EP0829794B1 - Pressure reducing lift valve - Google Patents

Pressure reducing lift valve Download PDF

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Publication number
EP0829794B1
EP0829794B1 EP97107824A EP97107824A EP0829794B1 EP 0829794 B1 EP0829794 B1 EP 0829794B1 EP 97107824 A EP97107824 A EP 97107824A EP 97107824 A EP97107824 A EP 97107824A EP 0829794 B1 EP0829794 B1 EP 0829794B1
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EP
European Patent Office
Prior art keywords
pressure
piston
control piston
valve according
seat valve
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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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EP97107824A
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German (de)
French (fr)
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EP0829794A1 (en
Inventor
Anton Estendorfer
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Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
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Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet valves

Definitions

  • the invention relates to a pressure reducing seat valve in the preamble of the claim 1 specified Art.
  • Pressure reducing valves in which the reduced pressure opposes the closing element the spring and in the opening direction are applied in the high pressure hydraulics used for many purposes.
  • a pressure reducing valve is used in clamping devices of machine tools for setting the Clamping pressure, which is lower than the inlet pressure and possibly only approx. Can be 10% of the inlet pressure.
  • Pressure tightness is in the closed position indispensable in many applications with a pressure reducing valve. This Pressure tightness is a major advantage of pressure reducing poppet valves Leaky pressure reducing slide valves, which are used for pressure tightness need an additional solenoid or check valve in the closed position.
  • valves of the prior art are of a different kind because that Closing element from the inlet or pump pressure in the opening direction from Valve seat away and against the spring while the lower one Pressure downstream of the seat acts on the closing element in the closing direction.
  • the invention is based, a pressure reducing seat valve the task mentioned type to create the largely silent and long Tool life works.
  • the control spring lifts the closing element in the pressure reducing seat valve the reduced pressure on the control piston from the seat via the control piston.
  • the reduced pressure leads together with that of the inlet pressure in the closing direction acted upon the closing element the control piston back to the valve seat as soon as the reduced pressure corresponds to the set value.
  • the closing element becomes far from the valve seat lifted to the reduced pressure as quickly as possible on the set To keep height. Since usually only a small amount of pressure medium is required is to restore the reduced pressure, the control piston then quickly pushed back against the rule spring, so that there is fear that the closing element hits the valve seat firmly under the inlet pressure.
  • the hydraulic damping device first attacks the control piston, which is the Movement of the closing element controls and suppresses rapid game movements of the control piston, especially in the closing direction of the closing element. It does not come to the feared even with suddenly falling reduced pressure Rattling of the closing element. This creates an annoying noise suppresses and the pressure reducing seat valve remains functionally reliable over a long service life.
  • the closing element guided by the control piston, approaches Valve seat to set the reduced pressure or when the reduced pressure is reached To shut off the pressure without swinging and pounding several times. Only hydraulically dampen the closing movement of the control piston, also has the advantage of a rapid opening movement of the closing element to initiate the pressure adjustment without delay if the reduced pressure drops.
  • the pressure medium must act on the control piston during this intervention pass the throttled flow path against the control spring, whereby a too rapid closing movement of the control piston and consequently of the closing element is prevented.
  • the damping effect can be predetermined.
  • the hydraulic Damping device works in the manner of a pressure reducing seat valve integrated hydraulic shock absorber. It is favorable that the damping device is easily integrated into the special, proven seat valve concept at which the inlet or pump pressure the seat closing element in the closing direction and against the spring the reduced pressure against the spring and acts on the closing element in the opening direction.
  • the opening and hydraulically dampen the closing movements of the control piston may be appropriate for some requirements according to claim 2, the opening and hydraulically dampen the closing movements of the control piston.
  • claim 3 serves as a displacement element which is adjustable with the control piston Piston that also limits the restricted flow path.
  • the piston is loaded by the reduced pressure on both loading sides, see above In this regard, the control characteristic of the pressure reducing seat valve is not noticeable being affected.
  • the storage chamber has a double function, since it pressurized by the throttled flow path receives and to Actuation of the control piston against the control spring serves.
  • the displacement element of the hydraulic damping device forming piston s the additional function of a stroke limitation of the control piston, so that it is not moved too far into the spring chamber.
  • the throttled is according to claim 6
  • Flow path bypassed by a check valve that is in the direction of flow opens to the storage chamber and blocks in the opposite direction.
  • the check valve to save space in Piston arranged.
  • the embodiment according to claim 9 is technically simple.
  • the pressure medium for damping (in the closing direction or in the closing and opening direction of the control piston) flow through at least one channel running in the housing.
  • the plunger is designed as a flow guide trumpet.
  • the pressure medium coming from the valve seat is not only guided (without disturbing turbulence) brought to the side of the reduced pressure, but also to the throttled flow path, which makes the damping more even becomes.
  • the flow control trumpet is part of the hydraulic Damping device, because the throttled flow path and the storage chamber when steaming, e.g. would be overwhelmed due to the flow dynamics.
  • the embodiment according to claim 12 is technically favorable this course is an optimal support of the hydraulic damping device reached.
  • the pressure reducing seat valve can in a simple way to different working pressure ranges convert without having to change the expensive control spring and the housing.
  • a pressure reducing seat valve D according to FIG. 1 has a block-shaped connection housing G (which may be the housing of a consumer) one Stepped bore 1 in which an insert 2 with a valve seat S is positioned.
  • a screw-in housing insert 3 is used to position the insert 2, which is secured by a locking and sealing nut 4.
  • a control piston R is displaceable.
  • a spring F is provided in the spring chamber 19. The preload of the Regelfeder F is adjustable by conventional devices, not shown.
  • the Housing insert 3 forms a module unit with its components and can against other housing inserts 3 with the same external dimensions, but with differently dimensioned control piston R while using the control spring F and the housing can be replaced to make the pressure reducing seat valve D easy adapt to different working pressure ranges.
  • the valve seat S is located between a port P for the input or Pump pressure and a connection A for the reduced pressure.
  • the valve seat S is a closing element E, e.g. a hardened Steel ball associated with hardened valve seat S, which is supported in a holding part 5 and is guided in a screw 6 under the force of a weak closing spring 7 is guided.
  • the screw insert 6 is with screwed the insert 2 and supports a filter assembly 8.
  • housing insert 3 is a section with a larger than the bore 9 Provided diameter of a cylindrical housing wall 10 and a Has shoulder 15. Passages 11 connect the valve seat S to the connector A for the reduced pressure.
  • the control piston R is integrally connected to a larger piston K and one Tappet 12.
  • the piston K delimits a storage chamber 13 in which the control piston R with the reduced pressure against the force of the control spring F and in Opening direction can be acted upon.
  • the piston K delimits with its outer circumference a throttled flow path 14 to the storage chamber 13 and functions, e.g., as a stroke stop for the control piston R towards the shoulder 15.
  • the piston K forms together with the throttled flow path 14 and Storage chamber 13 a hydraulic damping device B for the control piston R, which adjusts the closing element E during opening and closing movements.
  • Desired pressure set at control spring F is available. This reduced pressure acts on the control piston R against the control spring F, the closing element E being held tightly on the seat S, also due to the inlet pressure in port P. The diminished one Pressure also prevails in the storage chamber 13. Sinks, for example due to Consumption, the reduced pressure, then the control spring F overcomes the counterforce of the control piston R and lifts the closing element E from the valve seat S. At this opening movement is via the throttled flow path 14 Pressure medium sucked into the storage chamber 13, causing the opening movement is steamed. If the pressure in port A approaches the set one again Value for the reduced pressure, then the control piston R against the Control spring F moved up and the closing element E to the valve seat S. brought or pressed on this. Contained in the storage chamber 13 Pressure fluid is due to the difference in diameter between the piston K and the control piston R pressed through the throttled flow path 14, see above that the closing movement is dampened.
  • the plunger 12 for guiding the closing element E is to be throttled Flow path 14 formed widening flow guide trumpet.
  • Fig. 2 is also indicated that instead of or in addition to the throttled Flow path 14 between the outer circumference of the piston K and the housing wall 10 (Fig. 1) a throttled flow path 14 'housed directly in the piston K. is, which is characterized by a symbolic choke 16.
  • Flow path 14 could (alternatively or additively) a separate one running in the housing Flow path 14 "can be provided with the throttle 16.
  • the piston K could be equipped with a pressure compensation groove or a seal (Fig. 3).
  • the piston K which is larger than the control piston R, is a displacement element forms, is also for a relatively small amount of pressure medium for filling the storage chamber 13 forced a strong flow, the throttled Flow path 14, 14 ', 14 "has to pass. With this even with a small amount of pressure medium powerful flow can be an effective hydraulic damping effect for the control piston R.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
  • Gas Separation By Absorption (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Superconductors And Manufacturing Methods Therefor (AREA)

