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EP0952356A1 - Screw-in valve and valve assembly - Google Patents

Screw-in valve and valve assembly Download PDF

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Publication number
EP0952356A1
EP0952356A1 EP98124556A EP98124556A EP0952356A1 EP 0952356 A1 EP0952356 A1 EP 0952356A1 EP 98124556 A EP98124556 A EP 98124556A EP 98124556 A EP98124556 A EP 98124556A EP 0952356 A1 EP0952356 A1 EP 0952356A1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
screw
thread section
external thread
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.)
Granted
Application number
EP98124556A
Other languages
German (de)
French (fr)
Other versions
EP0952356B1 (en
Inventor
Walter Plotz
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.)
Hawe Hydraulik GmbH and Co KG
Original Assignee
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
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Publication of EP0952356A1 publication Critical patent/EP0952356A1/en
Application granted granted Critical
Publication of EP0952356B1 publication Critical patent/EP0952356B1/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
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/08—Assemblies of units, each for the control of a single servomotor only
    • F15B13/0803—Modular units
    • F15B13/0821—Attachment or sealing of modular units to each other
    • 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
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/08—Assemblies of units, each for the control of a single servomotor only
    • F15B13/0803—Modular units
    • F15B13/0828—Modular units characterised by sealing means of the modular units
    • 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
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/08—Assemblies of units, each for the control of a single servomotor only
    • F15B13/0803—Modular units
    • F15B13/0832—Modular valves
    • F15B13/0835—Cartridge type valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/08—Assemblies of units, each for the control of a single servomotor only
    • F15B13/0803—Modular units
    • F15B13/0878—Assembly of modular units
    • F15B13/0896—Assembly of modular units using different types or sizes of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
    • F15B2013/004—Cartridge 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
    • Y10T137/7504—Removable valve head and seat unit
    • Y10T137/7613—Threaded into valve casing

