EP0074496B1 - Valve device, especially for a pressure casting machine - Google Patents

Valve device, especially for a pressure casting machine Download PDF

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Publication number
EP0074496B1
EP0074496B1 EP82107315A EP82107315A EP0074496B1 EP 0074496 B1 EP0074496 B1 EP 0074496B1 EP 82107315 A EP82107315 A EP 82107315A EP 82107315 A EP82107315 A EP 82107315A EP 0074496 B1 EP0074496 B1 EP 0074496B1
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EP
European Patent Office
Prior art keywords
valve
control
arrangement according
threaded bush
stroke
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Expired
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EP82107315A
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German (de)
French (fr)
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EP0074496A1 (en
Inventor
Hans Gebhard Krines
Hans-Jürgen Müller
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Vickers Systems GmbH
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Vickers Systems GmbH
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
    • B22D17/00—Pressure die casting or injection die casting, i.e. casting in which the metal is forced into a mould under high pressure
    • B22D17/20—Accessories: Details
    • B22D17/32—Controlling equipment

Definitions

  • the invention relates to a valve arrangement, in particular for die casting machines, with the features of the preamble of claim 1.
  • the invention has for its object to form a valve assembly of the generic type so that the adjustment of the threaded bushing is possible with relatively small forces.
  • the flanks of the threads of the threaded bushing and the valve housing which lie one on top of the other, separate from one another with each switching cycle of the valve cone, so that the thread flanks are inevitably lubricated from adjacent oil pressure spaces.
  • the threads therefore remain easy to move.
  • the direct drive can be done by hand without the use of large handwheels or a motor drive does not require a gear ratio, rather the use of a stepping motor with low torque in the direct drive is sufficient.
  • the solution according to the invention is thus space-saving and can be implemented with simple means.
  • the entire valve mechanism of the device according to the invention is designed as a cylindrical cartridge and forms an interchangeable structural unit with the individual valve parts described below.
  • the bore 2 of the housing is z. B. with a feed line, not shown, of a pressure accumulator of a die casting machine in connection, while the axial bore 3 is connected to the cylinder space.
  • the holes 2 and 3 can also serve another purpose.
  • the annular valve seat 4 is formed by the inner end of the bore 3; the screwed-in head surface 5 of the valve cone 6 bears against it when the valve is closed.
  • the arrangement and design of the valve seat 4 and the screwed-in head surface 5 is such that, when the valve is closed, the pressure in the line 2 and the annular chamber 2a can act on the projected diameter surface of the section 5a of the head surface 5.
  • the housing 1 has a further bore 7, which can also be closed with respect to the bore 3 by the valve cone 6.
  • This has a hollow cylindrical shape and is guided with its outer wall on a section 8 of the longitudinal bore 9 of the housing.
  • the rear end of the valve cone 6 has a ring-like outward reinforcement 10, just as the bore 9 has a corresponding extension 11.
  • an annular shoulder 12 is formed on the housing and an annular shoulder 13 on the valve cone 6, between which a corresponding annular space is created in the enlargement 11 of the bore 9 and is kept depressurized via the bore 14.
  • the rear reinforcement 10 increases the effective rear end face compared to the front effective end face of the valve cone 6.
  • the inner wall of the hollow valve cone 6 also forms a shoulder 15 which forms the abutment of a spring 16 described in more detail below.
  • the enlargement 11 of the bore 9 merges into a valve chamber 17, into which a bore 18 opens, which is connected via a first check valve 19 and a second opposing check valve 20 to a bore 21, which in turn via the bores 22, 23 with another Chamber 24 communicates.
  • the head 25 of a threaded bushing 26 is arranged so that it can move and be sealed.
  • Its end face 27 (FIG. 2), like the rear end face 28 of the valve cone 6, is under the effect of the pressure in the chamber 17 and the bore 18.
  • the threaded bushing 26 engages with the external thread in the internal thread 29 of the valve housing 1.
  • the rear end face 30 of the threaded bushing 26 (FIG. 2) is under the effect of the pressure in the chamber 31, which also prevails in the bore 21 and also through the bores 22, 23 in the chamber 24, which are formed by the shoulders 32, 33 of the threaded bushing is axially limited.
  • Is against the end face 27 of the threaded bush the second end of the axial pressure spring 16, which can optionally also be equipped with an axial pressure bearing to reduce the rotational friction forces.
  • the shaft 34 of the adjustment drive for the threaded bushing 26 provided with the general reference number 35 is mounted.
  • the shaft 34 is connected via a coupling part 36 to the drive shaft 37 of the adjusting drive arranged in the housing 38.
  • B. can be a low torque stepper motor.
  • the front end of the shaft 34 extends in a sealed manner into the interior 39 of the valve cone 6 and is enclosed by the spring 16.
  • the threaded bush 26 which is connected to the threaded shaft in a rotationally fixed manner.
  • the threaded bushing 26 can be connected to the shaft 34 via a plurality of rows of axial balls 40. According to FIG.
  • the parts 26 and 34 can be connected in a rotationally fixed manner via a rotary wedge 41, which engages in a corresponding groove 42 of the threaded bush 26, while according to FIG. 3c the torsional strength of the threaded bush 26 and the shaft 34 via springs and grooves 43, 44 can be accomplished.
  • valve cone 6 The interior 39 of the valve cone 6 as well as the interior of the shaft 34 is kept depressurized via a bore 45.
  • the valve cone 6 is guided, in addition to bearing against the wall of the bore 9 and the extension 11, by means of an axial rod 46 which is guided within the shaft 34.
  • this axial rod 46 is passed through the shaft 37 of the adjusting drive 35 and ends at the level of a displacement transducer 47, through which a position-controlled regulation of the valve cone 6 of the valve control described below can take place.
  • the check valve 19 acts as a differential pressure valve between the chamber 17 in front (ie in FIGS. 1 and 2 on the left) of the threaded sleeve 26 and the chamber 31 behind (ie on the right) of the threaded sleeve 26.
  • pressure is applied in the bore 21, it is in the chamber 31 this pressure, while in the chamber 17 there is a lower pressure caused by the check valve 19, as a result of which the threaded bushing 26 is pressed to the left in FIGS.
  • the enlarged head 25 of the sleeve carries two seals 25a and 25b, which can be designed as a ring or gap seal.
  • valve 1 provides a check valve 50 connected to the bore 7 as a control pressure safety valve so that the valve plug 6 remains closed even when the main pressure suddenly escapes through the bore 2.
  • An electrically operated, leak-free directional seat valve 51 connects to the valve 50 as a pilot stage for the sudden opening of the valve cone 6.
  • a flow control valve for the limited control oil supply for the slow opening and closing movement of the plug valve 6 is designated, which is connected to a check valve 53, which serves to separate the control oil flow between the directional seat valve 51 and the main control valve 54.
  • An electrically operated leakage-free directional seat valve 55 is connected to the outlet 62 of the main control valve 54, and a throttle valve 56 for manual preselection of the slow opening movement of the valve cone 6, which is connected to the bore 21 of the housing 1, is connected upstream.
  • the quick opening of the valve cone 6 can take place at any time during the slow opening process. If the directional seat valve 51 is switched on and the previously closed main control valve 54 is opened, the control current escapes from the chamber 17 via the check valve 20, the bore 21, the line 61 and the open main control valve 54 and the line 62 with the larger outflow cross section than that of the Throttle valve 56.
  • the throttle valve 56 and directional valve 55 is replaced here by an electrically, proportionally adjustable design with position control. This makes it possible to regulate the slow opening and closing of the valve cone 6 as desired, i. H. to achieve a target-actual value comparison of the valve cone 6 via the displacement sensor 47.
  • the main control valve 54 is opened quickly in the manner described above.
  • the electrically controllable directional seated valves 51 and 55 shown in FIG. 1 can optionally also be designed with pneumatic or hydraulic control.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Lift Valve (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Safety Valves (AREA)

