten 7, 7' von Federn 8 gehalten (Haltestellung des Verbrauchers V). Bei Erregen des Betätigungsmagneten 7 wird die Druckleitung 1 mit der Arbeitsleitung 3 verbunden, während gleichzeitig die Arbeitsleitung 4 mit der Rücklaufleitung 2 verbunden ist. Der Zylinder 5 wird nach unten verstellt. Wird hingegen bei entregtem Betätigungsmagneten 7 der Betätigungsmagnet 7' erregt, dann wird die Druckleitung 1 mit der Arbeitsleitung 4 und die Rücklaufleitung 2 mit der Arbeitsleitung 3 verbunden. Der Zylinder 5 wird nach oben verstellt. In beiden Ventilen S sind die Betätigungsmagneten über Entlastungsverbindungen 2a mit der Rücklaufleitung 2 verbunden.A hydraulic control H according to FIG. 1 has a consumer V, for example a double-acting hydraulic cylinder 5. The consumer V is connected to a solenoid valve device M via working lines 3, 4, to which a pressure line 1 and a return line 2 are connected. The solenoid valve device M has two 4/2-way seat valves S, each of which has an actuating magnet 7, 7 '(plunger armature magnet) on its housing 6, 6'. In the illustrated shut-off positions, the valves are held by springs 8 when the actuating magnets 7, 7 'are not energized (position of the consumer V). When the actuating magnet 7 is energized, the pressure line 1 is connected to the working line 3, while at the same time the working line 4 is connected to the return line 2. The cylinder 5 is adjusted downwards. If, on the other hand, the actuating magnet 7 'is excited when the actuating magnet 7 is de-energized, then the pressure line 1 is connected to the working line 4 and the return line 2 to the working line 3. The cylinder 5 is after adjusted above. In both valves S, the actuating magnets are connected to the return line 2 via relief connections 2a.

In Fig. 2 ist der Aufbau des linken 4/2-Wege-Sitzventils S von Fig. 1 verdeutlicht. Im Gehäuse 6 sind zwei nebeneinanderliegende Kammern 9, 10 vorgesehen. An einen Kammerteil 31 der linken Kammer 9 ist die Rücklaufleitung angeschlossen, an den Kammerteil 31 der rechten Kammer 10 die Arbeitsleitung 3. Ferner ist an die Kammer 9 die Arbeitsleitung 4 angeschlossen, während an die Kammer 10 direkt die Druckleitung 1 angeschlossen ist. In den Kammern 9, 10 sind Ventilpatronen P eingesetzt (strichliert angedeutet), deren Detailaufbau anhand der Fig. 3 erläutert werden wird. Von den Patronen P stehen an einer Gehäuseseite 13 zwei parallele Ventilstößel 11, 12 vor. Auf der Gehäuseseite 13 ist der Betätigungsmagnet 7 mit seinem Gehäuse 18 abgedichtet festgelegt. Er enthält eine Spule 14 sowie einen beweglichen Anker 15, der in einem Ankerrohr 16 verschiebbar geführt ist. Im unteren Ende des Ankerrohres 16 sitzt ein Kern 17 mit einer Ausgleichsbohrung 19, die eine untenliegende, offene Ausnehmung 20 mit dem oberen Teil des Ankerrohrs 16 verbindet. Der Betätigungsmagnet 7 ist ein handelsüblicher druckdichter oder ein flüssigkeitsdichter Naßtauchankermagnet.2 shows the structure of the left 4/2-way seat valve S from FIG. 1. Two adjacent chambers 9, 10 are provided in the housing 6. The return line is connected to a chamber part 31 of the left chamber 9, the working line 3 to the chamber part 31 of the right chamber 10. Furthermore, the working line 4 is connected to the chamber 9, while the pressure line 1 is connected directly to the chamber 10. Valve cartridges P are inserted (indicated by dashed lines) in the chambers 9, 10, the detailed structure of which will be explained with reference to FIG. 3. Two parallel valve tappets 11, 12 protrude from the cartridges P on a housing side 13. On the housing side 13, the actuating magnet 7 is fixed in a sealed manner with its housing 18. It contains a coil 14 and a movable armature 15, which is guided in an armature tube 16 so that it can move. In the lower end of the anchor tube 16 there is a core 17 with a compensating bore 19 which connects an open recess 20 at the bottom to the upper part of the anchor tube 16. The actuating magnet 7 is a commercially available pressure-tight or liquid-tight wet plunger magnet.