Definitions

  • the invention relates to a screw-in valve according to the preamble of claim 1 and a screw-in valve arrangement according to the preamble of claim 6.
  • Screw-in valves or screw-in valve arrangements are used in high-pressure hydraulics for space-saving implementation of various valve function variants, e.g. with block constructions, advantageous.
  • Typical practical applications are described, for example, in product information P 7710-1 "Screw-in valves type C", Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co. KG, edition 03/95 or publication D 7490-1 "2 / 2-way screw-in valves EM "from Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co. KG, March 1996.
  • the threaded hole into which the screw-in valve is screwed in is connected to pressure medium channels, which require the required valve function becomes.
  • the threaded hole can be located in a block or directly in a hydraulic component, such as a hydraulic cylinder or hydraulic motor, and is usually open to an outside that is under ambient pressure. Sealing to the outside takes place either by means of a seal pressed onto the outside or by a seal arranged in the threaded bore near the mouth of the threaded bore. The seal is activated by the thread tension of the screwed-in valve housing of the screw-in valve.
  • the invention is based on the object of specifying a screw-in valve or a screw-in valve arrangement in which the risk of automatic loosening during operation is avoided and the requirements for the assembly of the screw-in valve can be reduced.
  • the high pressure also comes into effect at the other end of the external thread section via the pressure compensation path, so that the occurrence of a loosening moment is avoided under pressure surges.
  • the requirements for observing very precise tightening torques can be reduced due to the elimination of the risk of automatic loosening.
  • material pairings can be realized that were not previously permitted due to the acute risk of loosening, because the required tightening torque can be determined so that only the tightness is guaranteed without the risk of automatic loosening To have to be considerate.
  • the pressure effective in the high pressure range propagates up to that under the tightening tension of the thread-activated seal, so that pressure surges cannot produce any loosening force in the threaded connection. Loosening of the screw-in valve is avoided even when the torque is tight, just sufficient for the required sealing effect.
  • valve housing itself is equipped with the pressure compensation path. Regardless of which threaded hole or which body the screw-in valve is screwed into, there is always no risk of automatic loosening.
  • the pressure compensation path is predetermined in a technically simple way by local abrasion in the threaded area on the valve housing.
  • a slitting of threads is provided in the external thread, so that the pressure balances out through the slits.
  • the pressure equalization path should connect both ends of the external thread section to one another. An extensive elimination of the risk of loosening can, however, also be achieved if the pressure equalization path only opens into the low-pressure side end area of the external thread, without leading completely into the low-pressure area.
  • the pressure compensation path is conveniently provided in the valve housing in terms of manufacturing technology.
  • the pressure compensation path is alternatively formed in the form of a channel in the base body.
  • the pressure equalization path is formed in the threaded connection, specifically according to claim 10 by local abrasion, such as grinding or slitting, or according to claim 11 by deliberate selection of a thread fit that is unusually loose.
  • the screw-in valve or the screw-in valve arrangement can be used for different valve functions in which there is a risk of pressure surges on the high-pressure side.
  • screw-in valve arrangements are expediently protected against loosening, the thread core diameter of which is ⁇ 16 mm, preferably ⁇ 20 mm.
  • FIG. 1 shows a screw-in valve in a screw-in valve arrangement, partly in an axial section.
  • a screw-in valve V e.g. a solenoid-operated directional seat valve has a sleeve-shaped valve housing S in which valve components 9 required for the valve function are accommodated, which in the embodiment shown protrude downward beyond the valve housing S.
  • the screw-in valve V is a commercially available structural unit which is to be screwed or screwed into a threaded bore B of a base body G which is formed in accordance with the manufacturer's requirements.
  • valve housing S is screwed with an axial external thread section F into an internal thread section K of the threaded bore B such that a seal C positioned in a circumferential groove 1 of the valve housing S is compressed to the outside for a required sealing effect .
  • a flank 2 of the annular groove 1 defines an end region of the externally threaded section F, while a shoulder 3 defines the other end region of the externally threaded section F.
  • bores 4, 5 open into the threaded bore B.
  • the bores 4, 5 form pressure medium channels which are separated from one another by a seal 7 compressed by a shoulder 6 on the valve component 9 on a bore shoulder 8 are.
  • a high-pressure area H is present at the inner end area 3 of the external thread section F, while a low-pressure or ambient pressure area L is present at the upper end area 2 of the external thread section F.
  • the pressure present in the high-pressure region H is transferred to the low-pressure or ambient pressure region L by means of a pressure compensation path D, that is to say possibly up to the seal C, so that the threaded connection is at least largely pressure-balanced in the axial direction and pressure surges in the High pressure area H does not generate any loosening torque for the external thread section F of the valve housing S.
  • the pressure compensation path D can be designed differently. Only one pressure compensation path D is indicated in FIG. 1, although in practice several pressure compensation paths could be provided distributed over the circumference of the threaded connection.
  • a longitudinal bore 10 is drilled in the valve housing S and runs within the external thread section F and just below the threads between the shoulders 2, 3.
  • An alternate pressure compensation path D ' is indicated by dash-dotted lines and connects the high-pressure side to the low-pressure side H, L as channel 11 in the base body G.
  • the pressure compensation path D '' is indicated in the threaded connection.
  • the thread combs of the external thread section F and / or the thread combs of the internal thread section K could be local, e.g. by grinding or milling or flattening. It is also conceivable to form axial slots through the threads, e.g.
  • the pressure compensation path D '' could also be formed by choosing a relatively loose fit between the internal thread section K and the external thread section F to switch between to transfer the threads from the high pressure side to the low pressure side L.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Housings (AREA)
  • Lift Valve (AREA)
  • Details Of Valves (AREA)
  • Closures For Containers (AREA)
  • Glass Compositions (AREA)

Abstract

The valve (V) has a housing (S) with an externally threaded screw-in section (F) between low pressure or ambient pressure side (L) and a high pressure side (H). At least one pressure equalisation path (D,D") is provided for connecting the two sides. The path may comprise an axial bore (10) connecting the start and end of the threaded section or it may be formed by local removal of threads of the externally threaded section by grinding or flattening.

Description

Die Erfindung betrifft ein Einschraubventil gemäß dem Oberbegriff des Anspruchs 1 bzw. eine Einschraubventil-Anordnung gemäß dem Oberbegriff des Anspruchs 6.The invention relates to a screw-in valve according to the preamble of claim 1 and a screw-in valve arrangement according to the preamble of claim 6.