Description

Die Erfindung bezieht sich auf eine Ventilanordnung, insbesondere für Druckgießmaschinen, mit den Merkmalen des Oberbegriffs des Anspruchs 1.The invention relates to a valve arrangement, in particular for die casting machines, with the features of the preamble of claim 1.

Bei einer bekannten Ventilanordnung dieser Art (US-A-3 159 375) sind zwei Hubbegrenzungsanschläge vorgesehen, die nacheinander zur Wirkung kommen sollen und wovon der eine Anschlag einen Kolben mit Zylinderraum in einer Buchse umfaßt, die sich mit einem Außengewinde im Ventilgehäuse abstützt und über ein Handrad verstellt werden kann. Bei der Öffnungsbegrenzung des Hauptventils schlägt der Ventilkegel mit seinem Steuerkolben gegen den Anschlag, so daß die auftretenden Kräfte schließlich über das Gewinde auf das Ventilgehäuse übertragen werden müssen. Die feste Aufeinanderpressung der Gewindeflanken infolge der immer aus der gleichen Richtung auftretenden Kräfte führt dazu, daß mit der Zeit immer größere Bereiche der Gewindeflanken aneinander trocken haften. Es sind deshalb sehr große Kräfte erforderlich, um diese Haftreibung zu überwinden und die Gewindebuchse zu verstellen.In a known valve arrangement of this type (US-A-3 159 375) two stroke limit stops are provided which are to come into effect one after the other and of which one stop comprises a piston with a cylinder space in a bushing which is supported by an external thread in the valve housing and above a handwheel can be adjusted. When the opening of the main valve is limited, the valve cone strikes against the stop with its control piston, so that the forces which occur must finally be transmitted to the valve housing via the thread. The firm pressing together of the thread flanks as a result of the forces always occurring from the same direction leads to the fact that over time, ever larger areas of the thread flanks adhere to one another dry. Very large forces are therefore required to overcome this static friction and to adjust the threaded bushing.

