EP1180598B1 - Valve assembly - Google Patents

Valve assembly Download PDF

Info

Publication number
EP1180598B1
EP1180598B1 EP20010119038 EP01119038A EP1180598B1 EP 1180598 B1 EP1180598 B1 EP 1180598B1 EP 20010119038 EP20010119038 EP 20010119038 EP 01119038 A EP01119038 A EP 01119038A EP 1180598 B1 EP1180598 B1 EP 1180598B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
connection
valve arrangement
consumer
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP20010119038
Other languages
German (de)
French (fr)
Other versions
EP1180598A3 (en
EP1180598A2 (en
Inventor
Jörg Dantlgraber
Reiner Püschel
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.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1180598A2 publication Critical patent/EP1180598A2/en
Publication of EP1180598A3 publication Critical patent/EP1180598A3/en
Application granted granted Critical
Publication of EP1180598B1 publication Critical patent/EP1180598B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery

Definitions

  • the invention relates to a valve arrangement for supplying a hydraulic consumer according to the preamble of patent claim 1.
  • Such a valve arrangement is known for example from DE 42 11 551 C2 and DE 43 34 167 A1 and is used in hydraulic systems in which a consumer is supplied via a variable displacement pump with a pressure medium.
  • a biasing valve is provided between the variable displacement pump and the consumer, which opens the connection to the consumer at a minimum pressure required for adjusting the delivery volume of the variable. This ensures that between the pressure connection of the variable displacement pump and the biasing valve of the required for actuating an actuator of the variable displacement minimum pressure. This minimum pressure is throttled over the congestion valve, so that lying below this pressure consumer pressures are adjustable.
  • the preload valve is designed with a bluff body which is biased by a biasing spring against a valve seat.
  • the force applied by the spring corresponds to the minimum pressure for adjusting the variable displacement pump.
  • the bluff body is designed with a valve seat, against the biasing spring, a valve body of a pressure relief valve is biased. Since the effective area of the valve body is lower than that of the bluff body, the valve body only opens against the force of the preloading spring when a maximum consumer pressure is reached at which a connection to a tank is opened via the pressure limiting valve.
  • the Spring rate of the biasing spring and the area ratios of the valve body and the bluff body are selected depending on the maximum consumer pressure to be set and the minimum pressure.
  • a hydraulic system for acting on a consumer with a regulated consumer pressure is further known in which a backup valve between a pump and the consumer is provided which opens at a sufficient to adjust the delivery volume of the pump minimum pressure and with a is provided between the consumer-side outlet of the accumulation valve and the tank connected throttle valve, the opening cross-section is adjustable.
  • GB 1 443 799 A1 discloses a valve arrangement which has a pressure-limiting valve which can be pre-controlled via a pilot valve arrangement.
  • the system pressure on the pilot pressure of the pilot valve assembly is adjustable.
  • the present invention seeks to provide a valve assembly that allows adjustment of the maximum consumer pressure to different operating conditions with minimal device complexity.
  • the valve arrangement according to the invention has a pressure connection, a consumer connection and a bluff body which is biased against a valve seat via a biasing spring accommodated in a spring chamber and which opens a connection between the pressure connection and the consumer connection when a minimum pressure in the pressure connection is reached and is provided with a pressure limiting connection. by its control to the two other terminals towards the pressure in these can be limited to a maximum value.
  • the pressure limiting connection can be opened by the bluff body to the two other connections, the spring chamber is connected to the pressure connection via a nozzle and, on the one hand, a pilot valve arrangement and, on the other hand, a congestion valve connected to the spring chamber via a throttle cross section which can be varied by the bluff body. Since the bluff body according to the invention is additionally biased by a control pressure in the closing direction, the biasing spring can be designed weaker than the prior art described in the introduction according to DE 42 11 551 C2 and DE 43 34 167 A1.
  • the spring chamber associated with the spring chamber is connected via a nozzle to the pressure connection, wherein the control pressure in the spring chamber can be limited by a parallel to the pilot valve arrangement connected congestion valve, which is effective for adjusting the minimum pressure required for adjusting the variable.
  • the bluff body be carried out with a first control edge, via which a connection to the congestion valve incentives exchange cross section with increasing consumer pressure is zuu Kunststoffbar, so that upon reaching the maximum consumer pressure of the bluff body in the closed position acting control pressure is determined only by the pilot valve assembly, while in underlying area of the control pressure through the accumulation valve and the flow control valve is predetermined.
  • the bluff body can be designed with a further control edge over which a tank connection can be opened when the maximum control pressure set via the pilot valve arrangement is exceeded, so that the pressure medium can flow off directly to the tank with minimal pressure losses. That is, in the valve arrangement according to the invention, the comparatively large-area bluff body is also part of the pressure limiting valve, via which the pressure medium flow is controlled upon reaching the maximum pressure.
  • the pilot valve arrangement serves only for setting the effective in the closing direction pilot pressure, so that it can be designed with a small cross-section.
  • the effective for setting the minimum pressure accumulation valve is preferably designed as a check valve, the closing spring determines the minimum pressure together with the biasing body biasing in the closing direction biasing spring.
  • the pilot valve arrangement can be embodied, for example, as an electrically adjustable pressure-limiting valve or through a large number of pressure-limiting valves connected in parallel, which can be selectively connected via a directional control valve.
  • the bluff body is designed with a second control edge forming shell breakthrough over the connection to the tank is aufêtbar on reaching the maximum consumer pressure.