Abstract

The valve (P) for high-pressure hydraulics has a regulating piston (R) acted on by the reduced pressure against a spring loading. This lifts a closure element (E) acted on by the input pressure in the closing direction towards the valve seat. The regulating piston has a hydraulic damper (B). The damper is effective at least for the closing movements of the closure element controlled by the regulating valve. There may be a hydraulic damper for the closing and opening movements of the closure element. The hydraulic damper may have a displacement element.

Description

Die Erfindung betrifft ein Druckminder-Sitzventil der im Oberbegriff des Anspruchs 1 angegebenen Art.The invention relates to a pressure reducing seat valve in the preamble of the claim 1 specified Art.

Druckminderventile, bei denen der geminderte Druck das Schließelement gegen die Feder und in Öffnungsrichtung beaufschlagt, werden in der Hochdruckhydraulik für sehr viele Einsatzzwecke verwendet. Beispielsweise dient ein Druckminder-ventil in Spannvorrichtungen von Werkzeugmaschinen zum Einstellen des Spanndrucks, der niedriger als der Eingangsdruck ist und gegebenenfalls nur ca. 10% des Eingangsdrucks betragen kann. Druckdichtheit in der Schließstellung ist bei einem Druckminder-Ventil in vielen Anwendungsfällen unabdingbar. Diese Druckdichtheit ist ein hauptsächlicher Vorteil von Druckminder-Sitzventilen gegenüber leckagebehafteten Druckminder-Schieberventilen, die für die Druckdichtheit in der Schließstellung ein zusätzliches Magnet- oder Rückschlagventil benötigen. In der Praxis kann bei Druckminder-Sitzventilen, insbesondere bei hoher Druckdifferenz zwischen dem Eingangsdruck und dem geminderten Druck, beim Öffnen jedoch ein störendes Rattern des Schließelements (störendes Geräusch und starker Verschleiß)auftreten. Aus diesen Gründen werden trotz höherer Herstellungskosten und des zusätzlichen Aufwandes für die Druckdichtheit Druckminder-Schieberventile häufig bevorzugt.Pressure reducing valves, in which the reduced pressure opposes the closing element the spring and in the opening direction are applied in the high pressure hydraulics used for many purposes. For example, a pressure reducing valve is used in clamping devices of machine tools for setting the Clamping pressure, which is lower than the inlet pressure and possibly only approx. Can be 10% of the inlet pressure. Pressure tightness is in the closed position indispensable in many applications with a pressure reducing valve. This Pressure tightness is a major advantage of pressure reducing poppet valves Leaky pressure reducing slide valves, which are used for pressure tightness need an additional solenoid or check valve in the closed position. In practice, with pressure reducing seat valves, especially with high Pressure difference between the inlet pressure and the reduced pressure, at However, opening a disturbing rattling of the closing element (disturbing noise and heavy wear) occur. For these reasons, despite higher manufacturing costs and the additional effort for pressure tightness pressure reducing slide valves often preferred.