Der Erfindung liegt die Aufgabe zugrunde, eine Ventilanordnung der oberbegrifflichen Art so auszubilden, daß die Verstellung der Gewindebuchse mit verhältnismäßig kleinen Kräften möglich wird.The invention has for its object to form a valve assembly of the generic type so that the adjustment of the threaded bushing is possible with relatively small forces.

Die gestellte Aufgabe wird, wie in Anspruch 1 angegeben, gelöst.The stated object is, as stated in claim 1, solved.

Bei der erfindungsgemäßen Ventilanordnung lösen sich bei jedem Schaltspiel des Ventilkegels die aufeinander liegenden Flanken der Gewinde der Gewindebuchse und des Ventilgehäuses voneinander, so daß eine zwangsläufige Schmierung der Gewindeflanken aus benachbarten Öldruckräumen erfolgt. Die Gewinde bleiben deshalb leicht gängig. Der Direktantrieb kann von Hand ohne Anwendung großer Handräder erfolgen bzw. für einen motorischen Antrieb braucht man keine Übersetzung, vielmehr genügt die Verwendung eines Schrittschaltmotors mit niedrigem Drehmoment im Direktantrieb. Die erfindungsgemäße Lösung ist somit raumsparend und mit einfachen Mitteln zu verwirklichen.In the valve arrangement according to the invention, the flanks of the threads of the threaded bushing and the valve housing, which lie one on top of the other, separate from one another with each switching cycle of the valve cone, so that the thread flanks are inevitably lubricated from adjacent oil pressure spaces. The threads therefore remain easy to move. The direct drive can be done by hand without the use of large handwheels or a motor drive does not require a gear ratio, rather the use of a stepping motor with low torque in the direct drive is sufficient. The solution according to the invention is thus space-saving and can be implemented with simple means.

Ausführungsbeispiele der Erfindung werden anhand der Zeichnung beschrieben. Dabei zeigt :

  • Figur 1 eine erste Ausführungsform mit einer Schnittdarstellung des Hauptventils und einem hydraulischen Schaltplan der Steuerventileinrichtung ;
  • Figur 2 eine zweite Ausführungsform mit einem zusätzlichen Wegaufnehmer am Hauptventil und einer Variante der Steuerventileinrichtung ; und
  • Figur 3 Ausführungsbeispiele für drehfeste, axial verschiebbare Verbindungen zwischen einer Welle und einer Buchse.
Embodiments of the invention are described with reference to the drawing. It shows:
  • Figure 1 shows a first embodiment with a sectional view of the main valve and a hydraulic circuit diagram of the control valve device;
  • Figure 2 shows a second embodiment with an additional displacement sensor on the main valve and a variant of the control valve device; and
  • Figure 3 embodiments for non-rotatable, axially movable connections between a shaft and a socket.

Der gesamte Ventilmechanismus der erfindungsgemäßen Vorrichtung ist als zylindrische Patrone ausgeführt und bildet mit den einzelnen nachstehend beschriebenen Ventilteilen eine auswechselbare Baueinheit. Die Bohrung 2 des Gehäuses steht z. B. mit einer nicht dargestellten Speiseleitung eines Druckspeichers einer Druckgießmaschine in Verbindung, während die axiale Bohrung 3 mit dem Zylinderraum verbunden ist. Die Bohrungen 2 und 3 können auch einer anderen Zweckbestimmung dienen. Der ringförmige Ventilsitz 4 wird durch das innere Ende der Bohrung 3 gebildet ; gegen ihn liegt die eingedrehte Kopffläche 5 des Ventilkegels 6 bei geschlossenem Ventil an. Die Anordnung und Ausbildung des Ventilsitzes 4 und der eingedrehten Kopffläche 5 ist so getroffen, daß bei geschlossenem Ventil der Druck in der Leitung 2 und der Ringkammer 2a auf die projektierte Durchmesserfläche des Abschnitts 5a der Kopffläche 5 wirken kann.The entire valve mechanism of the device according to the invention is designed as a cylindrical cartridge and forms an interchangeable structural unit with the individual valve parts described below. The bore 2 of the housing is z. B. with a feed line, not shown, of a pressure accumulator of a die casting machine in connection, while the axial bore 3 is connected to the cylinder space. The holes 2 and 3 can also serve another purpose. The annular valve seat 4 is formed by the inner end of the bore 3; the screwed-in head surface 5 of the valve cone 6 bears against it when the valve is closed. The arrangement and design of the valve seat 4 and the screwed-in head surface 5 is such that, when the valve is closed, the pressure in the line 2 and the annular chamber 2a can act on the projected diameter surface of the section 5a of the head surface 5.