Einschraubventile bzw. Einschraubventil-Anordnungen sind in der Hochdruckhydraulik zur platzsparenden Umsetzung verschiedener Ventilfunktionsvarianten, z.B. bei Blockkonstruktionen, vorteilhaft. Typische Anwendungsfälle aus der Praxis sind beispielsweise beschrieben in der Produktinformation P 7710-1 "Einschraubventile Typ C", der Firma Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co. KG, Ausgabe 03/95 oder der Druckschrift D 7490-1 "2/2-Wege-Einschraubventile EM" der Firma Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co. KG, März 1996. Die Gewindebohrung, in welche das Einschraubventil eingeschraubt wird, steht mit Druckmittelkanälen in Verbindung, bei denen die jeweils erforderliche Ventilfunktion benötigt wird. Die Gewindebohrung kann sich dabei sowohl in einem Block als auch direkt in einer Hydraulikkomponente, wie einem Hydraulikzylinder oder Hydraulikmotor, befinden, und ist im Regelfall zu einer unter Umgebungsdruck stehenden Außenseite offen. Die Abdichtung zur Außenseite erfolgt entweder durch eine auf die Außenseite gepreßte Dichtung oder eine nahe der Mündung der Gewindebohrung in der Gewindebohrung angeordnete Dichtung. Die Dichtung wird jeweils aktiviert durch die Gewindeanzugsspannung des eingeschraubten Ventilgehäuses des Einschraubventils.Screw-in valves or screw-in valve arrangements are used in high-pressure hydraulics for space-saving implementation of various valve function variants, e.g. with block constructions, advantageous. Typical practical applications are described, for example, in product information P 7710-1 "Screw-in valves type C", Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co. KG, edition 03/95 or publication D 7490-1 "2 / 2-way screw-in valves EM "from Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co. KG, March 1996. The threaded hole into which the screw-in valve is screwed in is connected to pressure medium channels, which require the required valve function becomes. The threaded hole can be located in a block or directly in a hydraulic component, such as a hydraulic cylinder or hydraulic motor, and is usually open to an outside that is under ambient pressure. Sealing to the outside takes place either by means of a seal pressed onto the outside or by a seal arranged in the threaded bore near the mouth of the threaded bore. The seal is activated by the thread tension of the screwed-in valve housing of the screw-in valve.

Da im Regelfall der höhere Druck das Ventilgehäuse entgegengesetzt zur Einschraubrichtung beaufschlagt und im Betrieb Druckstöße auftreten, ergibt sich ein Lockerungsmoment für die Gewindeverbindung, das, z.B. nach 50.000 Lastwechseln, das Ventilgehäuse in der Gewindebohrung lösen kann und die Ventilfunktion stört bzw. zunichte macht. Da nicht bei allen Einsatzfällen bei Montage des Einschraubventils ein Drehmomentschlüssel benutzt wird, ferner ohnedies nur bei kleinen Durchmessern unter 16 mm ein ausreichend festes Anzugsmoment möglich ist, u.a. auch abhängig von der Materialpaarung zwischen dem Ventilgehäuse und dem Grundkörper (Stahl, Guß, Aluminium, u.dgl.), ist dies ein bedeutsamer Nachteil von Einschraubventilen bzw. Einschraubventil-Anordnungen.Since the higher pressure generally acts on the valve housing in the opposite direction to the screwing-in direction and pressure surges occur during operation, there is a loosening moment for the threaded connection, which can loosen the valve housing in the threaded bore, for example after 50,000 load changes, and disrupt or destroy the valve function. Since a torque wrench is not used in all applications when assembling the screw-in valve, furthermore, a sufficiently firm tightening torque is only possible with small diameters under 16 mm, also depending on the material pairing between the valve housing and the base body (steel, cast iron, aluminum, etc. . Like.), this is a significant disadvantage of screw-in valves or screw-in valve arrangements.

Weiterer Stand der Technik ist zu findenin DE-196 25 349 A, US 5 217 260 A, EP 0 676 548 A, US 5 617 890 A, US 5 718 264 A und US 5 584 323 A, wo aber in keinem Fall ein Druckausgleich über ein Einschraubgewinde angesprochen wird.Further prior art can be found in DE-196 25 349 A, US 5 217 260 A, EP 0 676 548 A, US 5 617 890 A, US 5 718 264 A and US 5 584 323 A, but in no case where Pressure equalization is addressed via a screw thread.

Der Erfindung liegt die Aufgabe zugrunde, ein Einschraubventil bzw. eine Einschraubventil-Anordnung anzugeben, bei denen die Gefahr des selbsttätigen Lockern im Betrieb vermieden ist und die Anforderungen für die Montage des Einschraubventils verringerbar sind.The invention is based on the object of specifying a screw-in valve or a screw-in valve arrangement in which the risk of automatic loosening during operation is avoided and the requirements for the assembly of the screw-in valve can be reduced.

Die gestellte Aufgabe wird erfindungsgemaß mit den Merkmalen des Anspruchs 1 oder des nebengeordneten Anspruchs 6 gelöst.The object is achieved according to the invention with the features of claim 1 or the independent claim 6.