Im Kern 17 ist ein Übertragungsglied G linear geführt, das aus einem Schaft 23 und einem unteren, beide Ventilstößel 11, 12 übergreifenden Querteil 24 besteht. Das Übertragungsglied G kann als Drehteil pilzförmig ausgebildet sein. Der Schaft 23 ist in einer Bohrung 21 des Kerns 17 verschiebbar mittels Gleitlagern 22 geführt und gegen ein Kippen abgestützt. Der Querteil 24 sitzt in der Ausnehmung 20 des Kerns 17, in die auch die Ventilstößel 11, 12 ragen.In the core 17, a transmission member G is guided linearly, which consists of a shaft 23 and a lower cross part 24, which overlaps both valve lifters 11, 12. The transmission member G can be mushroom-shaped as a rotating part. The shaft 23 is slidably guided in a bore 21 of the core 17 by means of slide bearings 22 and is supported against tilting. The cross part 24 is seated in the recess 20 of the core 17, into which the valve lifters 11, 12 also protrude.

Jede Patrone P in Fig. 2 ist ein 2/2-Wege-Sitzventil gemäß Fig. 3, wobei die Patrone P in ein in der Kammer 9 bzw. 10 vorgesehenes Innengewinde 25 eingeschraubt ist. Die Patrone P weist ein Oberteil 26a und Unterteil 26b auf. Im Unterteil 26b ist eine umlaufende Nut 27 vorgesehen, die über einen Kanal 28 mit einer innenliegenden Ventilkammer 29 verbunden ist. Relativ zu einem Ventilsitz 30 ist in der Ventilkammer 29 ein Ventilelement 32 verschiebbar, das an einem Hals 33 ein mit dem Ventilsitz 30 zusammenwirkendes Schließelement 34 trägt, zweckmäßigerweise mit einer kegeligen oder kugeligen Dichtfläche. Das Ventilelement 32 wird über eine Kugel 36 und ein Federwiderlager 37 von einer Schließfeder 38 im Kammerteil 31 beaufschlagt. Am Kammerteil 31 ist die Rücklaufleitung 2 an die Umfangsnut 27 die Arbeitsleitung 4 angeschlossen (s. Fig. 1 und 2). Im Ventilelement 32 verbindet ein Längskanal 35 den Kammerteil 31 mit einer Kammer 39, die im Oberteil 26a einen Dichteinsatz 40 enthält. Den Dichteinsatz 40 durchsetzt der Ventilstößel 11, der durch eine Bohrung 41 im Oberteil 26 und mit seinem freien Ende über die Gehäuseseite 13 ragt.Each cartridge P in FIG. 2 is a 2/2-way seat valve according to FIG. 3, the cartridge P being screwed into an internal thread 25 provided in the chamber 9 or 10. The cartridge P has an upper part 26a and a lower part 26b. A circumferential groove 27 is provided in the lower part 26b and is connected via a channel 28 to an internal valve chamber 29. Relative to a valve seat 30, a valve element 32 is displaceable in the valve chamber 29, which carries a closing element 34 which cooperates with the valve seat 30 on a neck 33, expediently with a conical or spherical sealing surface. The valve element 32 is acted upon by a closing spring 38 in the chamber part 31 via a ball 36 and a spring abutment 37. On the chamber part 31, the return line 2 is connected to the circumferential groove 27 of the working line 4 (see FIGS. 1 and 2). In the valve element 32, a longitudinal channel 35 connects the chamber part 31 to a chamber 39 which contains a sealing insert 40 in the upper part 26a. The valve tappet 11 passes through the sealing insert 40 and projects through a bore 41 in the upper part 26 and with its free end over the housing side 13.

Das Ventil ist statisch weitgehend druckausgeglichen, so daß das Ventilelement 32 nur durch die Kraft der Schließfeder 38 geschlossen gehalten wird. Durch Druck auf den Ventilstößel 11 von oben wird das Ventil geöffnet. Die andere Patrone P ist gleich ausgebildet. Auch ihr Ventilstößel 12 steht mit seinem freien Ende vor. Bei der gezeigten Ausführungsform steht der Ventilstößel 12 um ein Maß X weniger vor als der Ventilstößel 11, der ggfs. direkt am Querteil 24 anliegt (negative Überdeckung).The valve is statically largely pressure-balanced, so that the valve element 32 is kept closed only by the force of the closing spring 38. The valve is opened by pressing the valve tappet 11 from above. The other cartridge P is of the same design. Its valve lifter 12 also protrudes with its free end. In the embodiment shown, the valve tappet 12 protrudes by an amount X less than the valve tappet 11, which, if applicable, bears directly on the transverse part 24 (negative coverage).