Aus US-A-4190076 ist ein pneumatisches Druckminder-Ventil mit einem Membran-Regelkolben und Sitzventil-Ausbildung bekannt, wobei das Schließelement vom Eingangsdruck in Öffnungs- und vom geminderten Druck im Schließrichtung zum Sitz beaufschlagt wird. Mit dem Schließelement ist ein hydraulischer Dämpfungskolben in einer durch eine Membrane vom Strömungsweg separierten Dämpfungskammer in beiden Bewegungsrichtungen durch ein Joch fest gekoppelt. Durch die Kopplung mittels des Joches wirkt der Dämpfungskolben auf den Membran-Regelkolben ein. From US-A-4190076 is a pneumatic pressure reducing valve with a diaphragm control piston and seat valve training known, the closing element the inlet pressure in the opening direction and the reduced pressure in the closing direction is charged to the seat. With the closing element is a hydraulic damping piston in a membrane separated from the flow path Damping chamber coupled in both directions of movement by a yoke. By coupling by means of the yoke, the damping piston acts on the Diaphragm control piston.

Bei einem aus DE-A-3201432 bekannten Dreiwege-Druckregelventil mit zwei getrennten, jeweils einem Sitz zugeordneten Schließelementen arbeiten die Schließelemente wechselweise. An das die Verbindung vom Pumpenanschluß zum Rücklauf überwachenden Schließelement ist pumpendruckseitig ein Drosselkolben angeformt, der mit dem nach unten verlängerten Sitz für das Schließelement einen sogenannten Abblasquerschnitt des Schließelements verzögert zur Wirkung kommen läßt.In a three-way pressure control valve known from DE-A-3201432 work with two separate locking elements, each assigned to a seat the locking elements alternately. The connection from the pump connection the closing element monitoring the return is on the pump pressure side Throttle piston molded on, with the seat extended downwards for the Closing element delays a so-called blow-off cross section of the closing element has an effect.

Aus US-A-4603710 ist ein hydraulisches gedämpftes Rückschlagventil ohne federbelasteten Regelkolben bekannt, bei dem das Schließelement mittels eines geschleppten Verdrängerkolbens Druckmittel aus einer Speicherkammer über einen gedrosselten Strömungsweg verdrängt. Auf diese Weise wird in Schließrichtung des Rückschlagventils eine Dämpfung erzielt.From US-A-4603710 is a hydraulic damped check valve without spring-loaded Control piston known in which the closing element by means of a dragged displacer pressure medium from a storage chamber via a throttled flow path displaced. This way, the closing direction of the check valve achieves damping.

Aus US-A-4168721 ist ein Schieberventil mit Blendenfunktion und einer hydraulischen Dämpfungsvorrichtung bekannt. Die Dämpfungsvorrichtung arbeitet mit Druckmittel, das von der Pumpenseite über eine Drossel in eine Federkammer und von dieser über Drosselöffnungen zum Tank abströmt, um auf den Regelkolben und den damit einstückig verbundenen Blendenschieber einzuwirken.From US-A-4168721 is a slide valve with an orifice function and a hydraulic Damping device known. The damping device works with Pressure medium from the pump side via a throttle into a spring chamber and flows from this via throttle openings to the tank to the control piston and to act on the shutter slider connected in one piece.

Die vorerwähnten Ventile des Standes der Technik sind von anderer Art, da das Schließelement vom Eingangs- oder Pumpendruck in Öffnungsrichtung vom Ventilsitz weg und gegen die Feder beaufschlagt wird, während der niedrigere Druck stromab des Sitzes das Schließelement in Schließrichtung beaufschlagt.The aforementioned valves of the prior art are of a different kind because that Closing element from the inlet or pump pressure in the opening direction from Valve seat away and against the spring while the lower one Pressure downstream of the seat acts on the closing element in the closing direction.

Der Erfindung liegt die Aufgabe zugrunde, ein Druckminder-Sitzventil der eingangs genannten Art zu schaffen, das weitgehend geräuschlos und über lange Standzeit arbeitet.The invention is based, a pressure reducing seat valve the task mentioned type to create the largely silent and long Tool life works.

Die gestellte Aufgabe wird erfindungsgemäß mit den Merkmalen des Anspruchs 1 gelöst. The object is achieved according to the invention with the features of claim 1 solved.