Über den Druckausgleichsweg kommt der hohe Druck auch am anderen Ende des Außengewindeabschnittes zur Wirkung, so daß unter Druckstößen das Entstehen eines Lockerungsmoments vermieden ist. Die Anforderungen an die Beachtung sehr exakter Anziehdrehmomente können wegen Wegfalls der Gefahr der selbsttätigen Lockerung gemildert werden. Insbesondere bei größeren Gewindedurchmessern, beispielsweise von 16 mm oder mehr, lassen sich Materialpaarungen realisieren, die bisher aufgrund der akuten Lockerungsgefahr nicht zulässig waren, denn das erforderliche Anzugsdrehmoment läßt sich so festlegen, daß nur die Dichtigkeit gewährleistet wird, ohne auf die Gefahr der selbsttätigen Lockerung Rücksicht nehmen zu müssen.The high pressure also comes into effect at the other end of the external thread section via the pressure compensation path, so that the occurrence of a loosening moment is avoided under pressure surges. The requirements for observing very precise tightening torques can be reduced due to the elimination of the risk of automatic loosening. In particular with larger thread diameters, for example of 16 mm or more, material pairings can be realized that were not previously permitted due to the acute risk of loosening, because the required tightening torque can be determined so that only the tightness is guaranteed without the risk of automatic loosening To have to be considerate.

In der Einschraubventil-Anordnung pflanzt sich der im Hochdruckbereich wirksame Druck bis zu der unter der Anzugsspannung der gewindeaktivierten Dichtung fort, so daß Druckstöße keine Lockerungskraft in der Gewindeverbindung erzeugen können. Selbst bei moteratem Anzugsdrehmoment, gerade ausreichend für die erforderliche Dichtwirkung, wird ein Lockern des Einschraubventils vermieden.In the screw-in valve arrangement, the pressure effective in the high pressure range propagates up to that under the tightening tension of the thread-activated seal, so that pressure surges cannot produce any loosening force in the threaded connection. Loosening of the screw-in valve is avoided even when the torque is tight, just sufficient for the required sealing effect.

Gemäß Anspruch 2 ist das Ventilgehäuse selbst mit dem Druckausgleichsweg ausgestattet. Unabhängig davon, in welche Gewindebohrung oder welchen Grundkörper das Einschraubventil eingeschraubt wird, ist stets die Gefahr einer selbsttätigen Lockerung ausgeschlossen.According to claim 2, the valve housing itself is equipped with the pressure compensation path. Regardless of which threaded hole or which body the screw-in valve is screwed into, there is always no risk of automatic loosening.

Gemäß Anspruch 3 wird der Druckausgleichsweg auf herstellungstechnisch einfachem Weg durch lokale Abtragungen im Gewindebereich am Ventilgehäuse vorbestimmt.According to claim 3, the pressure compensation path is predetermined in a technically simple way by local abrasion in the threaded area on the valve housing.

Alternativ wird gemäß Anspruch 4 im Außengewinde eine Schlitzung von Gewindegängen vorgesehen, so daß sich der Druck über die Schlitze ausgleicht.Alternatively, according to claim 4, a slitting of threads is provided in the external thread, so that the pressure balances out through the slits.

Zu Anspruch 5 ist eine baulich einfache und wirkungsvolle Lösung des Druckausgleichswegs angegeben.A structurally simple and effective solution of the pressure compensation path is given for claim 5.

Dabei ist hervorzuheben, daß idealerweise der Druckausgleichsweg beide Enden des Außengewindeabschnittes miteinander verbinden sollte. Eine weitgehende Beseitigung der Lockerungsgefahr läßt sich jedoch auch erreichen, wenn der Druckausgleichsweg nur im niederdruckseitigen Endbereich des Außengewindes mündet, ohne vollständig in den Niederdruckbereich zu führen.It should be emphasized that ideally the pressure equalization path should connect both ends of the external thread section to one another. An extensive elimination of the risk of loosening can, however, also be achieved if the pressure equalization path only opens into the low-pressure side end area of the external thread, without leading completely into the low-pressure area.

Gemäß Anspruch 7 ist der Druckausgleichsweg herstellungstechnisch bequem im Ventilgehäuse vorgesehen.According to claim 7, the pressure compensation path is conveniently provided in the valve housing in terms of manufacturing technology.

Gemäß Anspruch 8 ist hingegen alternativ der Druckausgleichsweg im Grundkörper in Form eines Kanals gebildet.According to claim 8, however, the pressure compensation path is alternatively formed in the form of a channel in the base body.

Gemäß Anspruch 9 wird der Druckausgleichsweg in der Gewindeverbindung gebildet, und zwar gemäß Anspruch 10 durch lokale Abtragungen, wie Abschleifen oder Schlitzen, oder gemäß Anspruch 11 durch bewußte Auswahl einer an sich unüblich losen Gewindepassung.According to claim 9, the pressure equalization path is formed in the threaded connection, specifically according to claim 10 by local abrasion, such as grinding or slitting, or according to claim 11 by deliberate selection of a thread fit that is unusually loose.

