EP0952356B1 - Screw-in valve and valve assembly - Google Patents
Screw-in valve and valve assembly Download PDFInfo
- Publication number
- EP0952356B1 EP0952356B1 EP98124556A EP98124556A EP0952356B1 EP 0952356 B1 EP0952356 B1 EP 0952356B1 EP 98124556 A EP98124556 A EP 98124556A EP 98124556 A EP98124556 A EP 98124556A EP 0952356 B1 EP0952356 B1 EP 0952356B1
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- EP
- European Patent Office
- Prior art keywords
- valve
- thread section
- pressure
- screw
- high pressure
- 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
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Classifications
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- 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
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- 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
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- 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
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- 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 3.
- 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. for block constructions, advantageous.
- Typical practical applications are described, for example, in product formation P 7710-1 "Screw-in valves type C", from Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co. KG, edition 03/95 or the publication D 7490-1 "2 / 2-way screw-in vortile EM "from Heilmeier & Weinlein Factory for 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 bore 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 hole 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 thread engagement can allow pressure equalization between the high-pressure side and the low-pressure side in some installation cases, for example depending on manufacturing tolerances.
- the thread engagement always has a throttling effect, so that pressure equalization occurs at most with a delay, and especially in the event of a pressure surge on the high-pressure side, a considerable compressive force builds up on the valve housing opposite to the screwing direction, from which a considerable loosening moment occurs via the thread pitch for the threaded connection, especially in the case of large-diameter valve housings, such as those used to control high working pressures.
- valve housing Since, as a rule, the higher pressure acts on the valve housing in the opposite direction to the screw-in direction and pressure surges occur during operation, there is a loosening moment for the threaded connection, which, for. B. after 50,000 load changes, the valve housing can loosen in the threaded hole 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. .
- 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, so that a loosening moment is avoided under pressure surges.
- the requirements for observing very precise tightening torques can be alleviated 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 valve housing is equipped with the pressure compensation path. Regardless of which threaded hole or which body the screw-in valve is screwed into, the risk of an automatic locating is always excluded.
- a slot of threads can be provided in the external thread, so that the pressure over the slots is balanced.
- 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.
- the pressure compensation path is conveniently formed in the valve housing or alternatively in the base body in the form of a channel.
- the pressure compensation path can also be formed by slots in the threads in the threaded connection.
- 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 compensation path only opens into the low-pressure side end area of the external thread, without leading completely into the low-pressure area.
- 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
- 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 do not generate any loosening torque for the external thread section F of the valve housing S.
- the pressure equalization 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 drilled in the valve housing S is provided, which runs within the external thread section F and just below the threads between the shoulders 2, 3.
- Dash-dot lines indicate an alternative pressure compensation path D ', which 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.
- axial slots could be formed through the threads, for example by grinding or milling, in the threads of the external thread section F and / or the internal thread section K.
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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)
- Closures For Containers (AREA)
- Glass Compositions (AREA)
- Details Of Valves (AREA)
- Lift Valve (AREA)
Description
Die Erfindung betrifft ein Einschraubventil gemäß dem Oberbegriff des Anspruchs 1 bzw. eine Einschraubventil-Anordnung gemäß dem Oberbegriff des Anspruchs 3.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 3.
Einschraubventile bzw. Einschraubventil-Anordnungen (DE 196 25 349 A) sind in der Hochdruckhydraulik zur platzsparenden Umsetzung verschiedener Ventilfunktionsvarianten, z.B. bei Blockkonstruktionen, vorteilhaft. Typische Anwendungsfälle aus der Praxis sind beispielsweise beschrieben in der Produktformation 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-Einschraubvebtile EM" der Firma Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co. KG, März 1996. Die Gewindebohrung, in welche das Einschraubventil eingeschraubt ist, 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 (DE 196 25 349 A) are used in high-pressure hydraulics for space-saving implementation of various valve function variants, e.g. for block constructions, advantageous. Typical practical applications are described, for example, in product formation P 7710-1 "Screw-in valves type C", from Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co. KG, edition 03/95 or the publication D 7490-1 "2 / 2-way screw-in vortile EM "from Heilmeier & Weinlein Factory for 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 bore 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 hole 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.