In dem Druckminder-Sitzventil hebt die Regelfeder das Schließelement gegen den geminderten Druck am Regelkolben über den Regelkolben vom Sitz ab. Der geminderte Druck führt zusammen mit dem vom Eingangsdruck in Schließrichtung beaufschlagten Schließelement den Regelkolben zum Ventilsitz zurück, sobald der geminderte Druck dem eingestellten Wert entspricht. Speziell bei einem starken Abfall des geminderten Drucks wird das Schließelement weit vom Ventilsitz abgehoben, um den geminderten Druck so rasch wie möglich auf der eingestellten Höhe zu halten. Da üblicherweise nur eine geringe Druckmittelmenge erforderlich ist, um den geminderten Druck wieder herzustellen, wird der Regelkolben dann gegen die Regelfeder rasch zurückgedrückt, so daß zu befürchten ist, daß das Schließelement unter dem Eingangsdruck fest auf den Ventilsitz schlägt. Die hydraulische Dämpfvorrichtung greift zuvor jedoch am Regelkolben an, der die Bewegung des Schließelementes steuert und unterdrückt rasche Spielbewegungen des Regelkolbens, vor allem in Schließrichtung des Schließelements. Es kommt auch bei schlagartig fallendem geminderten Druck nicht zum gefürchteten Rattern des Schließelements. Dadurch wird eine störende Geräuschentwicklung unterdrückt und bleibt das Druckminder-Sitzventil über lange Standzeit funktionssicher. Das Schließelement nähert sich, geführt durch den Regelkolben, dem Ventilsitz, um den geminderten Druck einzustellen bzw. bei Erreichen des geminderten Drucks abzusperren, ohne mehrmals hin- und herzupendeln und anzuschlagen. Nur die Schließbewegung des Regelkolbens hydraulisch abzudämpfen, hat ferner den Vorteil einer zügigen Öffnungsbewegung des Schließelements, um bei einem Abfall des geminderten Drucks die Druckangleichung unverzögert einzuleiten. Das Druckmittel muß bei diesem Eingriff zum Beaufschlagen des Regelkolbens gegen die Regelfeder den gedrosselten Strömungsweg passieren, wodurch eine zu rasche Schließbewegung des Regelkolbens und konsequenterweise des Schließelementes verhindert wird. Durch die Enge des Strömungsweges läßt sich der Dämpfungseffekt vorherbestimmen. Ist, um auch die Öffnungsbewegung hydraulisch abzudämpfen, in der Speicherkammer das Verdrängerelement vorgesehen, dann wird in der Speicherkammer enthaltenes Druckmittel bei der Öffnungsbewegung durch den gedrosselten Strömungsweg gepreßt. Die hydraulische Dämpfungsvorrichtung arbeitet nach Art eines in das Druckminder-Sitzventil integrierten hydraulischen Stoßdämpfers. Günstig ist dabei, daß die Dämpfvorrichtung in das spezielle, bewährte Sitzventilkonzept problemlos integriert ist, bei dem der Eingangs- oder Pumpendruck das Sitz-Schließelement in Schließrichtung und gegen die Feder der geminderte Druck hingegen gegen die Feder und am Schließelement in Öffnungsrichtung wirkt.The control spring lifts the closing element in the pressure reducing seat valve the reduced pressure on the control piston from the seat via the control piston. The reduced pressure leads together with that of the inlet pressure in the closing direction acted upon the closing element the control piston back to the valve seat as soon as the reduced pressure corresponds to the set value. Especially with a strong one When the reduced pressure drops, the closing element becomes far from the valve seat lifted to the reduced pressure as quickly as possible on the set To keep height. Since usually only a small amount of pressure medium is required is to restore the reduced pressure, the control piston then quickly pushed back against the rule spring, so that there is fear that the closing element hits the valve seat firmly under the inlet pressure. The However, the hydraulic damping device first attacks the control piston, which is the Movement of the closing element controls and suppresses rapid game movements of the control piston, especially in the closing direction of the closing element. It does not come to the feared even with suddenly falling reduced pressure Rattling of the closing element. This creates an annoying noise suppresses and the pressure reducing seat valve remains functionally reliable over a long service life. The closing element, guided by the control piston, approaches Valve seat to set the reduced pressure or when the reduced pressure is reached To shut off the pressure without swinging and pounding several times. Only hydraulically dampen the closing movement of the control piston, also has the advantage of a rapid opening movement of the closing element to initiate the pressure adjustment without delay if the reduced pressure drops. The pressure medium must act on the control piston during this intervention pass the throttled flow path against the control spring, whereby a too rapid closing movement of the control piston and consequently of the closing element is prevented. Through the narrowness of the flow path the damping effect can be predetermined. Is to also the opening movement dampen hydraulically, the displacement element in the storage chamber provided, then pressure medium contained in the storage chamber at the Opening movement pressed through the restricted flow path. The hydraulic Damping device works in the manner of a pressure reducing seat valve integrated hydraulic shock absorber. It is favorable that the damping device is easily integrated into the special, proven seat valve concept at which the inlet or pump pressure the seat closing element in the closing direction and against the spring the reduced pressure against the spring and acts on the closing element in the opening direction.

Es kann für einige Anforderungen gemäß Anspruch 2 zweckmäßig sein, die Öffnungs- und die Schließbewegungen des Regelkolbens hydraulisch abzudämpfen.It may be appropriate for some requirements according to claim 2, the opening and hydraulically dampen the closing movements of the control piston.

Gemäß Anspruch 3 dient als Verdrängerelement der mit dem Regelkolben verstellbare Kolben, der gleichzeitig den gedrosselten Strömungsweg begrenzt. Der Kolben ist an beiden Beaufschlagungsseiten vom geminderten Druck belastet, so diesbezüglich die Regelcharakteristik des Druckminder-Sitzventils nicht spürbar beeinflußt wird.According to claim 3 serves as a displacement element which is adjustable with the control piston Piston that also limits the restricted flow path. The The piston is loaded by the reduced pressure on both loading sides, see above In this regard, the control characteristic of the pressure reducing seat valve is not noticeable being affected.

Gemäß Anspruch 4 hat die Speicherkammer eine Doppelfunktion, da sie das durch den gedrosselten Strömungsweg gepreßte Druckmittel aufnimmt und zur Beaufschlagung des Regelkolbens gegen die Regelfeder dient.According to claim 4, the storage chamber has a double function, since it pressurized by the throttled flow path receives and to Actuation of the control piston against the control spring serves.