Die Magnetventil-Vorrichtung M (Fig. 4), z.B. zur Steuerung des Verbrauchers V gemäß Fig. 1, weist zwei 4/2-Wege-Sitzventile in einem gemeinsamen Gehäuse 42 auf, an dem die in einem gemeinsamen Magnetblock 44 untergebrachten Betätigungsmagneten 7, 7' an der Gehäuseseite befestigt sind, an der die vier Ventilstößel 11, 12 zugänglich sind. Der Magnetblock 44 hat relativ dünne Außenwände 43 und eine dünne Trennwand 45 zwischen den beiden Betätigungsmagneten 7, 7'. Beide Betätigungsmagneten 7, 7' weisen im Kern 17 eine Ausnehmung 20 für den Querteil 24 des Übertragungsgliedes G auf, der beide Ventilstößel 11, 12 eines Paares der 4/2-Wege-Sitzventile beaufschlagt, wenn der Anker 15 nach unten gezogen wird. Ragt der Ventilstößel 14 weiter vor als der Ventilstößel 12, dann wird die Verbindung zum Rücklauf 2 früher geöffnet als die Verbindung von der Druckleitung 1 zur Arbeitsleitung 3. Der Magnet wird dadurch entlastet und kann relativ schwach und klein und leicht sein. Es ergibt sich eine kompakte Bauweise, weil das Gehäuse 42 und der Magnetblock 44 klein sind und weil die verschiedenen Kanäle zum Verknüpfen der Steuerfunktionen im Gehäuse 42 einfach unterbringbar sind. Fig. 2 kann als Schnitt in der Ebene II-II von Fig. 4 angesehen werden.The solenoid valve device M (Fig. 4), e.g. 1, has two 4/2-way seat valves in a common housing 42, to which the actuating magnets 7, 7 'housed in a common magnetic block 44 are fastened to the side of the housing to which the four Valve tappets 11, 12 are accessible. The magnetic block 44 has relatively thin outer walls 43 and a thin partition 45 between the two actuating magnets 7, 7 '. Both actuating magnets 7, 7 'have in the core 17 a recess 20 for the transverse part 24 of the transmission member G, which acts on both valve lifters 11, 12 of a pair of the 4/2-way seat valves when the armature 15 is pulled down. If the valve tappet 14 protrudes further than the valve tappet 12, then the connection to the return 2 is opened earlier than the connection from the pressure line 1 to the working line 3. This relieves the pressure on the magnet and can be relatively weak and small and light. The result is a compact design because the housing 42 and the magnetic block 44 are small and because the various channels for linking the control functions in the housing 42 can easily be accommodated. Fig. 2 can be viewed as a section in the plane II-II of Fig. 4.

Da die Betätigungsmagneten und ihre beweglichen Komponenten zwar dem Hydraulikmedium ausgesetzt, jedoch durch die in den Fig. 2, 3 und 4 nicht dargestellten Entlastungsverbindungen 2a (s. Fig. 1) mit der Rücklaufleitung verbunden sind, kann jeder Betätigungsmagnet 7, 7' als preiswerter flüssigkeitsdichter Naßtauchankermagnet ausgebildet sein, der moderate Drücke bis zu 10 Bar klaglos verkraftet. Denkbar ist es aber auch, druckdichte Magneten zu verwenden, die dem Arbeitsdruck ausgesetzt sind.Since the actuating magnets and their movable components are exposed to the hydraulic medium, but are connected to the return line by the relief connections 2a (see FIG. 1), which are not shown in FIGS. 2, 3 and 4, each actuating magnet 7, 7 'can be considered cheaper liquid-tight wet plunger magnet can be designed, the moderate pressures up to 10 bar without complaint coped with. However, it is also conceivable to use pressure-tight magnets that are exposed to the working pressure.