Gemäß Anspruch 12 läßt sich das Einschraubventil bzw. die Einschraubventil-Anordnung für unterschiedliche Ventilfunktionen verwenden, bei denen die Gefahr von Druckstößen an der Hochdruckseite existiert.According to claim 12, the screw-in valve or the screw-in valve arrangement can be used for different valve functions in which there is a risk of pressure surges on the high-pressure side.

Gemäß Anspruch 13 werden zweckmäßigerweise Einschraubventil-Anordnungen gegen Lockern geschützt, deren Gewindekerndurchmesser ≥ 16 mm, vorzugsweise ≥ 20 mm, ist.According to claim 13 screw-in valve arrangements are expediently protected against loosening, the thread core diameter of which is ≥ 16 mm, preferably ≥ 20 mm.

Anhang der Zeichnung wird eine Ausführungsform eines Einschraubventils erläutert. In Fig. 1 ist, teilweise in einem Achsschnitt, ein Einschraubventil in einer Einschraubventil-Anordnung gezeigt.An embodiment of a screw-in valve is explained in the appendix of the drawing. 1 shows a screw-in valve in a screw-in valve arrangement, partly in an axial section.

Ein Einschraubventil V, z.B. ein magnetbetätigtes Wege-Sitzventil, weist ein hülsenförmig auslaufendes Ventilgehäuse S auf, in dem für die Ventilfunktion benötigte Ventilkomponenten 9 untergebracht sind, die bei der gezeigten Ausführungsform nach unten über das Ventilgehäuse S überstehen. Das Einschraubventil V ist eine handelsübliche Baueinheit, die in eine den Anforderungen des Herstellers entsprechend gebildete Gewindebohrung B eines Grundkörpers G einzuschrauben bzw. eingeschraubt ist. In der in Fig. 1 gezeigten Einschraubventil-Anordnung E ist das Ventilgehäuse S mit einem axialen Außengewindeabschnitt F in einen Innengewindeabschnitt K der Gewindebohrung B derart eingeschraubt, daß eine in einer Umfangsnut 1 des Ventilgehäuses S positionierte Dichtung C für eine geforderte Abdichtwirkung nach außen komprimiert wird. Eine Flanke 2 der Ringnut 1 definiert einen Endbereich des Außengewindeabschnittes F, während eine Schulter 3 den anderen Endbereich des Außengewindeabschnittes F definiert. Im Abstand unterhalb der freien Außenseite A des Grundkörpers G münden Bohrungen 4, 5 in die Gewindebohrung B. Die Bohrungen 4, 5 bilden Druckmittel-Kanäle, die durch eine von einer Schulter 6 an der Ventilkomponente 9 an einer Bohrungsschulter 8 komprimierte Dichtung 7 voneinander getrennt sind. Am innenliegenden Endbereich 3 des Außengewindeabschnittes F liegt ein Hochdruckbereich H vor, während am oberen Endbereich 2 des Außengewindeabschnittes F ein Niederdruck- oder Umgebungsdruckbereich L vorliegt.A screw-in valve V, e.g. a solenoid-operated directional seat valve has a sleeve-shaped valve housing S in which valve components 9 required for the valve function are accommodated, which in the embodiment shown protrude downward beyond the valve housing S. The screw-in valve V is a commercially available structural unit which is to be screwed or screwed into a threaded bore B of a base body G which is formed in accordance with the manufacturer's requirements. In the screw-in valve arrangement E shown in FIG. 1, the valve housing S is screwed with an axial external thread section F into an internal thread section K of the threaded bore B such that a seal C positioned in a circumferential groove 1 of the valve housing S is compressed to the outside for a required sealing effect . A flank 2 of the annular groove 1 defines an end region of the externally threaded section F, while a shoulder 3 defines the other end region of the externally threaded section F. At a distance below the free outside A of the base body G bores 4, 5 open into the threaded bore B. The bores 4, 5 form pressure medium channels which are separated from one another by a seal 7 compressed by a shoulder 6 on the valve component 9 on a bore shoulder 8 are. A high-pressure area H is present at the inner end area 3 of the external thread section F, while a low-pressure or ambient pressure area L is present at the upper end area 2 of the external thread section F.

Erfindungsgemäß wird der im Hochdruckbereich H vorliegende Druck mittels eines Druckausgleichsweges D in den Niederdruck- oder Umgebungsdruckbereich L übertragen, d.h. gegebenenfalls bis an die Dichtung C, damit die Gewindeverbindung in axialer Richtung zumindest weitestgehend druckausgeglichen ist und Druckstöße im Hochdruckbereich H kein Lockerungsdrehmoment für den Außengewindeabschnitt F des Ventilgehäuses S erzeugen.According to the present invention, the pressure present in the high-pressure region H is transferred to the low-pressure or ambient pressure region L by means of a pressure compensation path D, that is to say possibly up to the seal C, so that the threaded connection is at least largely pressure-balanced in the axial direction and pressure surges in the High pressure area H does not generate any loosening torque for the external thread section F of the valve housing S.