Gemäß Anspruch 5 hat der das Verdrängerelement der hydraulischen Dämpfvorrichtung bildende Kolben die Zusatzfunktion einer Hubbegrenzung des Regelkolbens, damit dieser nicht unzulässig weit in die Federkammer verschoben wird.According to claim 5, the displacement element of the hydraulic damping device forming pistons the additional function of a stroke limitation of the control piston, so that it is not moved too far into the spring chamber.

Um nur die Schließbewegung zu dämpfen, ist gemäß Anspruch 6 der gedrosselte Strömungsweg von einem Rückschlagventil umgangen, das in Strömungsrichtung zur Speicherkammer öffnet und in der Gegenrichtung absperrt.In order to dampen only the closing movement, the throttled is according to claim 6 Flow path bypassed by a check valve that is in the direction of flow opens to the storage chamber and blocks in the opposite direction.

Gemäß Anspruch 7 ist das Rückschlagventil zur Einsparung von Bauraum im Kolben angeordnet. According to claim 7, the check valve to save space in Piston arranged.

Um auch bei einer relativ kleinen bewegten Druckmittelmenge einen ausreichenden Dämpfungseffekt zu erzielen, ist gemäß Anspruch 8 er Durchmesser des Kolbens größer als der Durchmesser des Regelkolbens.In order to achieve an adequate level even with a relatively small amount of pressure medium moved To achieve damping effect, according to claim 8, he diameter of the piston larger than the diameter of the control piston.

Herstellungstechnisch einfach ist die Ausführungsform gemäß Anspruch 9.The embodiment according to claim 9 is technically simple.

Bei der alternativen Ausführungsform gemäß Anspruch 10 muß das Druckmittel zur Dämpfung (in Schließrichtung oder in Schließ-und Öffnungsrichtung des Regelkolbens) durch wenigstens einen im Gehäuse verlaufenden Kanal strömen. Bei dieser Ausbildung läßt sich ein üblicher Regelkolben ohne Modifikation verwenden.In the alternative embodiment according to claim 10, the pressure medium for damping (in the closing direction or in the closing and opening direction of the control piston) flow through at least one channel running in the housing. At this training can use a conventional control piston without modification.

Als flankierende Maßnahme zur wirkungsvollen Dämpfung ist bei der Ausführungsform gemäß Anspruch 11 der Stößel als Strömungsleit-Trompete ausgebildet. Dadurch wird das aus dem Ventilsitz kommende Druckmittel nicht nur geführt (ohne störende Turbulenzen) zur Seite des geminderten Drucks gebracht, sondern auch zum gedrosselten Strömungsweg, wodurch die Dämpfung vergleichmäßigt wird. Bei bestimmten Arbeitsbedingungen, Druckverhältnissen oder Druckmittelmengen, ist die Strömungsleit-Trompete Teil der hydraulischen Dämpfvorrichtung, weil ggfs. der gedrosselte Strömungsweg und die Speicherkammer beim Dämpfen, z.B. infolge der Strömungsdynamik, überfordert wären.As a flanking measure for effective damping is in the embodiment According to claim 11, the plunger is designed as a flow guide trumpet. As a result, the pressure medium coming from the valve seat is not only guided (without disturbing turbulence) brought to the side of the reduced pressure, but also to the throttled flow path, which makes the damping more even becomes. Under certain working conditions, pressure conditions or Pressure fluid quantities, the flow control trumpet is part of the hydraulic Damping device, because the throttled flow path and the storage chamber when steaming, e.g. would be overwhelmed due to the flow dynamics.

Herstellungstechnisch günstig ist die Ausführungsform gemäß Anspruch 12. Mit diesem Verlauf wird eine optimale Unterstützung der hydraulischen Dämpfungsvorrichtung erreicht.The embodiment according to claim 12 is technically favorable this course is an optimal support of the hydraulic damping device reached.

Bei der alternativen Ausführungsform gemäß Anspruch 13 läßt sich das Druckminder-Sitzventil auf einfache Weise auf unterschiedliche Arbeits-Druckbereiche umrüsten, ohne die teure Regelfeder und das Gehäuse wechseln zu müssen. In the alternative embodiment according to claim 13, the pressure reducing seat valve can in a simple way to different working pressure ranges convert without having to change the expensive control spring and the housing.

Gemäß Anspruch 14 ergibt sich eine einfache Montage. Die Kooperation zwischen dem gehärteten Ventilsitz und der gehärteten Stahlkugel garantiert lange Standzeiten, begünstigt durch die ein störendes Arbeitsgeräusch verhindernde und den Verschleiß mindernde hydraulische Dämpfvorrichtung. Anstelle einer Stahlkugel können auch andere Sitz-Schließelementformen benutzt werden können, z.B. ein kegeliges Schließelement oder ein kegeliges Schließelement mit einem Schieberansatz.According to claim 14 there is a simple assembly. The cooperation between the hardened valve seat and the hardened steel ball guarantee a long life Downtime, favored by the annoying working noise and wear-reducing hydraulic damper. Instead of one Steel ball other seat closing element shapes can be used e.g. a conical closing element or a conical closing element with a Slide approach.

Anhand der Zeichnung werden Ausführungsformen des Erfindungsgegenstandes erläutert. Es zeigen:

Fig. 1
einen Längsschnitt durch ein Druckminder-Sitzventil mit einer hydraulischen Dämpfvorrichtung,
Fig. 2
einen Teil eines Schnittes einer geänderten Ausführungsform, und
Fig. 3
einen Teil eines Schnittes einer weiteren geänderten Ausführungsform.
Embodiments of the subject matter of the invention are explained with the aid of the drawing. Show it:
Fig. 1
a longitudinal section through a pressure reducing seat valve with a hydraulic damping device,
Fig. 2
a part of a section of a modified embodiment, and
Fig. 3
a part of a section of a further modified embodiment.