Auf Höhe der Bohrung 2 weist das Gehäuse 1 eine weitere Bohrung 7 auf, die gegenüber der Bohrung 3 gleichfalls durch den Ventilkegel 6 abschließbar ist. Dieser weist hohlzylindrische Form auf und wird mit seiner Außenwand an einem Abschnitt 8 der Längsbohrung 9 des Gehäuses geführt. Das hintere Ende des Ventilkegels 6 weist eine ringartige nach außen gerichtete Verstärkung 10 auf, wie auch die Bohrung 9 eine entsprechende Erweiterung 11 besitzt. Hierdurch wird einerseits eine Ringschulter 12 an dem Gehäuse und eine Ringschulter 13 an dem Ventilkegel 6 gebildet, zwischen denen in der Erweiterung 11 der Bohrung 9 ein entsprechender Ringraum entsteht, der über die Bohrung 14 drucklos gehalten ist. Andererseits wird durch die hintere Verstärkung 10 die wirksame rückseitige Stirnfläche gegenüber der vorderen wirksamen Stirnfläche des Ventilkegels 6 vergrößert. Die Innenwand des hohlen Ventilkegels 6 bildet ebenfalls eine Schulter 15, die das eine Widerlager einer untenstehend noch näher beschriebenen Feder 16 bildet.At the level of the bore 2, the housing 1 has a further bore 7, which can also be closed with respect to the bore 3 by the valve cone 6. This has a hollow cylindrical shape and is guided with its outer wall on a section 8 of the longitudinal bore 9 of the housing. The rear end of the valve cone 6 has a ring-like outward reinforcement 10, just as the bore 9 has a corresponding extension 11. In this way, on the one hand, an annular shoulder 12 is formed on the housing and an annular shoulder 13 on the valve cone 6, between which a corresponding annular space is created in the enlargement 11 of the bore 9 and is kept depressurized via the bore 14. On the other hand, the rear reinforcement 10 increases the effective rear end face compared to the front effective end face of the valve cone 6. The inner wall of the hollow valve cone 6 also forms a shoulder 15 which forms the abutment of a spring 16 described in more detail below.

Die Erweiterung 11 der Bohrung 9 geht in eine Ventilkammer 17 über, in die eine Bohrung 18 mündet, die über ein erstes Rückschlagventil 19 und ein zweites entgegengerichtetes Rückschlagventil 20 mit einer Bohrung 21 verbunden ist, die ihrerseits über die Bohrungen 22, 23 mit einer weiteren Kammer 24 in Verbindung steht.The enlargement 11 of the bore 9 merges into a valve chamber 17, into which a bore 18 opens, which is connected via a first check valve 19 and a second opposing check valve 20 to a bore 21, which in turn via the bores 22, 23 with another Chamber 24 communicates.

In der Erweiterung 11 der Bohrung 9 ist der Kopf 25 einer Gewindebüchse 26 verschieblich und abgedichtet angeordnet. Ihre Stirnseite 27 (Fig. 2) steht wie auch die rückseitige Stirnfläche 28 des Ventilkegels 6 unter der Wirkung des Druckes in der Kammer 17 und der Bohrung 18. Die Gewindebüchse 26 greift mit ihrem Außengewinde in das Innengewinde 29 des Ventilgehäuses 1 ein. Die rückseitige Stirnfläche 30 der Gewindebüchse 26 (Fig. 2) steht unter Wirkung des Druckes in der Kammer 31, der auch in der Bohrung 21 sowie über die Bohrungen 22, 23 in der Kammer 24 herrscht, die von den Schultern 32, 33 der Gewindebüchse axial begrenzt wird. Gegen die Stirnseite 27 der Gewindebüchse liegt das zweite Ende der Axialdruckfeder 16 an, die wahlweise auch mit einem Axialdrucklager zur Reduzierung der Drehreibkräfte ausgestattet sein kann.In the extension 11 of the bore 9, the head 25 of a threaded bushing 26 is arranged so that it can move and be sealed. Its end face 27 (FIG. 2), like the rear end face 28 of the valve cone 6, is under the effect of the pressure in the chamber 17 and the bore 18. The threaded bushing 26 engages with the external thread in the internal thread 29 of the valve housing 1. The rear end face 30 of the threaded bushing 26 (FIG. 2) is under the effect of the pressure in the chamber 31, which also prevails in the bore 21 and also through the bores 22, 23 in the chamber 24, which are formed by the shoulders 32, 33 of the threaded bushing is axially limited. Is against the end face 27 of the threaded bush the second end of the axial pressure spring 16, which can optionally also be equipped with an axial pressure bearing to reduce the rotational friction forces.