  • the nozzle is advantageously formed in the bottom of the cup-shaped bluff body.
  • Figure 1 shows a simplified circuit diagram of a valve assembly 1, via which a hydraulic consumer 2, for example an aggregate of an injection molding machine with a variable displacement pump 4 is connectable.
  • a hydraulic consumer 2 for example an aggregate of an injection molding machine with a variable displacement pump 4 is connectable.
  • the variable displacement pump 4 can be designed for example as a piston pump, preferably axial piston pump or radial piston pump, wherein the actuator 6 is formed by a control cylinder with associated control valve.
  • the valve assembly 1 has an input port P to which the pressure port of the variable displacement pump 4 is connected.
  • the consumer 2 is connected to a consumer port A, while a tank 8 is connected to a tank port T.
  • a biasing valve 12 is arranged, the bluff body is acted upon by a biasing spring 14 in the closing direction and the pressure in the pressure line 10 in the opening direction.
  • a pilot-operated pressure relief valve 16 is provided, which is acted upon in the closing direction by a pre-control pressure which is predetermined via a pilot valve arrangement 18.
  • valve 12 and pressure relief valve 16 are shown separately from each other - as can be seen from the following explanations, the two components 12, 16 are integrated in a common valve assembly, wherein the biasing spring 14 and the Valve body of the pressure relief valve 16 biases in the closing direction.
  • the consumer pressure tapped off from the pressure line 10 via a control line 20 in which a nozzle is located can be individually limited as a function of the operating conditions.
  • the pilot valve assembly has three parallel connected, designed as pressure relief valves pilot valves 22, 23, 24, wherein the pilot valve 22 is connected directly into the control line 20, while the two remaining pilot valves 23, 24, a preferably electrically adjustable directional control valve 26 upstream, via which one of the two pilot valves 23, 24 is selectively switched on.
  • the pilot valve 22 is effective, via which the maximum effective consumer pressure can be limited to a maximum pressure.
  • the two pilot valves 23, 24 limit the maximum consumer pressure to lower pressures than the pilot valve 22, so that by switching the directional control valve 26 and by appropriately connecting the pilot valve 23 or 24 correspondingly changed maximum consumer pressures are adjustable.
  • FIG. 2 shows a greatly simplified sectional view through a valve assembly 1, with which the circuit shown in Figure 1 is realized.
  • the valve assembly 1 has a valve housing 30, in the valve bore 32, a bluff body 34 is guided. This is biased by the biasing spring 14 against a valve seat 36, so that the pressure port P is shut off from the working port A.
  • the bluff body 34 acts as a common valve member for both the valve 12 and the pressure relief valve 16.
  • the bluff body 34 is designed as a cup-shaped piston, in the bottom of the nozzle 38 is arranged, via which the interior 40 of the piston with a spring chamber 42 of the valve assembly 1 is connectable. That is, the pressure at the pressure port P is transmitted in the closed position of the bluff body 34 via the interior 40 and the nozzle 38 in the spring chamber 42, so that the bluff body 34 is biased in addition to the force of the biasing spring 14 by the control pressure in the spring chamber 42 in the closed position.
  • a biasing terminal 44 which is connected via a tank line 46 to the tank 8.
  • a check valve check valve 48 is provided in the tank line 46, the closing spring 50 is selected in response to the adjustment of the variable 4 to be set minimum pressure.
  • the biasing terminal 44 forms a throttle cross-section 52, which during the axial movement of the bluff body 34 by the bottom-side peripheral edge 54 is open or aufberichtbar.
  • a pressure limiting port 56 which is connected downstream of the check valve 48 to the tank line 46.
  • this pressure limiting connection 56 can be replaced by another one Control edge 58 are turned on, which is formed by an opening 60 in the jacket of the bluff body 34.
  • Figure 2 shows the valve assembly in its basic position in which the pressure at the working port A is less than the minimum pressure required for the adjustment of the variable 4. It is assumed that the pressure relief valve 28 is set to 192 bar and the force of the biasing spring 14 is a pressure of 8 bar and the force of the closing spring 50 corresponds to a pressure of 10 bar. Accordingly, the check valve 48 opens at a pressure of 10 bar in the spring chamber 42, so that the back of the bluff body 34 is acted upon by a force in the closing direction, which corresponds to a pressure of 18 bar (closing spring 14 8 bar, check valve 48 10 bar).
  • valve assembly Upon reaching this minimum pressure in the pressure port P of the bluff body 34 is lifted as shown in Figure 2 of its valve seat 36 and opened the connection to the consumer port A. In this case, the minimum pressure is throttled to the load pressure required by the consumer by the opening damper 16.
  • the valve assembly is in storage function. It flows a control oil flow whose size is determined by the cross section of the nozzle 38 and the pressure difference (of 8 bar) above the nozzle, via the nozzle 18 and the check valve 48 to the tank.
  • the valve arrangement has virtually no function in such an operating state.
  • the throttle cross-section 52 With increasing pressure at the consumer port A, the throttle cross-section 52 is increasingly fed. As long as the load pressure has a level that does not respond to the pressure limiting valve 28, the bluff body 34 remains in a position below the position shown in Figure 3, in which the throttle cross section 52 may just be slightly open.
  • the accumulation valve 12 and the pressure relief valve 16 are integrated with each other, wherein the bluff body 34 acts as a common valve member for both components.
  • the system pressure to be limited can be adjusted in a simple manner via the pilot valve 28, so that the valve arrangement can be adapted to different operating conditions.
  • a valve arrangement for supplying a hydraulic consumer with a pressure medium, wherein a biasing valve for adjusting a variable displacement required minimum pressure is adjustable.
  • the maximum consumer pressure is limited by a pressure limiting valve, wherein the pressure limiting valve is associated with a pilot valve arrangement, via which the effective in the closing direction of a bluff body of the pressure relief valve control pressure is variable.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)