Der Druckausgleichsweg D kann konstruktiv unterschiedlich ausgebildet sein. Es ist in Fig. 1 nur ein Druckausgleichsweg D angedeutet, obwohl in der Praxis über den Umfang der Gewindeverbindung verteilt mehrere Druckausgleichswege vorgesehen sein könnten.The pressure compensation path D can be designed differently. Only one pressure compensation path D is indicated in FIG. 1, although in practice several pressure compensation paths could be provided distributed over the circumference of the threaded connection.

In ausgezogenen Linien ist eine im Ventilgehäuse S gebohrte Längsbohrung 10 vorgesehen, die innerhalb des Außengewindeabschnittes F und knapp unterhalb deren Gewindegängen zwischen den Schultern 2, 3 verläuft. Strichpunktiert ist ein alternativer Druckausgleichsweg D' angedeutet, der als Kanal 11 im Grundkörper G die Hochdruckseite mit der Niederdruckseite H, L verbindet. Als weitere Alternative ist der Druckausgleichsweg D'' in der Gewindeverbindung angedeutet. In diesem Fall könnten die Gewindekämme des Außengewindeabschnittes F und/oder die Gewindekämme des Innengewindeabschnittes K lokal, z.B. durch Abschleifen oder Abfräsen oder Abflachen, bearbeitet sein. Denkbar ist es ferner, axiale Schlitze durch die Gewindegänge zu formen, z.B. durch Schleifen oder Fräsen, und zwar in den Gewindegängen des Außengewindeabschnittes F und/oder des Innengewindeabschnittes K. Schließlich könnte der Druckausgleichsweg D'' auch dadurch gebildet werden, daß eine relativ lose Passung zwischen dem Innengewindeabschnitt K und dem Außengewindeabschnitt F gewählt wird, um zwischen den Gewindegängen den Druck von der Hochdruckseite zur Niederdruckseite L zu übertragen.In solid lines, a longitudinal bore 10 is drilled in the valve housing S and runs within the external thread section F and just below the threads between the shoulders 2, 3. An alternate pressure compensation path D 'is indicated by dash-dotted lines and connects the high-pressure side to the low-pressure side H, L as channel 11 in the base body G. As a further alternative, the pressure compensation path D '' is indicated in the threaded connection. In this case, the thread combs of the external thread section F and / or the thread combs of the internal thread section K could be local, e.g. by grinding or milling or flattening. It is also conceivable to form axial slots through the threads, e.g. by grinding or milling, namely in the threads of the external thread section F and / or the internal thread section K. Finally, the pressure compensation path D '' could also be formed by choosing a relatively loose fit between the internal thread section K and the external thread section F to switch between to transfer the threads from the high pressure side to the low pressure side L.

Claims (13)