Ein Druckminder-Sitzventil D gemäß Fig. 1 weist in einem blockförmigen Anschlußgehäuse G (das gegebenenfalls das Gehäuse eines Verbrauchers ist) eine Stufenbohrung 1 auf, in der ein Einsatz 2 mit einem Ventilsitz S positioniert ist. Zum Positionieren des Einsatzes 2 dient ein einschraubbarer Gehäuse-Einsatz 3, der durch eine Sicherungs- und Dichtungsmutter 4 gesichert ist. In einer axialen Bohrung 9 ist ein Regelkolben R verschiebbar. In einer zur Atmosphäre entlüfteten Federkammer 19 ist eine Regelfeder F vorgesehen. Die Vorspannkraft der Regelfeder F ist durch nicht-dargestellte, übliche Einrichtungen verstellbar. Der Gehäuse-Einsatz 3 bildet mit seinen Komponenten eine Moduleinheit und kann gegen andere Gehäuseeinsätze 3 mit gleichen Außenabmessungen, jedoch mit anders dimensionierten Regelkolben R unter Weiterverwendung der Regelfeder F und das Gehäuse ausgetauscht werden, um das Druckminder-Sitzventil D einfach an unterschiedliche Arbeitsdruckbereiche anzupassen. A pressure reducing seat valve D according to FIG. 1 has a block-shaped connection housing G (which may be the housing of a consumer) one Stepped bore 1 in which an insert 2 with a valve seat S is positioned. A screw-in housing insert 3 is used to position the insert 2, which is secured by a locking and sealing nut 4. In an axial Bore 9, a control piston R is displaceable. In a vented to atmosphere A spring F is provided in the spring chamber 19. The preload of the Regelfeder F is adjustable by conventional devices, not shown. The Housing insert 3 forms a module unit with its components and can against other housing inserts 3 with the same external dimensions, but with differently dimensioned control piston R while using the control spring F and the housing can be replaced to make the pressure reducing seat valve D easy adapt to different working pressure ranges.

Der Ventilsitz S befindet sich zwischen einem Anschluß P für den Eingangs- bzw. Pumpendruck und einem Anschluß A für den geminderten Druck. Auf der Seite des Anschlusses P ist dem Ventilsitz S ein Schließelement E, z.B. eine gehärtete Stahlkugel bei gehärtetem Ventilsitz S, zugeordnet, das in einem Halteteil 5 gestützt und geführt wird, der in einem Schraubeinsatz 6 unter der Kraft einer schwachen Schließfeder 7 verschiebbar geführt ist. Der Schraubeinsatz 6 ist mit dem Einsatz 2 verschraubt und stützt eine Filteranordnung 8 ab.The valve seat S is located between a port P for the input or Pump pressure and a connection A for the reduced pressure. On the website of the port P, the valve seat S is a closing element E, e.g. a hardened Steel ball associated with hardened valve seat S, which is supported in a holding part 5 and is guided in a screw 6 under the force of a weak closing spring 7 is guided. The screw insert 6 is with screwed the insert 2 and supports a filter assembly 8.

Im Gehäuseeinsatz 3 ist ein Abschnitt mit gegenüber der Bohrung 9 vergrößertem Durchmesser vorgesehen, der eine zylindrische Gehäusewand 10 und eine Schulter 15 aufweist. Durchgänge 11 verbinden den Ventilsitz S mit dem Anschluß A für den geminderten Druck.In the housing insert 3 is a section with a larger than the bore 9 Provided diameter of a cylindrical housing wall 10 and a Has shoulder 15. Passages 11 connect the valve seat S to the connector A for the reduced pressure.

Der Regelkolben R ist einstückig verbunden mit einem größeren Kolben K und einem Stößel 12. Der Kolben K begrenzt eine Speicherkammer 13, in der der Regelkolben R mit dem geminderten Druck gegen die Kraft der Regelfeder F und in Öffnungsrichtung beaufschlagbar ist. Der Kolben K begrenzt mit seinem Außenumfang einen gedrosselten Strömungsweg 14 zur Speicherkammer 13 und fungiert, z.B., als Hubanschlag für den Regelkolben R in Richtung zur Schulter 15.The control piston R is integrally connected to a larger piston K and one Tappet 12. The piston K delimits a storage chamber 13 in which the control piston R with the reduced pressure against the force of the control spring F and in Opening direction can be acted upon. The piston K delimits with its outer circumference a throttled flow path 14 to the storage chamber 13 and functions, e.g., as a stroke stop for the control piston R towards the shoulder 15.

Der Kolben K bildet zusammen mit dem gedrosselten Strömungsweg 14 und der Speicherkammer 13 eine hydraulische Dämpfvorrichtung B für den Regelkolben R, der das Schließelement E bei Öffnungs- und Schließbewegungen verstellt.The piston K forms together with the throttled flow path 14 and Storage chamber 13 a hydraulic damping device B for the control piston R, which adjusts the closing element E during opening and closing movements.