Description

Die Erfindung betrifft eine Ventilanordnung zur Versorgung eines hydraulischen Verbrauchers gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a valve arrangement for supplying a hydraulic consumer according to the preamble of patent claim 1.

Eine derartige Ventilanordnung ist beispielsweise aus der DE 42 11 551 C2 und der DE 43 34 167 A1 bekannt und wird bei hydraulischen Systemen eingesetzt, bei denen ein Verbraucher über eine Verstellpumpe mit einem Druckmittel versorgt wird. Dabei ist zwischen der Verstellpumpe und dem Verbraucher ein Vorspannventil vorgesehen, das bei einem zur Verstellung des Fördervolumens der Verstellpumpe erforderlichen Mindestdruck die Verbindung zum Verbraucher öffnet. Dadurch ist sichergestellt, daß zwischen dem Druckanschluß der Verstellpumpe und dem Vorspannventil der zur Betätigung eines Stellgliedes der Verstellpumpe erforderliche Mindestdruck herrscht. Dieser Mindestdruck wird über das Stauventil abgedrosselt, so daß auch unterhalb dieses Druckes liegende Verbraucherdrücke einstellbar sind.Such a valve arrangement is known for example from DE 42 11 551 C2 and DE 43 34 167 A1 and is used in hydraulic systems in which a consumer is supplied via a variable displacement pump with a pressure medium. In this case, a biasing valve is provided between the variable displacement pump and the consumer, which opens the connection to the consumer at a minimum pressure required for adjusting the delivery volume of the variable. This ensures that between the pressure connection of the variable displacement pump and the biasing valve of the required for actuating an actuator of the variable displacement minimum pressure. This minimum pressure is throttled over the congestion valve, so that lying below this pressure consumer pressures are adjustable.

Bei den bekannten Lösungen ist das Vorspannventil mit einem Staukörper ausgeführt, der über eine Vorspannfeder gegen einen Ventilsitz vorgespannt ist. Die von der Feder aufgebrachte Kraft entspricht dem Mindestdruck zur Verstellung der Verstellpumpe. Der Staukörper ist mit einem Ventilsitz ausgeführt, gegen den über die Vorspannfeder ein Ventilkörper eines Druckbegrenzungsventils vorgespannt ist. Da die Wirkfläche des Ventilkörpers geringer ist, als diejenige des Staukörpers öffnet der Ventilkörper gegen die Kraft der Vorspannfeder erst bei Erreichen eines maximalen Verbraucherdruckes, bei dem über das Druckbegrenzungsventil eine Verbindung zu einem Tank aufgesteuert wird. Die Federrate der Vorspannfeder und die Flächenverhältnisse des Ventilkörpers und des Staukörpers werden in Abhängigkeit vom einzustellenden maximalen Verbraucherdruck und vom Mindestdruck gewählt.In the known solutions, the preload valve is designed with a bluff body which is biased by a biasing spring against a valve seat. The force applied by the spring corresponds to the minimum pressure for adjusting the variable displacement pump. The bluff body is designed with a valve seat, against the biasing spring, a valve body of a pressure relief valve is biased. Since the effective area of the valve body is lower than that of the bluff body, the valve body only opens against the force of the preloading spring when a maximum consumer pressure is reached at which a connection to a tank is opened via the pressure limiting valve. The Spring rate of the biasing spring and the area ratios of the valve body and the bluff body are selected depending on the maximum consumer pressure to be set and the minimum pressure.

Nachteilig bei dieser Lösung ist, daß eine bei bestimmten Betriebszuständen des Verbrauchers erforderliche Änderung der Vorspann- und Maximaldrücke nicht möglich ist. Des weiteren muß bei der Auslegung der Vorspannfeder ein geeigneter Kompromiß gefunden werden, der auf der einen Seite eine zuverlässige Begrenzung des maximalen Verbraucherdruckes gewährleistet auf der anderen Seite jedoch auch bei der Einstellung des Mindestdruckes ein weiches Ansprechen beim Abheben des Staukörpers von seinem Ventilsitz ermöglicht. Bei derartigen Lösungen ist die Federrate der Vorspannfeder relativ hoch, so daß die Federkraftdifferenz in dem Bereich zwischen gerade abgehobenem Staukörper und vollständig aufgesteuertem Vorspannventil relativ hoch sind. Ein weiterer Nachteil der bekannten Lösung besteht darin, daß die Ausbildung des Staukörpers mit integriertem Druckbegrenzungsventil einen erheblichen vorrichtungstechnischen Aufwand erfordert.The disadvantage of this solution is that a change in the preload and maximum pressures required for certain operating states of the consumer is not possible. Furthermore, a suitable compromise must be found in the design of the biasing spring, which ensures on the one hand a reliable limitation of the maximum consumer pressure on the other hand, however, allows a soft response when lifting the bluff body from his valve seat even when setting the minimum pressure. In such solutions, the spring rate of the biasing spring is relatively high, so that the spring force difference in the area between just lifted baffle and fully open biasing valve are relatively high. Another disadvantage of the known solution is that the formation of the bluff body with integrated pressure relief valve requires a considerable device complexity.