In dem Ventilgehäuse 1 ist die Welle 34 des mit der allgemeinen Bezugsziffer 35 versehene Verstellantrieb für die Gewindebüchse 26 gelagert. Hierbei ist die Welle 34 über einen Kupplungsteil 36 mit der Antriebswelle 37 des in dem Gehäuse 38 angeordneten Verstellantriebs verbunden, der z. B. ein Schrittmotor mit kleinem Drehmoment sein kann. Das vordere Ende der Welle 34 ragt abgedichtet bis in den Innenraum 39 des Ventilkegels 6 und wird von der Feder 16 umschlossen. Gleichfalls abgedichtet gegenüber der Welle 34 ist die Gewindebüchse 26, die drehfest mit der Gewindewelle verbunden ist. Hierzu kann gemäß Fig.3a die Gewindebüchse 26 über mehrere axiale Kugelreihen 40 mit der Welle 34 verbunden sein. Gemäß Fig.3b können die Teile 26 und 34 über einen Drehkeil 41, der in eine entsprechende Nut 42 der Gewindebüchse 26 eingreift, drehfest verbunden sein, während gemäß Fig. 3c die Drehfestigkeit der Gewindebüchse 26 und der Welle 34 über Federn und Nuten 43, 44 bewerkstelligt werden kann.In the valve housing 1, the shaft 34 of the adjustment drive for the threaded bushing 26 provided with the general reference number 35 is mounted. Here, the shaft 34 is connected via a coupling part 36 to the drive shaft 37 of the adjusting drive arranged in the housing 38. B. can be a low torque stepper motor. The front end of the shaft 34 extends in a sealed manner into the interior 39 of the valve cone 6 and is enclosed by the spring 16. Also sealed with respect to the shaft 34 is the threaded bush 26, which is connected to the threaded shaft in a rotationally fixed manner. For this purpose, according to FIG. 3a, the threaded bushing 26 can be connected to the shaft 34 via a plurality of rows of axial balls 40. According to FIG. 3b, the parts 26 and 34 can be connected in a rotationally fixed manner via a rotary wedge 41, which engages in a corresponding groove 42 of the threaded bush 26, while according to FIG. 3c the torsional strength of the threaded bush 26 and the shaft 34 via springs and grooves 43, 44 can be accomplished.

Der Innenraum 39 des Ventilkegels 6 wie auch der Innenraum der Welle 34 ist über eine Bohrung 45 drucklos gehalten. Die Führung des Ventilkegels 6 erfolgt außer durch Anlage an der Wand der Bohrung 9 und der Erweiterung 11 durch eine Axialstange 46, die innerhalb der Welle 34 geführt ist.The interior 39 of the valve cone 6 as well as the interior of the shaft 34 is kept depressurized via a bore 45. The valve cone 6 is guided, in addition to bearing against the wall of the bore 9 and the extension 11, by means of an axial rod 46 which is guided within the shaft 34.

Gemäß Fig. 2 ist diese axiale Stange 46 durch die Welle 37 des Verstellantriebs 35 hindurchgeführt und endet auf Höhe eines Wegaufnehmers 47, durch den eine lagekontrollierte Regelung des Ventilkegels 6 der untenstehend beschriebenen Ventilsteuerung erfolgen kann.2, this axial rod 46 is passed through the shaft 37 of the adjusting drive 35 and ends at the level of a displacement transducer 47, through which a position-controlled regulation of the valve cone 6 of the valve control described below can take place.

Für die Erfindung ist die Betrachtung der Gewindebüchse 26, insbesondere deren Gewinde 29 und das Gegengewinde 48 (Fig. 2) des Gehäuses 1 wichtig. Das Rückschlagventil 19 wirkt hierbei als Differenzdruckventil zwischen der Kammer 17 vor (d. h. in den Fig. 1 und 2 links) der Gewindebüchse 26 und der Kammer 31 hinter (d. h. rechts) der Gewindebüchse 26. Bei Druckgabe in der Bohrung 21 stellt sich in der Kammer 31 dieser Druck ein, während in der Kammer 17 sich ein druch das Rückschlagventil 19 bewirkter geringerer Druck herrscht, wodurch die Gewindebüchse 26 nach links in den Fig. 1 und 2 gedrückt wird und sich hierbei die Flanken des Gewindes 29 der Büchse 26 von den Flanken des Gewindes 48 entgegen der Wirkung der Feder 16 abheben und die Flanken mit einem Schmierfilm neuerlich versehen werden. Zum Verstellen der Büchse 26, wodurch der Hub des Ventilkegels 6 veränderbar ist, bedarf es daher nur geringer Kräfte an der Welle 34, da nur die auftretenden Reibungskräfte zwischen den Gewinden 29 und 48 sowie den Dichtungen und die Federkräfte 16, 19 und 20 zu überwinden sind. Ein Haften oder Festfressen der Gewindeflanken aneinander ist ausgeschlossen durch Wiederholung des vorgenannten Ablaufes nach jeder erfolgten Gewindeflanken-Druckbeaufschlagung.It is important for the invention to consider the threaded bushing 26, in particular its thread 29 and the counter thread 48 (FIG. 2) of the housing 1. The check valve 19 acts as a differential pressure valve between the chamber 17 in front (ie in FIGS. 1 and 2 on the left) of the threaded sleeve 26 and the chamber 31 behind (ie on the right) of the threaded sleeve 26. When pressure is applied in the bore 21, it is in the chamber 31 this pressure, while in the chamber 17 there is a lower pressure caused by the check valve 19, as a result of which the threaded bushing 26 is pressed to the left in FIGS. 1 and 2 and the flanks of the thread 29 of the bushing 26 move away from the flanks lift the thread 48 against the action of the spring 16 and the flanks are provided with a lubricating film again. To adjust the sleeve 26, whereby the stroke of the valve cone 6 can be changed, only small forces are therefore required on the shaft 34, since only the friction forces occurring between the threads 29 and 48 and the seals and the spring forces 16, 19 and 20 have to be overcome are. Sticking or seizing of the thread flanks to one another is excluded by repeating the above-mentioned process after each thread flank pressure has been applied.