Bei der Einschraubventil-Anordnung gemäß DE 196 25349 A kann bei manchen Einbaufällen, z.B. abhängig von Herstellungstoleranzen, der Gewindeeingriff einen Druckausgleich zwischen der Hochdruckseite und der Niederdruckseite zulassen. Jedoch hat der Gewindeeingriff stets eine Drosselwirkung, so dass sich ein Druckausgleich allenfalls verzögert einstellt, und sich speziell bei einem Druckstoß an der Hochdruckseite zunächst eine erhebliche Druckkraft auf das Ventilgehäuse entgegengesetzt zur Einschraubrichtung aufbaut, aus der über die Gewindesteigung ein beträchtliches Lockerungsmoment für die Gewindeverbindung entsteht, insbesondere bei großdurchmessrigen Ventilgehäusen, wie sie zur Steuerung hoher Arbeitsdrücke benutzt werden.In the screw-in valve arrangement according to DE 196 25349 A, the thread engagement can allow pressure equalization between the high-pressure side and the low-pressure side in some installation cases, for example depending on manufacturing tolerances. However, the thread engagement always has a throttling effect, so that pressure equalization occurs at most with a delay, and especially in the event of a pressure surge on the high-pressure side, a considerable compressive force builds up on the valve housing opposite to the screwing direction, from which a considerable loosening moment occurs via the thread pitch for the threaded connection, especially in the case of large-diameter valve housings, such as those used to control high working pressures.
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. Einschraubventilanordnungen Weiterer Stand der Technik ist zu finden 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 und US 5 584 323 A, wo aber in keinem Fall ein Druckausgleich über ein Einschraubgewinde angesprochen wird.Since, as a rule, the higher pressure acts on the valve housing in the opposite direction to the screw-in direction and pressure surges occur during operation, there is a loosening moment for the threaded connection, which, for. B. after 50,000 load changes, the valve housing can loosen in the threaded hole 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. . The like.), this is a significant disadvantage of screw-in valves or screw-in valve arrangements 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 compensation via a screw-in thread is addressed.
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 erfindungsgemäß mit den Merkmalen des Anspruchs 1 oder des nebengeordneten Anspruchs 3 gelöst.The object is achieved according to the invention with the features of claim 1 or the independent claim 3.
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. Das Ventilgehäuse ist mit dem Druckausgleichsweg ausgestattet. Unabhängig davon, in welche Gewindebohrung oder welchen Grundkörper das Einschraubventil eingeschraubt wird, ist stets die Gefahr einer selbsttätigen Lokkerung ausgeschlossen. Alternativ kann im Außengewinde eine Schlitzung von Gewindegängen vorgesehen sein, so daß sich der Druck über die Schlitze ausgleicht.Via the pressure equalization path, the high pressure also comes into effect at the other end of the external thread section, so that a loosening moment is avoided under pressure surges. The requirements for observing very precise tightening torques can be alleviated 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. The valve housing is equipped with the pressure compensation path. Regardless of which threaded hole or which body the screw-in valve is screwed into, the risk of an automatic locating is always excluded. Alternatively, a slot of threads can be provided in the external thread, so that the pressure over the slots is balanced.
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. Hierbei ist der Druckausgleichsweg herstellungstechnisch bequem im Ventilgehäuse oder alternativ im Grundkörper in Form eines Kanals gebildet. Der Druckausgleichsweg kann auch durch Schlitze in den Gewindegängen in der Gewindeverbindung gebildet sein.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. Here, the pressure compensation path is conveniently formed in the valve housing or alternatively in the base body in the form of a channel. The pressure compensation path can also be formed by slots in the threads in the threaded connection.
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 compensation path only opens into the low-pressure side end area of the external thread, without leading completely into the low-pressure area.
Gemäß Anspruch 4 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 4, 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 5 werden zweckmäßigerweise Einschraubventil-Anordnungen gegen Lockern geschützt, deren Gewindekerndurchmesser ≥ 16 mm, vorzugsweise ≥ 20 mm, ist.According to claim 5, 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 appended 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 do 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 equalization 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 altemativer 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 axiale Schlitze durch die Gewindegänge geformt sein, z.B. durch Schleifen oder Fräsen, und zwar in den Gewindegängen des Außengewindeabschnittes F und/oder des Innengewindeabschnittes K.In solid lines, a longitudinal bore 10 drilled in the valve housing S is provided, which runs within the external thread section F and just below the threads between the shoulders 2, 3. Dash-dot lines indicate an alternative pressure compensation path D ', which 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, axial slots could be formed through the threads, for example by grinding or milling, in the threads of the external thread section F and / or the internal thread section K.
Claims (5)
- Screw-in cartridge valve (V), particularly for high pressure hydraulics, including a valve housing (S) having an exterior screw-in thread section (F) extending between a low pressure or ambient pressure area (L) and a high pressure area (H), characterised in that said valve housing (S) comprises at least one pressure equalisation path (D, D") interconnecting the low pressure or ambient pressure area (L) of the exterior thread section (F) with the high pressure area (H) of the same exterior thread section (F), the equalisation path being formed either as an axial bore (10) or as axial slits (12) in threads of the exterior thread section, respectively, for connecting a thread section start portion (3) with the thread section end portion (2).
- Screw-in cartridge valve as in claim 1, characterised in that said valve housing (S) is provided at its end portion of the exterior thread section (F) opposite to said high pressure area (H) with a circumferential groove (1) for receiving a sealing, and that said axial bore (10) extends below the thread and essentially parallel to the axis of the exterior thread section (F) from said high pressure area (H) to one flank (2) of said circumferential groove (1).