Aus der DE 43 34 167 A1 ist weiterhin ein hydraulisches System zur Beaufschlagung eines Verbrauchers mit einem geregelten Verbraucherdruck bekannt, bei dem ein Stauventil zwischen einer Pumpe und dem Verbraucher vorgesehen ist, das bei einem zur Verstellung des Fördervolumens der Pumpe ausreichenden Mindestdruck öffnet und mit einem zwischen den verbraucherseitigen Ausgang des Stauventils und den Tank geschalteten Drosselventil versehen ist, dessen Öffnungsquerschnitt verstellbar ist.From DE 43 34 167 A1 a hydraulic system for acting on a consumer with a regulated consumer pressure is further known in which a backup valve between a pump and the consumer is provided which opens at a sufficient to adjust the delivery volume of the pump minimum pressure and with a is provided between the consumer-side outlet of the accumulation valve and the tank connected throttle valve, the opening cross-section is adjustable.

Des Weiteren ist in der GB 1 443 799 A1 eine Ventilanordnung offenbart, die ein Druckbegrenzungsventil aufweist, das über eine Pilotventilanordnung vorsteuerbar ist. Bei dieser Lösung ist der Systemdruck über den Vorsteuerdruck der Pilotventilanordnung einstellbar.Furthermore, GB 1 443 799 A1 discloses a valve arrangement which has a pressure-limiting valve which can be pre-controlled via a pilot valve arrangement. In this solution, the system pressure on the pilot pressure of the pilot valve assembly is adjustable.

Demgegenüber liegt der Erfindung die Aufgabe zugrunde, eine Ventilanordnung zu schaffen, die eine Anpassung des maximalen Verbraucherdruckes an unterschiedliche Betriebsbedingungen mit minimalem vorrichtungstechnischen Aufwand ermöglicht.In contrast, the present invention seeks to provide a valve assembly that allows adjustment of the maximum consumer pressure to different operating conditions with minimal device complexity.

Diese Aufgabe wird durch eine Ventilanordnung mit den Merkmalen des Patentanspruchs 1 gelöst.This object is achieved by a valve arrangement having the features of patent claim 1.

Die erfindungsgemäße Ventilanordnung hat einen Druckanschluss, einen Verbraucheranschluss und einen Staukörper, der über eine in einem Federraum untergebrachte Vorspannfeder gegen einen Ventilsitz vorgespannt ist und der bei Erreichen eines Mindestdruckes im Druckanschluss eine Verbindung zwischen dem Druckanschluss und dem Verbraucheranschluss aufsteuert und ist mit einem Druckbegrenzungsanschluss versehen, durch dessen Aufsteuerung zu den beiden anderen Anschlüssen hin der Druck in diesen auf einen Maximalwert begrenzbar ist. Erfindungsgemäß ist der Druckbegrenzungsanschluss durch den Staukörper zu den beiden anderen Anschlüssen aufsteuerbar, der Federraum über eine Düse mit dem Druckanschluss verbunden und einerseits eine Pilotventilanordnung und andererseits über einen durch den Staukörper veränderbaren Drosselquerschnitt ein Stauventil an den Federraum angeschlossen.
Da der Staukörper erfindungsgemäß zusätzlich von einem Steuerdruck in Schließrichtung vorgespannt ist, kann die Vorspannfeder schwächer als beim eingangs beschriebenen Stand der Technik gemäß der DE 42 11 551 C2 und der DE 43 34 167 A1 ausgelegt werden.The valve arrangement according to the invention has a pressure connection, a consumer connection and a bluff body which is biased against a valve seat via a biasing spring accommodated in a spring chamber and which opens a connection between the pressure connection and the consumer connection when a minimum pressure in the pressure connection is reached and is provided with a pressure limiting connection. by its control to the two other terminals towards the pressure in these can be limited to a maximum value. According to the invention, the pressure limiting connection can be opened by the bluff body to the two other connections, the spring chamber is connected to the pressure connection via a nozzle and, on the one hand, a pilot valve arrangement and, on the other hand, a congestion valve connected to the spring chamber via a throttle cross section which can be varied by the bluff body.
Since the bluff body according to the invention is additionally biased by a control pressure in the closing direction, the biasing spring can be designed weaker than the prior art described in the introduction according to DE 42 11 551 C2 and DE 43 34 167 A1.

Erfindungsgemäß ist der dem Staukörper zugeordnete Federraum über eine Düse mit dem Druckanschluß verbunden, wobei der Steuerdruck im Federraum durch ein parallel zur Pilotventilanordnung geschaltetes Stauventil begrenzbar ist, das zur Einstellung des zur Verstellung der Verstellpumpe erforderlichen Mindestdruckes wirksam ist.According to the invention the spring chamber associated with the spring chamber is connected via a nozzle to the pressure connection, wherein the control pressure in the spring chamber can be limited by a parallel to the pilot valve arrangement connected congestion valve, which is effective for adjusting the minimum pressure required for adjusting the variable.