Da die Stirnfläche 28 der Verstärkung 10 zusammen mit der Schulterfläche 15 eine größere Fläche als die projektierten Flächen der Abschnitte 5a und 5b (siehe Fig.1) bilden, ist hierdurch die für den Schließvorgang des Ventilkegels 6 erforderliche Differentialdruckwirkung gegeben.Since the end face 28 of the reinforcement 10 together with the shoulder face 15 form a larger area than the projected areas of the sections 5a and 5b (see FIG. 1), this provides the differential pressure effect required for the closing process of the valve cone 6.

Um die Druckdifferenz zwischen der Kammer 17 einerseits und den Kammern 24 und 31 zu gewährleisten, trägt der erweiterte Kopf 25 der Büchse zwei Dichtungen 25a und 25b, die als Ring- oder Spaltichtung ausgeführt sein können.In order to ensure the pressure difference between the chamber 17 on the one hand and the chambers 24 and 31, the enlarged head 25 of the sleeve carries two seals 25a and 25b, which can be designed as a ring or gap seal.

Der Schaltplan nach Fig. 1 sieht ein mit der Bohrung 7 in Verbindung stehendes Rückschlagventil 50 als Steuerdruck-Sicherheitsventil vor, damit der Ventilkegel 6 auch dann geschlossen bleibt, wenn der Hauptdruck über die Bohrung 2 plötzlich entweicht. An das Ventil 50 schließt ein elektrisch betätigtes leckölfreies Wegesitzventil 51 als Vorsteuerstufe für die schlagartige Öffnung des Ventilkegels 6 an. Mit 52 ist ein Stromregelventil für die begrenzte Steuer- ölversorgung für die langsame Öffnungs- und Schließbewegung des Kegelventils 6 bezeichnet, das mit einem Rückschlagventil 53 verbunden ist, das der Trennung der Steuerölströmung zwischen dem Wegesitzventil 51 und dem Hauptsteuerventil 54 dient. Bei Betätigen des Hauptsteuerventils 54 über das Pilotventil 51 kann eine schlagartige Öffnungsbewegung des Ventilkegels 6 erfolgen. Mit dem Ausgang 62 des Hauptsteuerventils 54 ist ein elektrisch betätigtes leckölfreies Wegesitzventil 55 verbunden, dem ein Drosselventil 56 zur manuellen Vorwahl der langsamen Öffnungsbewegung des Ventilkegels 6 vorgeschaltet ist, das mit der Bohrung 21 des Gehäuses 1 verbunden ist.1 provides a check valve 50 connected to the bore 7 as a control pressure safety valve so that the valve plug 6 remains closed even when the main pressure suddenly escapes through the bore 2. An electrically operated, leak-free directional seat valve 51 connects to the valve 50 as a pilot stage for the sudden opening of the valve cone 6. With 52 a flow control valve for the limited control oil supply for the slow opening and closing movement of the plug valve 6 is designated, which is connected to a check valve 53, which serves to separate the control oil flow between the directional seat valve 51 and the main control valve 54. When the main control valve 54 is actuated via the pilot valve 51, the valve plug 6 can open suddenly. An electrically operated leakage-free directional seat valve 55 is connected to the outlet 62 of the main control valve 54, and a throttle valve 56 for manual preselection of the slow opening movement of the valve cone 6, which is connected to the bore 21 of the housing 1, is connected upstream.