In der dargestellten Position des Druckminder-Sitzventils D ist im Anschluß A der gewünschte und an der Regelfeder F eingestellte geminderte Druck vorhanden. Dieser geminderte Druck beaufschlagt den Regelkolben R gegen die Regelfeder F, wobei das Schließelement E in dichter Anlage auf dem Sitz S gehalten wird, auch durch den im Anschluß P herrschenden Eingangsdruck. Der geminderte Druck herrscht auch in der Speicherkammer 13. Sinkt, beispielsweise aufgrund Verbrauchs, der geminderte Druck, dann überwindet die Regelfeder F die Gegenkraft des Regelkolbens R und hebt das Schließelement E vom Ventilsitz S ab. Bei dieser Öffnungsbewegung wird über den gedrosselten Strömungsweg 14 Druckmittel in die Speicherkammer 13 nachgesaugt, wodurch die Öffnungsbewegung gedämpft wird. Nähert sich der Druck im Anschluß A wieder dem eingestellten Wert für den geminderten Druck, dann werden der Regelkolben R gegen die Regelfeder F nach oben verschoben und das Schließelement E zum Ventilsitz S gebracht bzw. auf diesen gedrückt. In der Speicherkammer 13 enthaltenes Druckmittel wird aufgrund des Durchmesserunterschiedes zwischen dem Kolben K und dem Regelkolben R durch den gedrosselten Strömungsweg 14 gepreßt, so daß die Schließbewegung gedämpft wird.In the position shown of the pressure reducing valve D is in port A Desired pressure set at control spring F is available. This reduced pressure acts on the control piston R against the control spring F, the closing element E being held tightly on the seat S, also due to the inlet pressure in port P. The diminished one Pressure also prevails in the storage chamber 13. Sinks, for example due to Consumption, the reduced pressure, then the control spring F overcomes the counterforce of the control piston R and lifts the closing element E from the valve seat S. At this opening movement is via the throttled flow path 14 Pressure medium sucked into the storage chamber 13, causing the opening movement is steamed. If the pressure in port A approaches the set one again Value for the reduced pressure, then the control piston R against the Control spring F moved up and the closing element E to the valve seat S. brought or pressed on this. Contained in the storage chamber 13 Pressure fluid is due to the difference in diameter between the piston K and the control piston R pressed through the throttled flow path 14, see above that the closing movement is dampened.

Der Stößel 12 zum Führen des Schließelements E ist als sich zum gedrosselten Strömungsweg 14 hin erweitertende Strömungsleit-Trompete ausgebildet.The plunger 12 for guiding the closing element E is to be throttled Flow path 14 formed widening flow guide trumpet.

Um nur die Schließbewegung des Regelkolbens R zu dämpfen, die Öffnungsbewegung und das Nachsaugen des Druckmittels in die Speicherkammer 13 hingegen ungedämpft ablaufen zu lassen, kann der gedrosselte Strömungsweg 14 durch ein Rückschlagventil C umgangen werden, das gemäß Fig. 2 entweder im Kolben K direkt oder gemäß Fig. 3 in einem Kanal 17 im Gehäuse angeordnet ist. Der Kanal 17 führt vom Anschluß A zur Speicherkammer 13.In order to dampen only the closing movement of the control piston R, the opening movement and the suction of the pressure medium into the storage chamber 13, however To allow the flow path 14 to flow undamped bypassed by a check valve C, which is either in Piston K is arranged directly or according to FIG. 3 in a channel 17 in the housing. The channel 17 leads from the connection A to the storage chamber 13.

In Fig. 2 ist ferner angedeutet, daß anstelle des oder zusätzlich zum gedrosselten Strömungsweg 14 zwischen dem Außenumfang des Kolbens K und der Gehäusewand 10 (Fig. 1) ein gedrosselter Strömungsweg 14' direkt im Kolben K untergebracht ist, der durch eine versinnbildlichte Drossel 16 charakterisiert ist.In Fig. 2 is also indicated that instead of or in addition to the throttled Flow path 14 between the outer circumference of the piston K and the housing wall 10 (Fig. 1) a throttled flow path 14 'housed directly in the piston K. is, which is characterized by a symbolic choke 16.

Gemäß Fig. 3 könnte (alternativ oder additiv) ein eigener, im Gehäuse verlaufender Strömungsweg 14" mit der Drossel 16 vorgesehen sein. Der Kolben K könnte mit einer Druckausgleichsnut oder einer Dichtung ausgestattet werden (Fig. 3). 3 could (alternatively or additively) a separate one running in the housing Flow path 14 "can be provided with the throttle 16. The piston K could be equipped with a pressure compensation groove or a seal (Fig. 3).

Durch den gegenüber dem Regelkolben R größeren Kolben K, der ein Verdrängerelement bildet, wird auch für eine relativ kleine Druckmittelmenge zum Füllen der Speicherkammer 13 eine kräftige Strömung erzwungen, die den gedrosselten Strömungsweg 14, 14', 14" zu passieren hat. Mit dieser auch bei kleiner Druckmittelmenge kräftigen Strömung läßt sich ein wirksamer hydraulischer Dämpfungseffekt für den Regelkolben R erzielen.The piston K, which is larger than the control piston R, is a displacement element forms, is also for a relatively small amount of pressure medium for filling the storage chamber 13 forced a strong flow, the throttled Flow path 14, 14 ', 14 "has to pass. With this even with a small amount of pressure medium powerful flow can be an effective hydraulic damping effect for the control piston R.