Hierzu kann beispielsweise der Staukörper mit einer ersten Steuerkante ausgeführt werden, über die eine die Verbindung zum Stauventil ermöglichender Drosselquerschnitt mit steigendem Verbraucherdruck zusteuerbar ist, so daß bei Erreichen des maximalen Verbraucherdruckes der den Staukörper in Schließstellung beaufschlagende Steuerdruck nur durch die Pilotventilanordnung vorgegeben ist, während im darunterliegenden Bereich der Steuerdruck durch das Stauventil und das Stromregelventil vorgegeben ist.For this purpose, for example, the bluff body be carried out with a first control edge, via which a connection to the congestion valve ermöglichender throttle cross section with increasing consumer pressure is zuusteuerbar, so that upon reaching the maximum consumer pressure of the bluff body in the closed position acting control pressure is determined only by the pilot valve assembly, while in underlying area of the control pressure through the accumulation valve and the flow control valve is predetermined.

Erfindungsgemäß kann der Staukörper mit einer weiteren Steuerkante ausgeführt werden, über die bei Überschreiten des über die Pilotventilanordnung eingestellten maximalen Steuerdruckes ein Tankanschluß aufsteuerbar ist, so daß das Druckmittel direkt mit minimalen Druckverlusten zum Tank abströmen kann. D.h., bei der erfindungsgemäßen Ventilanordnung ist der vergleichsweise großflächige Staukörper auch Teil des Druckbegrenzungsventils, über das die Druckmittelströmung bei Erreichen des Maximaldruckes gesteuert wird. Die Pilotventilanordnung dient lediglich zur Einstellung des in Schließrichtung wirksamen Vorsteuerdruckes, so daß diese mit geringen Querschnitt ausgelegt werden kann.According to the invention, the bluff body can be designed with a further control edge over which a tank connection can be opened when the maximum control pressure set via the pilot valve arrangement is exceeded, so that the pressure medium can flow off directly to the tank with minimal pressure losses. That is, in the valve arrangement according to the invention, the comparatively large-area bluff body is also part of the pressure limiting valve, via which the pressure medium flow is controlled upon reaching the maximum pressure. The pilot valve arrangement serves only for setting the effective in the closing direction pilot pressure, so that it can be designed with a small cross-section.

Das zur Einstellung des Mindestdruckes wirksame Stauventil wird vorzugsweise als Rückschlagventil ausgebildet, dessen Schließfeder gemeinsam mit der den Staukörper in Schließrichtung vorspannenden Vorspannfeder den Mindestdruck bestimmt.The effective for setting the minimum pressure accumulation valve is preferably designed as a check valve, the closing spring determines the minimum pressure together with the biasing body biasing in the closing direction biasing spring.

Die Pilotventilanordnung kann beispielsweise als elektrisch verstellbares Druckbegrenzungsventil oder durch eine Vielzahl von parallel geschalteten Druckbegrenzungsventilen ausgeführt sein, die wahlweise über ein Wegeventil zuschaltbar sind.The pilot valve arrangement can be embodied, for example, as an electrically adjustable pressure-limiting valve or through a large number of pressure-limiting valves connected in parallel, which can be selectively connected via a directional control valve.

Bei einem besonders einfach herstellbaren Ausführungsbeispiel ist der Staukörper mit einem die zweite Steuerkante ausbildenden Manteldurchbruch ausgeführt, über den bei Erreichen des maximalen Verbraucherdruckes die Verbindung zum Tank aufsteuerbar ist.In a particularly simple to produce embodiment of the bluff body is designed with a second control edge forming shell breakthrough over the connection to the tank is aufsteuerbar on reaching the maximum consumer pressure.

Die Düse ist vorteilhafterweise im Boden des tassenförmig ausgebildeten Staukörpers ausgebildet.The nozzle is advantageously formed in the bottom of the cup-shaped bluff body.

Sonstige vorteilhafte Weiterbildungen der Erfindung sind Gegenstand der weiteren Unteransprüche.Other advantageous developments of the invention are the subject of the other dependent claims.

Im folgenden werden bevorzugte Ausführungsbeispiele der Erfindung anhand schematischer Zeichnungen näher erläutert.
Es zeigen:

  • Figur 1 ein Schaltschema einer erfindungsgemäßen Ventilanordnung zur Verbindung eines Verbrauchers mit einer Verstellpumpe;
  • Figuren 2 bis 4 eine Prinzipdarstellung der erfindungsgemäßen Ventilanordnung in unterschiedlichen Betriebszuständen.
In the following preferred embodiments of the invention will be explained in more detail with reference to schematic drawings.
Show it:
  • Figure 1 is a circuit diagram of a valve assembly according to the invention for connecting a consumer with a variable displacement pump;
  • Figures 2 to 4 is a schematic diagram of the valve assembly according to the invention in different operating conditions.