Einschraubventil (V), insbesondere für die Hochdruckhydraulik, mit einem Ventilgehäuse (S), an dem zwischen einer Niederdruck- oder Umgebungsdruckseite (L) und einer Hochdruckseite (H) wenigstens ein Einschraub-Außengewindeabschnitt (F) verläuft, dadurch gekennzeichnet, daß das Ventilgehäuse (S) wenigstens einen die Niederdruck- oder Umgebungsdruckseite (L) des Außengewindeabschnitts (F) mit der Hochdruckseite (H) desselben Außengewindeabschnittes (F) verbindenden Druckausgleichsweg (D, D'') aufweist.Screw-in valve (V), in particular for high-pressure hydraulics, with a valve housing (S), on which at least one screw-in external thread section (F) runs between a low-pressure or ambient pressure side (L) and a high-pressure side (H), characterized in that the valve housing (S) has at least one pressure compensation path (D, D '') connecting the low-pressure or ambient pressure side (L) of the external thread section (F) to the high-pressure side (H) of the same external thread section (F). Einschraubventil nach Anspruch 1, dadurch gekennzeichnet, daß der Druckausgleichsweg (D) eine den Gewindeabschnitts-Anfangsbereich (3) mit dem Gewindeabschnittsendbereich (2) verbindende Axialbohrung (10) im Ventilgehäuse (S) ist.Screw-in valve according to claim 1, characterized in that the pressure compensation path (D) is an axial bore (10) in the valve housing (S) connecting the thread section start area (3) with the thread section end area (2). Einschraubventil nach Anspruch 1, dadurch gekennzeichnet, daß der Druckausgleichsweg (D'') durch lokale Abtragungen von Gewindekämmen des Außengewindeabschnittes (F), z.B. durch Abschleifen bzw. Abflachen, gebildet ist.Screw-in valve according to claim 1, characterized in that the pressure compensation path (D '') is formed by local abrasion of thread combs of the external thread section (F), for example by grinding or flattening. Einschraubventil nach Anspruch 1, dadurch gekennzeichnet, daß der Druckausgleichsweg (D'') durch Schlitze (12) in Gewindegängen des Außengewindeabschnittes (F) gebildet ist.Screw-in valve according to claim 1, characterized in that the pressure equalization path (D '') is formed by slots (12) in threads of the external thread section (F). Einschraubventil nach Anspruch 1, dadurch gekennzeichnet, daß das Ventilgehäuse (S) am dem Hochdruckbereich (H) abgewandten Endbereich des Außengewindeabschnittes (F) eine Umfangsnut (1) zur Aufnahme eines Dichtringes (C) aufweist, und daß der Druckausgleichsweg (D) als Bohrung (10) unterhalb der Gewindegänge und annähernd parallel zur Achse des Außengewindeabschnittes (F) vom Hochdruckbereich-Endbereich (3) des Außengewindeabschnittes (F) bis zu einer den Niederdruck-Endbereich definierenden Flanke (2) der Umfangsnut (1) ausgebildet ist.Screw-in valve according to Claim 1, characterized in that the valve housing (S) has a circumferential groove (1) for receiving a sealing ring (C) at the end region of the external thread section (F) facing away from the high pressure region (H), and in that the pressure compensation path (D) is a bore (10) below the threads and approximately parallel to the axis of the external thread section (F) from the high pressure area end area (3) of the external thread section (F) to a flank (2) of the circumferential groove (1) defining the low pressure end area. Einschraubventil-Anordnung (E), insbesondere für die Hochdruckhydraulik, mit einem in einer Gewindebohrung (B) eines Grundkörpers (G) angeordneten Ventilgehäuse (S), das einen sich zwischen einem Niederdruck- bzw. Umgebungsdruckbereich (L) und einem Hochdruckbereich (H) erstreckenden, in einen Innengewindeabschnitt (K) der Gewindebohrung (B) eingeschraubten Außengewindeabschnitt (F) aufweist, wobei im Niederdruck- oder Umgebungsdruckbereich (L) eine unter der Gewindeanzugsspannung aktivierte Abdichtung (C) vorgesehen ist, dadurch gekennzeichnet, daß zwischen dem Hochdruckbereich (H) und dem Niederdruck- bzw. Umgebungsdruckbereich (L) wenigstens ein sich vom Hochdruckbereich (H) bis zumindest nahe an die dem Hochdruckbereich (H) zugewandte Seite der Abdichtung (C) erstreckender Druckausgleichsweg (D, D', D'') angeordnet ist, mit dem der im Hochdruckbereich (H) auf den Außengewindeabschnitt (F) wirkende Druck in den Niederdruck- bzw. Umgebungsdruckbereich (L) des Außengewindeabschnittes (F) übertragbar ist.Screw-in valve arrangement (E), in particular for high-pressure hydraulics, with a valve housing arranged in a threaded bore (B) of a base body (G) (S), which has an external thread section (F) which extends between a low-pressure or ambient pressure area (L) and a high-pressure area (H) and is screwed into an internally threaded section (K) of the threaded bore (B), wherein in the low-pressure or ambient pressure area ( L) a seal (C) activated under the thread tightening tension is provided, characterized in that between the high pressure area (H) and the low pressure or ambient pressure area (L) at least one of the high pressure area (H) and at least close to that of the high pressure area ( H) facing side of the seal (C) extending pressure compensation path (D, D ', D'') is arranged, with which the