Claims (8)

  1. Solenoid valve apparatus (M) with at least two directional seat valves which are arranged one next to the other in a housing (6, 6', 42) and each have a linearly movable valve tappet (11, 12), and with a solenoid plunger magnet (7, 7') which is attached to the housing (6, 6', 42) with an armature travel direction which is parallel to the direction of the movement of the valve tappets (11, 12) which are parallel to one another, both valve tappets (11, 12) being capable of being acted on by the armature (15), aligned approximately with the centre between the valve tappets (11, 12), of the said solenoid plunger magnet (7, 7') together by means of a transverse component (24) onto which the travel movement of the armature can be transmitted by means of a shaft (23) which is guided in a hole (29) in the magnet core (17), characterized in that the shaft (23) forms, together with the transverse component (24), an inherently rigid, preferably integral transmission element (G), in the form of an inverted T, which is supported in the magnet core (17), secured against tilting, in such a way that the shaft (23) can be acted on directly by the armature (15), and in that both valve tappets (11, 12) can be adjusted in a staggered manner, by means of the transverse component (24), out of positions corresponding to shut-off positions or flow positions of the two directional seat valves into positions corresponding to flow positions or shut-off positions of the two directional seat valves, the one valve tappet (12 or 11) being acted on within the armature travel with a relative delay with respect to the other valve tappet (11 or 12).
  2. Solenoid valve apparatus according to Claim 1, characterized in that the two seat valves are of largely pressure-equalized construction and can be held in their shut-off position by means of, in each case, one closing spring (28) counter to the direction of travel of the armature when the solenoid plunger magnet (7, 7') is excited, and in that, in the shut-off position of the seat valves, different intervals (dimension X) are provided between the free ends of the two valve tappets (11, 12) and their bearing faces on the transverse carrier (24).
  3. Solenoid valve apparatus according to at least one of Claims 1 or 2, characterized in that the two valve tappets (11, 12) protrude beyond a housing face (13) with their free ends to different degrees.
  4. Solenoid valve apparatus according to one of Claims 1 or 2, characterized in that the two valve tappets (11, 12) protrude beyond a housing face (13) with their free ends to the same degree, and in that the transverse component (24) has bearing faces which are at different distances from the free ends.
  5. Solenoid valve apparatus according to Claims 1 to 4, characterized in that the transmission element (G) is of mushroom-shaped construction with a disc-shaped transverse component (24).
  6. Solenoid valve apparatus according to at least one of Claims 1 to 5, characterized in that the transverse component (24) is arranged countersunk in a recess (20) in the magnet core (17).
  7. Solenoid valve apparatus according to Claim 1, characterized in that at least one guide bearing (22), preferably two spaced sliding bearings, is or are provided in the hole (21) in the magnet core (17) for the shaft (23).
  8. Solenoid valve apparatus according to at least one of Claims 1 to 7, characterized in that each solenoid plunger magnet (7, 7') is a fluid-tight wet magnet.
EP92112951A 1991-08-12 1992-07-29 Solenoid valve apparatus Expired - Lifetime EP0527393B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9109976U 1991-08-12
DE9109976U DE9109976U1 (en) 1991-08-12 1991-08-12 Solenoid valve device

Publications (2)

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EP0527393A1 EP0527393A1 (en) 1993-02-17
EP0527393B1 true EP0527393B1 (en) 1996-03-27

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EP92112951A Expired - Lifetime EP0527393B1 (en) 1991-08-12 1992-07-29 Solenoid valve apparatus

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EP (1) EP0527393B1 (en)
AT (1) ATE136099T1 (en)
DE (2) DE9109976U1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202004002432U1 (en) 2004-02-17 2005-07-07 Hawe Hydraulik Gmbh & Co. Kg Magnetic double valve
DE102004051575B4 (en) * 2004-10-22 2015-12-17 Bosch Rexroth Aktiengesellschaft Directional seated valve
ES2428116T3 (en) 2011-06-16 2013-11-06 Hawe Hydraulik Se Distributor valve
DE102018116979A1 (en) * 2018-07-13 2020-01-16 Svm Schultz Verwaltungs-Gmbh & Co. Kg Electromagnetic actuator
DE102018117008A1 (en) * 2018-07-13 2020-01-16 Svm Schultz Verwaltungs-Gmbh & Co. Kg Electromagnetic actuator with bearing element

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2476519A (en) * 1944-12-04 1949-07-19 Adel Prec Products Corp Four-way valve
DE1085736B (en) * 1956-07-23 1960-07-21 Roger Charles Dubois Solenoid valve for fluids of all pressure ranges
IT947485B (en) * 1972-02-10 1973-05-21 Sirai S R L Soc Italiana Regol IN PARTICULAR VALVE WITH ELECTROMAGNETIC OPERATION
DE2646940A1 (en) * 1976-10-18 1978-04-20 Bieri Ag Liebefeld Liebefeld H ELECTROMAGNETICALLY ACTUATED HYDRAULIC DIRECTIONAL VALVE

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EP0527393A1 (en) 1993-02-17
DE9109976U1 (en) 1991-10-10
DE59205820D1 (en) 1996-05-02
ATE136099T1 (en) 1996-04-15

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