- Screw-in cartridge valve assembly (E), particularly for high pressure hydraulics, comprising a valve housing (S) provided in a threaded bore (B) of a base body (G), said valve housing (S) having an exterior thread section (F) extending between a low pressure or ambient pressure area (L) and a high pressure area (H), said exterior thread section (F) being screwed into an interior thread section (K) of said threaded bore (B), and further comprising a sealing (C) in said low pressure or ambient area (L) which sealing is activated by means of the thread tightening tension, characterised in that at least one pressure equalisation path (D, D', D") is provided between said high pressure area (H) and said low pressure or ambient pressure area (L) which extends from said high pressure area (H) at least to close to the side of the sealing (C) facing said high pressure area (H), the equalisation path being formed either as a bore (10) in the valve housing (S) for connecting both end portions of said exterior thread section (F), or as a channel (11) formed in the base body (G) and extending from said high pressure area (H) to said sealing (C), or as axial slits (12) in threads of said interior thread section (K) and/or of said exterior thread section (F), respectively, by means of which pressure equalisation path the pressure acting in said high pressure area (H) on said exterior thread section (F) is transmitted into said low pressure or ambient pressure area (L) of said exterior thread section (F):
- Screw-in cartridge valve assembly as in claim 3, characterised in that said valve housing (S) contains component groups (9) which provide the function of at least one of the following valve types between pressure fluid passages (4, 5) opening into said thread bore (B): pressure valve, multi-ways seat valve, pressure drop valve, switch-off valve, throttle valve and/or blocking valve, check valve, check valve with pilot operation, pressure reducing valve, pressure limiting valve, flow control valve, slot throttling valve, and pressure regulating valve.
- Screw-in cartridge valve assembly as in claim 3, characterised In that the thread root diameter of said exterior or interior thread sections (F, K) is equal to or larger than 16 mm, preferably equal to or larger than 20 mm.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE29807100U DE29807100U1 (en) | 1998-04-20 | 1998-04-20 | Screw-in valve and screw-in valve arrangement |
DE29807100U | 1998-04-20 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0952356A1 EP0952356A1 (en) | 1999-10-27 |
EP0952356B1 true EP0952356B1 (en) | 2004-04-28 |
Family
ID=8055992
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98124556A Expired - Lifetime EP0952356B1 (en) | 1998-04-20 | 1998-12-22 | Screw-in valve and valve assembly |
Country Status (3)
Country | Link |
---|---|
US (1) | US6192921B1 (en) |
EP (1) | EP0952356B1 (en) |
DE (2) | DE29807100U1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6783337B2 (en) * | 2002-11-13 | 2004-08-31 | Caterpillar Inc | Check valve seal assembly |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4823832A (en) * | 1984-07-11 | 1989-04-25 | Harden Industries, Inc. | Cartridge valve |
DE3440198A1 (en) * | 1984-11-03 | 1986-05-22 | F.W. Oventrop Arn. Sohn Kg, 5787 Olsberg | THERMOSTATICALLY ACTUATED VALVE |
US5050633A (en) * | 1989-06-19 | 1991-09-24 | Emhart Inc. | Fluid valve |
US5217260A (en) * | 1992-02-13 | 1993-06-08 | Fred Knapp Engraving Co., Inc. | Control valve with universal porting feature |
SE507067C2 (en) * | 1994-03-11 | 1998-03-23 | Voac Hydraulics Boraas Ab | Electromagnetic pilot valve insert with interchangeable flow restrictive end closure |
JPH084937A (en) * | 1994-06-17 | 1996-01-12 | Unisia Jecs Corp | Fluid control valve |
DE4431457C2 (en) * | 1994-09-03 | 1997-02-20 | Bosch Gmbh Robert | Electromagnetically operated pressure control valve |
US5590683A (en) * | 1994-10-11 | 1997-01-07 | Bennett; Barry D. | Compensating relief valve |
US5718264A (en) * | 1996-06-10 | 1998-02-17 | Sturman Industries | High speed 3-way control valve |
DE19625349A1 (en) * | 1996-06-25 | 1998-01-02 | Rexroth Mannesmann Gmbh | Solenoid actuated seat valve |
-
1998
- 1998-04-20 DE DE29807100U patent/DE29807100U1/en not_active Expired - Lifetime
- 1998-12-22 EP EP98124556A patent/EP0952356B1/en not_active Expired - Lifetime
- 1998-12-22 DE DE59811280T patent/DE59811280D1/en not_active Expired - Lifetime
-
1999
- 1999-03-24 US US09/275,143 patent/US6192921B1/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
EP0952356A1 (en) | 1999-10-27 |
US6192921B1 (en) | 2001-02-27 |
DE59811280D1 (en) | 2004-06-03 |
DE29807100U1 (en) | 1998-07-02 |
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