Der Funktionsablauf bei langsamen Öffnen des Kegelventils 6 spielt sich wie folgt ab :

  • Beim Einschalten des Wegesitzventils 55 kann über die Bohrung 21 und das Drosselventil 56 mehr Steueröl über die Leitung 60 abfließen, als über das Rückschlagventil 50, das Wegesitzventil 51, das Stromregelventil 52 und das Rückschlagventil 53 nachströmen kann. Hierdurch wird in der Bohrung 21 und der Kammer 17 über das Rückschlagventil 20 ein Druckabfall erzielt, der den Ventilkegel 6 durch den höheren Druck auf den Abschnitt 5a in Öffnungsrichtung bewegt. Bei Druckumkehr erfolgt ein Schließen des Ventilkegels 6.
The functional sequence when the plug valve 6 opens slowly is as follows:
  • When the directional seat valve 55 is switched on, more control oil can flow off via the line 60 via the bore 21 and the throttle valve 56 than can flow in via the check valve 50, the directional seat valve 51, the flow control valve 52 and the check valve 53. As a result, a pressure drop is achieved in the bore 21 and the chamber 17 via the check valve 20, which moves the valve cone 6 in the opening direction due to the higher pressure on the section 5a. When the pressure is reversed, the valve plug 6 closes.

Das schnelle Öffnen des Ventilkegels 6 kann zu jedem Zeitpunkt des langsamen Öffnungsvorganges erfolgen. Wird hierzu das Wegesitzventil 51 eingeschaltet und das vorher geschlossene Hauptsteuerventil 54 geöffnet, so entweicht der Steuerstrom aus der Kammer 17 über das Rückschlagventil 20, die Bohrung 21, die Leitung 61 und das geöffnete Hauptsteuerventil 54 und die Ableitung 62 mit dem größeren Abströmquerschnitt als dem des Drosselventils 56.The quick opening of the valve cone 6 can take place at any time during the slow opening process. If the directional seat valve 51 is switched on and the previously closed main control valve 54 is opened, the control current escapes from the chamber 17 via the check valve 20, the bore 21, the line 61 and the open main control valve 54 and the line 62 with the larger outflow cross section than that of the Throttle valve 56.

Bei der Ausführungsform nach Fig. 2 ist der Aufbau der Schaltung der gleiche wie nach Fig. 1, nur wirkt hier das freie Ende der Achsialstange 46 als Steuerfahne auf einen elektrischen Wegaufnehmer 47.2, the construction of the circuit is the same as in FIG. 1, only here the free end of the axial rod 46 acts as a control flag on an electrical displacement sensor 47.

Das Drosselventil 56 und Wegeventil 55 wird hier durch eine elektrisch, proportional verstellbare Bauart mit Lagekontrolle ersetzt. Dadurch ist es möglich, das langsame Öffnen und Schließen des Ventilkegels 6 beliebig zu regeln, d. h. einen Soll-Ist-Wertvergleich des Ventilkegels 6 über den Wegaufnehmer 47 zu erreichen.The throttle valve 56 and directional valve 55 is replaced here by an electrically, proportionally adjustable design with position control. This makes it possible to regulate the slow opening and closing of the valve cone 6 as desired, i. H. to achieve a target-actual value comparison of the valve cone 6 via the displacement sensor 47.

Das schnelle Öffnen des Hauptsteuerventils 54 erfolgt in vorstehend beschriebenem Sinne.The main control valve 54 is opened quickly in the manner described above.

Die in der Fig. 1 dargestellten elektrisch ansteuerbaren Wegesitzventile 51 und 55 können wahlweise auch mit pneumatischer oder hydraulischer Ansteuerung ausgeführt sein.The electrically controllable directional seated valves 51 and 55 shown in FIG. 1 can optionally also be designed with pneumatic or hydraulic control.

Claims (7)

1. Valve arrangement, especially for pressure die casting machines, with the following features :
- arranged in a valve housing (1) is a main valve with a valve cone (6), a control piston (10) and a stroke-limiting stop (25) ;
- the stroke-limiting stop (25) can be adjusted by means of a drive mechanism (26, 34), which comprises a threaded bush (26) and a support thread (48) arranged on the valve housing (1) ;
- a control valve device (50 to 56), which also contains throttle devices (56), is connected by at least one control line (61) to the main valve, so that the valve cone (6) of the latter can execute a delayed or a quick movement ;