pressure acting in the high pressure area (H) on the external thread section (F) in the low pressure or ambient pressure area (L) of the external thread section (F) is transferable. Einschraubventil-Anordnung nach Anspruch 6, dadurch gekennzeichnet, daß der Druckausgleichsweg (D) eine die Endbereiche (2, 3) des Außengewindeabschnittes (F) verbindende Bohrung (10) im Ventilgehäuse (S) ist.Screw-in valve arrangement according to claim 6, characterized in that the pressure compensation path (D) is a bore (10) in the valve housing (S) connecting the end regions (2, 3) of the external thread section (F). Einschraubventil-Anordnung nach Anspruch 6, dadurch gekennzeichnet, daß der Druckausgleichsweg (D') ein vom Hochdruckbereich (H) zur Abdichtung (C) verlaufender Kanal (11) im Grundkörper (G) ist.Screw-in valve arrangement according to claim 6, characterized in that the pressure compensation path (D ') is a channel (11) in the base body (G) which runs from the high pressure region (H) to the seal (C). Einschraubventil-Anordnung nach Anspruch 6, dadurch gekennzeichnet, daß der Druckausgleichsweg (D'') zwischen den ineinandergreifenden Gewindegängen des Innengewinde- und des Außengewindeabschnittes (F, K) ausgebildet ist.Screw-in valve arrangement according to claim 6, characterized in that the pressure compensation path (D '') is formed between the interlocking threads of the internal thread and the external thread section (F, K). Einschraubventil-Anordnung nach Anspruch 9, dadurch gekennzeichnet, daß Gewindegänge des Innen- und/oder Außengewindeabschnittes (F, K) lokal abgetragen sind, z.B. durch Abschleifen, Abflachen oder Schlitzen.Screw-in valve arrangement according to claim 9, characterized in that threads of the internal and / or external thread section (F, K) are removed locally, for example by grinding, flattening or slitting. Einschraubventil-Anordnung nach Anspruch 6, dadurch gekennzeichnet, daß die Passung zwischen den Innen- und Außengewindeabschnitten (F, K) gegenüber der Norm bewußt vergrößert ist, z.B. mit einem den Druckausgleichsweg (D'') bildenden Passungsspiel.Screw-in valve arrangement according to claim 6, characterized in that the fit between the internal and external thread sections (F, K) is opposite the standard is deliberately enlarged, for example with a fit clearance forming the pressure compensation path (D ''). Einschraubventil-Anordnung nach Anspruch 6, dadurch gekennzeichnet, daß das Ventilgehäuse (S) Komponentengruppen (9) enthält, die zwischen in die Gewindebohrung (B) mündenden Druckmittelkanälen (4, 5) die Funktion zumindest eines der folgenden Ventiltypen erzeugen: Druckventil, Sitz-Wegeventil, Druckgefälleventil, Abschaltventil, Drossel- und/oder Absperrventil, Rückschlagventil, Rückschlagventil entsperrbar, Druckminderventil, Druckbegrenzungsventil, Stromventil, Schlitzdrosselventil und Druckregelventil.Screw-in valve arrangement according to claim 6, characterized in that the valve housing (S) contains component groups (9) which produce the function of at least one of the following valve types between pressure medium channels (4, 5) opening into the threaded bore (B): pressure valve, seat valve Directional control valve, pressure drop valve, shut-off valve, throttle and / or shut-off valve, check valve, check valve can be unlocked, pressure reducing valve, pressure relief valve, flow control valve, slot throttle valve and pressure control valve. Einschraubventil-Anordnung nach Anspruch 6, dadurch gekennzeichnet, daß der Gewindekerndurchmesser der Außen- bzw. Innengewindeabschnitte (F, K) ≥ 16 mm, vorzugsweise ≥ 20 mm ist.Screw-in valve arrangement according to claim 6, characterized in that the thread core diameter of the external or internal thread sections (F, K) is ≥ 16 mm, preferably ≥ 20 mm.
EP98124556A 1998-04-20 1998-12-22 Screw-in valve and valve assembly Expired - Lifetime EP0952356B1 (en)

Applications Claiming Priority (2)

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DE29807100U 1998-04-20
DE29807100U DE29807100U1 (en) 1998-04-20 1998-04-20 Screw-in valve and screw-in valve arrangement

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EP0952356A1 true EP0952356A1 (en) 1999-10-27
EP0952356B1 EP0952356B1 (en) 2004-04-28

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US6783337B2 (en) * 2002-11-13 2004-08-31 Caterpillar Inc Check valve seal assembly

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US5217260A (en) * 1992-02-13 1993-06-08 Fred Knapp Engraving Co., Inc. Control valve with universal porting feature
EP0676548A1 (en) * 1994-03-11 1995-10-11 Voac Hydraulics Boras Ab Valve cartridge
US5584323A (en) * 1994-06-17 1996-12-17 Unisia Jecs Corporation Fluid control valve
US5617890A (en) * 1994-09-03 1997-04-08 Robert Bosch Gmbh Electromagnetically operable pressure-regulation valve
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DE19625349A1 (en) * 1996-06-25 1998-01-02 Rexroth Mannesmann Gmbh Solenoid actuated seat valve

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EP0952356B1 (en) 2004-04-28
US6192921B1 (en) 2001-02-27
DE59811280D1 (en) 2004-06-03

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