Figur 1 zeigt ein vereinfachtes Schaltschema einer Ventilanordnung 1, über die ein hydraulischer Verbraucher 2, beispielsweise ein Aggregat einer Spritzgußmaschine mit einer Verstellpumpe 4 verbindbar ist. Über die Ventilanordnung 1 kann der maximale Verbraucherdruck begrenzt und ein zur Betätigung der Stellglieder 6 der Verstellpumpe 4 erforderlicher Mindestdruck eingestellt werden. Die Verstellpumpe 4 kann beispielsweise als Kolbenpumpe, vorzugsweise Axialkolbenpumpe oder Radialkolbenpumpe ausgeführt sein, wobei das Stellglied 6 durch einen Stellzylinder mit zugeordnetem Regelventil gebildet ist.Figure 1 shows a simplified circuit diagram of a valve assembly 1, via which a hydraulic consumer 2, for example an aggregate of an injection molding machine with a variable displacement pump 4 is connectable. About the valve assembly 1, the maximum consumer pressure can be limited and a required for the actuation of the actuators 6 of the variable 4 minimum pressure can be set. The variable displacement pump 4 can be designed for example as a piston pump, preferably axial piston pump or radial piston pump, wherein the actuator 6 is formed by a control cylinder with associated control valve.

Die erfindungsgemäße Ventilanordnung 1 hat einen Eingangsanschluß P, an den der Druckanschluß der Verstellpumpe 4 angeschlossen ist. Der Verbraucher 2 ist an einen Verbraucheranschluß A angeschlossen, während ein Tank 8 an einen Tankanschluß T angeschlossen ist.The valve assembly 1 according to the invention has an input port P to which the pressure port of the variable displacement pump 4 is connected. The consumer 2 is connected to a consumer port A, while a tank 8 is connected to a tank port T.

Zur Einstellung des zur Verstellung der Verstellpumpe 4 erforderlichen Mindestdruckes ist in einer den Druckanschluß P mit dem Arbeitsanschluß A verbindenden Druckleitung 10 ein Vorspannventil 12 angeordnet, dessen Staukörper über eine Vorspannfeder 14 in Schließrichtung und über den Druck in der Druckleitung 10 in Öffnungsrichtung beaufschlagt ist.To set the minimum pressure required for adjustment of the variable 4 is in a pressure connection P to the working port A connecting pressure line 10, a biasing valve 12 is arranged, the bluff body is acted upon by a biasing spring 14 in the closing direction and the pressure in the pressure line 10 in the opening direction.

Zur Begrenzung des maximalen Verbraucherdruckes ist ein vorgesteuertes Druckbegrenzungsventil 16 vorgesehen, das in Schließrichtung durch einen über eine Pilotventilanordnung 18 vorgegebenen Vorsteuerdruck beaufschlagt ist. In der der Prinzipdarstellung gemäß Figur 1 sind Ventil 12 und Druckbegrenzungsventil 16 getrennt voneinander dargestellt - wie sich aus den nachfolgenden Erläuterungen ergibt, sind die beiden Bauelemente 12, 16 in einer gemeinsamen Ventilanordnung integriert, wobei die Vorspannfeder 14 auch den Ventilkörper des Druckbegrenzungsventil 16 in Schließrichtung vorspannt.To limit the maximum consumer pressure, a pilot-operated pressure relief valve 16 is provided, which is acted upon in the closing direction by a pre-control pressure which is predetermined via a pilot valve arrangement 18. In the schematic diagram of Figure 1 valve 12 and pressure relief valve 16 are shown separately from each other - as can be seen from the following explanations, the two components 12, 16 are integrated in a common valve assembly, wherein the biasing spring 14 and the Valve body of the pressure relief valve 16 biases in the closing direction.

Über die Pilotventilanordnung 18 läßt sich der über eine Steuerleitung 20, in der sich eine Düse befindet, von der Druckleitung 10 abgegriffene Verbraucherdruck individuell in Abhängigkeit von den Betriebsbedingungen begrenzen.Via the pilot valve arrangement 18, the consumer pressure tapped off from the pressure line 10 via a control line 20 in which a nozzle is located can be individually limited as a function of the operating conditions.

Bei dem in Figur 1 dargestellten Ausführungsbeispiel hat die Pilotventilanordnung drei parallel geschaltete, als Druckbegrenzungsventile ausgeführte Vorsteuerventile 22, 23, 24, wobei das eine Vorsteuerventil 22 direkt in die Steuerleitung 20 geschaltet ist, während den beiden verbleibenden Vorsteuerventilen 23, 24 ein vorzugsweise elektrisch verstellbares Wegeventil 26 vorgeschaltet ist, über das eines der beiden Vorsteuerventile 23, 24 wahlweise zuschaltbar ist. In der dargestellten Grundstellung des Wegeventils 26 ist das Vorsteuerventil 22 wirksam, über das der maximal wirksame Verbraucherdruck auf einen Höchstdruck begrenzbar ist. Die beiden Vorsteuerventile 23, 24 begrenzen den maximalen Verbraucherdruck auf niedrigere Drücke als das Vorsteuerventil 22, so daß durch Umschalten des Wegeventils 26 und durch entsprechendes Zuschalten des Vorsteuerventils 23 oder 24 entsprechend veränderte Maximalverbraucherdrücke einstellbar sind.In the embodiment shown in Figure 1, the pilot valve assembly has three parallel connected, designed as pressure relief valves pilot valves 22, 23, 24, wherein the pilot valve 22 is connected directly into the control line 20, while the two remaining pilot valves 23, 24, a preferably electrically adjustable directional control valve 26 upstream, via which one of the two pilot valves 23, 24 is selectively switched on. In the illustrated basic position of the directional control valve 26, the pilot valve 22 is effective, via which the maximum effective consumer pressure can be limited to a maximum pressure. The two pilot valves 23, 24 limit the maximum consumer pressure to lower pressures than the pilot valve 22, so that by switching the directional control valve 26 and by appropriately connecting the pilot valve 23 or 24 correspondingly changed maximum consumer pressures are adjustable.