Claims (14)

  1. Pressure-reducing seat valve (D) for high-pressure hydraulics, with a spring-loaded control piston (R) acted upon counter to the spring loading by the reduced pressure and intended to move relative to the valve seat (S) a closing element (E) acted upon in the closing direction relative to a valve seat (S) by the inlet pressure, a hydraulic damping device (B) for closing movements of the closing element (E) brought about at least by the control piston (R) being provided for the control piston (R), this device having an accumulator chamber (13) that can be filled with pressure medium under the reduced pressure, at least one restricted flow path (14, 14', 14'', 17) between the accumulator chamber (13) and the reduced-pressure side and in the accumulator chamber (13) a displacer element that can be moved by means of the control piston (R).
  2. Pressure-reducing seat valve according to Claim 1, characterized in that the hydraulic damping device is provided for the closing and the opening movements of the closing element (E).
  3. Pressure-reducing seat valve according to Claim 1, characterized in that the displacer element is a piston (K) that can be adjusted by means of the control piston (R) and, with its outer circumference and an adjacent housing wall (10), delimits a through gap that defines the restricted flow path (14).
  4. Pressure-reducing seat valve according to Claim 1, characterized in that the accumulator chamber (13) is the control chamber of the control piston (R).
  5. Pressure-reducing seat valve according to at least one of the preceding claims, characterized in that the piston (K) forms a stroke stop for the control piston (R) in the closing direction of the closing element (E) and is oriented towards a housing shoulder (15) arranged in the accumulator chamber (13).
  6. Pressure-reducing seat valve according to Claim 1, characterized in that the restricted flow path (14) is bypassed by a nonreturn valve (C) in the direction of flow into the accumulator chamber (13).
  7. Pressure-reducing seat valve according to Claim 6, characterized in that the nonreturn valve (C) is arranged in the piston (K).
  8. Pressure-reducing seat valve according to at least one of the preceding claims, characterized in that the outside diameter of the piston (K) is greater than the diameter of the control piston (R).
  9. Pressure-reducing seat valve according to Claim 3, characterized in that the piston (K) and a tappet (12) acting on the closing element (A) are of one-piece construction with the control piston (R).
  10. Pressure-reducing seat valve according to at least one of Claims 3, 4 and 7, characterized in that the restricted flow path (14'', 17) is provided at least in part, and/or the nonreturn valve (C) is provided, in a passage that bypasses the direct connection from the reduced-pressure side to the control piston (R) in the housing (G).
  11. Pressure-reducing seat valve according to Claim 10, characterized in that the tappet (12) is designed as a flow-guide trumpet that widens from the closing element (E) to the piston (K), preferably with a rotationally symmetrical enveloping surface (18) that guides the flow from the valve seat (S) into the inlet of the restricted flow passage (14).
  12. Pressure-reducing seat valve according to Claim 11, characterized in that the tappet (12) has a cylindrical end part (18a) and a conical connection (18b) to the piston (K), and in that the transition (18c) between the cylindrical end part (18a) and the conical connection (18b) has a concave curvature.
  13. Pressure-reducing seat valve according to at least one of the preceding claims, characterized in that the control piston (R) is arranged with the hydraulic damping device (B) in a housing insert (3) containing a pressure-relieved spring chamber (19) and forms a modular unit with the insert, with the exception of the control spring (F), the modular unit being replaceable by another modular unit with a larger or a smaller control piston (R).
  14. Pressure-reducing seat valve according to Claim 13, characterized in that the valve seat (S) is provided in a hardened steel insert (2) and fixed by means of the housing insert (3), and in that the closing element (E) is a hardened steel ball acted upon in the closing direction by a spring (7).
EP97107824A 1996-09-05 1997-05-13 Pressure reducing lift valve Expired - Lifetime EP0829794B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE29615498U DE29615498U1 (en) 1996-09-05 1996-09-05 Pressure reducing valve
DE29615498U 1996-09-05

Publications (2)

Publication Number Publication Date
EP0829794A1 EP0829794A1 (en) 1998-03-18
EP0829794B1 true EP0829794B1 (en) 2001-12-19

Family

ID=8028858

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97107824A Expired - Lifetime EP0829794B1 (en) 1996-09-05 1997-05-13 Pressure reducing lift valve

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EP (1) EP0829794B1 (en)
AT (1) ATE211273T1 (en)
DE (2) DE29615498U1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016223347A1 (en) 2016-11-24 2018-05-24 Hawe Hydraulik Se Pressure control valve with a damping device

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29808294U1 (en) 1998-05-07 1998-08-13 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Electro-hydraulic clamping module
DE29808295U1 (en) 1998-05-07 1998-08-13 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Seat valve
EP1970787B1 (en) 2007-03-16 2014-11-19 HAWE Hydraulik SE Pressure control seat valve
WO2013090458A1 (en) * 2011-12-12 2013-06-20 Parker-Hannifin Corporation Pressure reducing valve with pressure relief
CN113775590A (en) * 2021-10-18 2021-12-10 山东泰丰智能控制股份有限公司 Constant pressure differential valve with buffering function

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Publication number Priority date Publication date Assignee Title
DE2700058C2 (en) * 1977-01-03 1987-05-07 Alfred Teves Gmbh, 6000 Frankfurt Valve arrangement
US4168721A (en) * 1977-06-16 1979-09-25 Massey-Ferguson Inc. Pressure control valve
US4190076A (en) * 1978-03-24 1980-02-26 The Singer Company Damping valve for pressure regulator
CH661777A5 (en) * 1981-05-25 1987-08-14 Sulzer Ag CHECK VALVE.
DE3201432A1 (en) * 1982-01-19 1983-09-08 Uwe 2000 Hamburg Heine Damping device for control pistons

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016223347A1 (en) 2016-11-24 2018-05-24 Hawe Hydraulik Se Pressure control valve with a damping device

Also Published As

Publication number Publication date
DE59705857D1 (en) 2002-01-31
DE29615498U1 (en) 1996-10-24
ATE211273T1 (en) 2002-01-15
EP0829794A1 (en) 1998-03-18

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