characterised in that the threaded bush (26) has pressurised surfaces (27, 30, 33), on which counteracting displacement forces - in the support direction or in the release direction - develop onto the threaded bush (26), the relative size of which displacement forces to one another changes with every switching cycle of the valve cone (6).
2. Valve arrangement according to Claim 1, characterised in that the surfaces(30,33) pressurised in the release direction border on chamber arrangements (31, 24), which are connected (at 21) to the control line (61) and via nonreturn valves (19, 20), connected in opposite directions, to a valve control chamber (17), which contains the surface (27), of the threaded bush (26), pressurised in the support direction and the control piston (10).
3. Valve arrangement according to Claim 1 or 2, characterised in that the stroke-limiting stop (25) and the threaded bush (26) are integrated in a single construction, the stroke-limiting stop (25) containing on one side the surface (27) pressurised in the support direction and on the other side a partial surface (33) of the surfaces (30, 33) pressurised in the release direction, which surfaces are sealed from one another (seal 25a, 25b).
4. Valve arrangement according to one of Claims 1 to 3, characterised in that the drive mechanism (26, 34) comprises a shaft (34), with which the threaded bush (26) is connected so as to be non-rotational but axially displaceable.
5. Valve arrangement according to Claim 4, characterised in that the shaft (34) is hollow and accommodates an axle (46), one end of which is connected to the valve cone (6), whereas the other end is part of a displacement transducer (47).
6. Valve arrangement according to one of Claims 1 to 5, characterised in that the stroke-limiting stop (25) is at the same time designed as a thrust block for a valve spring (16) of the main valve.
7. Valve arrangement according to one of Claims 1 to 6, characterised in that the control valve device (50 to 56) has a pressure feed line (7) which can be shut off (valve 51), a circuit from flow-control valve (52) and adjustable throttle (56), to the connecting point of which is connected the control line (61), and a discharge valve (54), which, when the pressure feed line (7) is shut off, suddenly opens and depressurises the control line (61) whereas, when the pressure feed line (7) of the control line (61) is connected through, pressure oil is fed via the flow-control valve (52), and if necessary pressure oil is conducted away via the adjustable throttle (56).
EP82107315A 1981-08-20 1982-08-12 Valve device, especially for a pressure casting machine Expired EP0074496B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3132909 1981-08-20
DE19813132909 DE3132909A1 (en) 1981-08-20 1981-08-20 "VALVE DEVICE, IN PARTICULAR FOR DIE CASTING MACHINES

Publications (2)

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EP0074496A1 EP0074496A1 (en) 1983-03-23
EP0074496B1 true EP0074496B1 (en) 1985-03-13

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EP82107315A Expired EP0074496B1 (en) 1981-08-20 1982-08-12 Valve device, especially for a pressure casting machine

Country Status (4)

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EP (1) EP0074496B1 (en)
JP (1) JPS58103950A (en)
CA (1) CA1192375A (en)
DE (2) DE3132909A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH672672A5 (en) * 1985-12-10 1989-12-15 Vaillant Gmbh
DE3819128C2 (en) * 1988-06-04 1995-10-26 Conducta Endress & Hauser Gas detection system
US5137254A (en) * 1991-09-03 1992-08-11 Caterpillar Inc. Pressure compensated flow amplifying poppet valve

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2058112A1 (en) * 1970-11-26 1972-05-31 Idra Pressen Gmbh Method for controlling the connection of the multiplier to the plunger on multiplier die casting machines
DE7507129U (en) * 1975-08-28 Eglinski Geraetetechnik Kg Shut-off device for hydraulic systems. 700903
DE7604336U1 (en) * 1976-02-14 1976-07-15 Varsek, Zdenko, Dipl.-Ing., 7500 Karlsruhe VALVE DEVICE

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3159375A (en) * 1962-05-31 1964-12-01 Greenlee Bros & Co Flow control valve
US4011902A (en) * 1973-10-08 1977-03-15 Gebrueder Buehler Ag Device for pressure casting
IT1005917B (en) * 1974-04-02 1976-09-30 Italpresse Spa CONTROL DEVICE FOR THE SHUT-OFF VALVE OF THE ACCUMULATOR IN A HYDRAULIC PRESS FOR INJECTION MOLDING OF METALLIC BODIES
DE2737153A1 (en) * 1977-08-17 1979-03-01 Idra Pressen Gmbh VALVE FOR INFLUENCING THE PRESSURE MEDIUM ON DIE CASTING MACHINES
FR2444828A1 (en) * 1978-12-18 1980-07-18 Heurtey Metallurgie Control system for ram positioning - has sliding stop worked by motor driven screw and incorporating shock absorber

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7507129U (en) * 1975-08-28 Eglinski Geraetetechnik Kg Shut-off device for hydraulic systems. 700903
DE2058112A1 (en) * 1970-11-26 1972-05-31 Idra Pressen Gmbh Method for controlling the connection of the multiplier to the plunger on multiplier die casting machines
DE7604336U1 (en) * 1976-02-14 1976-07-15 Varsek, Zdenko, Dipl.-Ing., 7500 Karlsruhe VALVE DEVICE

Also Published As

Publication number Publication date
EP0074496A1 (en) 1983-03-23
CA1192375A (en) 1985-08-27
JPS58103950A (en) 1983-06-21
DE3262555D1 (en) 1985-04-18
DE3132909A1 (en) 1983-03-03

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