Anstelle mehrerer parallel geschalteter Druckbegrenzungsventile kann - wie in Figur 1 angedeutet - auch ein elektrisch verstellbares Druckbegrenzungsventil 28 als Pilotventil verwendet werden. Der Ausgangsanschluß der Pilotventilanordnung 18 ist an den Tankanschluß T angeschlossen.Instead of a plurality of pressure-limiting valves connected in parallel, it is also possible, as indicated in FIG. 1, to use an electrically adjustable pressure-limiting valve 28 as a pilot valve. The output port of the pilot valve assembly 18 is connected to the tank port T.

Figur 2 zeigt eine stark vereinfachte Schnittdarstellung durch eine Ventilanordnung 1, mit der die in Figur 1 dargestellte Schaltung realisiert ist. Demgemäß hat die Ventilanordnung 1 ein Ventilgehäuse 30, in dessen Ventilbohrung 32 ein Staukörper 34 geführt ist. Dieser ist über die Vorspannfeder 14 gegen einen Ventilsitz 36 vorgespannt, so daß der Druckanschluß P gegenüber dem Arbeitsanschluß A abgesperrt ist. Wie im folgenden noch näher erläutert wird, wirkt bei dem in Figur 2 dargestellten Ausführungsbeispiel der Staukörper 34 als gemeinsames Ventilglied sowohl für das Ventil 12 als auch für das Druckbegrenzungsventil 16.Figure 2 shows a greatly simplified sectional view through a valve assembly 1, with which the circuit shown in Figure 1 is realized. Accordingly, the valve assembly 1 has a valve housing 30, in the valve bore 32, a bluff body 34 is guided. This is biased by the biasing spring 14 against a valve seat 36, so that the pressure port P is shut off from the working port A. As will be explained in more detail below, in the exemplary embodiment illustrated in FIG. 2, the bluff body 34 acts as a common valve member for both the valve 12 and the pressure relief valve 16.

Der Staukörper 34 ist als tassenförmiger Kolben ausgeführt, in dessen Boden die Düse 38 angeordnet ist, über die der Innenraum 40 des Kolbens mit einem Federraum 42 der Ventilanordnung 1 verbindbar ist. D.h., der Druck am Druckanschluß P wird in Schließstellung des Staukörpers 34 über den Innenraum 40 und die Düse 38 in den Federraum 42 übertragen, so daß der Staukörper 34 neben der Kraft der Vorspannfeder 14 durch den Steuerdruck im Federraum 42 in Schließstellung vorgespannt ist.The bluff body 34 is designed as a cup-shaped piston, in the bottom of the nozzle 38 is arranged, via which the interior 40 of the piston with a spring chamber 42 of the valve assembly 1 is connectable. That is, the pressure at the pressure port P is transmitted in the closed position of the bluff body 34 via the interior 40 and the nozzle 38 in the spring chamber 42, so that the bluff body 34 is biased in addition to the force of the biasing spring 14 by the control pressure in the spring chamber 42 in the closed position.

Im Federraum 42 mündet ein Vorspannanschluß 44, der über eine Tankleitung 46 mit dem Tank 8 verbunden ist. In der Tankleitung 46 ist ein als Stauventil wirksames Rückschlagventil 48 vorgesehen, dessen Schließfeder 50 in Abhängigkeit von dem zur Verstellung der Verstellpumpe 4 einzustellenden Mindestdruck gewählt ist. Der Vorspannanschluß 44 bildet einen Drosselquerschnitt 52 aus, der während der Axialbewegung des Staukörpers 34 durch dessen bodenseitige Umfangskante 54 zu- bzw. aufsteuerbar ist.In the spring chamber 42 opens a biasing terminal 44 which is connected via a tank line 46 to the tank 8. In the tank line 46, an effective as a check valve check valve 48 is provided, the closing spring 50 is selected in response to the adjustment of the variable 4 to be set minimum pressure. The biasing terminal 44 forms a throttle cross-section 52, which during the axial movement of the bluff body 34 by the bottom-side peripheral edge 54 is open or aufsteuerbar.

Im Bereich zwischen dem Ventilsitz 36 und dem Vorspannanschluß 44 mündet in der Axialbohrung 32 ein Druckbegrenzungsanschluß 56, der stromabwärts des Rückschlagventils 48 mit der Tankleitung 46 verbunden ist. Dieser Druckbegrenzungsanschluß 56 kann beim Abheben des Staukörpers 34 vom Ventilsitz 36 durch eine weitere Steuerkante 58 aufgesteuert werden, die durch einen Durchbruch 60 im Mantel des Staukörpers 34 gebildet ist.In the area between the valve seat 36 and the biasing port 44 opens into the axial bore 32, a pressure limiting port 56 which is connected downstream of the check valve 48 to the tank line 46. When the bluff body 34 is lifted off from the valve seat 36, this pressure limiting connection 56 can be replaced by another one Control edge 58 are turned on, which is formed by an opening 60 in the jacket of the bluff body 34.

Im Federraum 42 der Ventilanordnung 1 mündet des weiteren eine zum elektromagnetisch proportional verstellbaren Druckbegrenzungsventil 28 führende Vorsteuerleitung 62.In the spring chamber 42 of the valve assembly 1 further opens a leading to the electromagnetically proportional pressure relief valve 28 pilot control line 62nd

Figur 2 zeigt die Ventilanordnung in ihrer Grundposition, in der der Druck am Arbeitsanschluß A geringer als der für die Verstellung der Verstellpumpe 4 erforderlichen Mindestdruck ist. Es sei angenommen, daß das Druckbegrenzungsventil 28 auf 192 bar eingestellt ist und die Kraft der Vorspannfeder 14 einem Druck von 8 bar und die Kraft der Schließfeder 50 einem Druck von 10 bar entspricht. Demgemäß öffnet das Rückschlagventil 48 bei einem Druck von 10 bar im Federraum 42, so daß die Rückseite des Staukörpers 34 mit einer Kraft in Schließrichtung beaufschlagt ist, die einem Druck von 18 bar (Schließfeder 14 8 bar, Rückschlagventil 48 10 bar) entspricht. Bei Erreichen dieses Mindestdruckes im Druckanschluß P wird der Staukörper 34 gemäß der Darstellung in Figur 2 von seinem Ventilsitz 36 abgehoben und die Verbindung zum Verbraucheranschluß A aufgesteuert. Dabei wird durch das sich öffnende Stauventil 16 der Mindestdruck auf den vom Verbraucher benötigten Lastdruck abgedrosselt. Die Ventilanordnung ist in Staufunktion. Es fließt ein Steuerölstrom, dessen Größe vom Querschnitt der Düse 38 und der Druckdifferenz (von 8 bar) über der Düse bestimmt ist, über die Düse 18 und das Rückschlagventil 48 zum Tank.Figure 2 shows the valve assembly in its basic position in which the pressure at the working port A is less than the minimum pressure required for the adjustment of the variable 4. It is assumed that the pressure relief valve 28 is set to 192 bar and the force of the biasing spring 14 is a pressure of 8 bar and the force of the closing spring 50 corresponds to a pressure of 10 bar. Accordingly, the check valve 48 opens at a pressure of 10 bar in the spring chamber 42, so that the back of the bluff body 34 is acted upon by a force in the closing direction, which corresponds to a pressure of 18 bar (closing spring 14 8 bar, check valve 48 10 bar). Upon reaching this minimum pressure in the pressure port P of the bluff body 34 is lifted as shown in Figure 2 of its valve seat 36 and opened the connection to the consumer port A. In this case, the minimum pressure is throttled to the load pressure required by the consumer by the opening damper 16. The valve assembly is in storage function. It flows a control oil flow whose size is determined by the cross section of the nozzle 38 and the pressure difference (of 8 bar) above the nozzle, via the nozzle 18 and the check valve 48 to the tank.

Auch bei einem Lastdruck höher als 18 bar im Arbeitsanschluß A herrscht am Staukörper 34 nur dann ein Kräftegleichgewicht, wenn der Druck im Federraum 42 um 8 bar, nämlich um das Druckäquivalent zur Kraft der Vorspannfeder 14, kleiner ist als der Lastdruck. Bei einem über 18 bar liegenden Lastdruck nimmt somit der Staukörper 34 eine Position nahe der nach Figur 2 ein, in der er mit seiner Umfangskante 54 einen Drosselquerschnitt 52 zwischen dem Federraum 42 und dem Vorspannanschluß 44 so steuert, daß die bei einer Druckdifferenz von 8 bar über die Düse 38 dem Federraum 42 zufließende Steuerölmenge gleich der bei einer Druckdifferenz von Lastdruck minus 8 bar (= Druck im Federraum 42) minus 10 bar (= Vorspanndruck des Rückschlagventils 48) aus dem Federraum 42 über das Rückschlagventil 48 zum Tank 8 abfließenden Ölmenge ist.Even with a load pressure higher than 18 bar in the working port A prevails on the bluff body 34 only a balance of forces when the pressure in the spring chamber 42 by 8 bar, namely the pressure equivalent to the force of the biasing spring 14, is smaller than the load pressure. With a load pressure of over 18 bar, the bluff body thus decreases 34 a position close to that of Figure 2, in which he controls with its peripheral edge 54 a throttle cross-section 52 between the spring chamber 42 and the biasing port 44 so that the at a pressure difference of 8 bar via the nozzle 38 the spring chamber 42 flowing amount of control oil equal to at a pressure difference of load pressure minus 8 bar (= pressure in the spring chamber 42) minus 10 bar (= bias pressure of the check valve 48) from the spring chamber 42 via the check valve 48 to the tank 8 effluent oil.

Die Ventilanordnung hat in einem solchen Betriebszustand praktisch keine Funktion.The valve arrangement has virtually no function in such an operating state.

Mit ansteigendem Druck am Verbraucheranschluß A wird der Drosselquerschnitt 52 immer mehr zugesteuert. Solange der Lastdruck ein Niveau hat, das das Druckbegrenzungsventil 28 nicht ansprechen läßt, verbleibt der Staukörper 34 in einer Position unterhalb der in Figur 3 gezeigten Position, in der der Drosselquerschnitt 52 gerade noch etwas offen sein möge.With increasing pressure at the consumer port A, the throttle cross-section 52 is increasingly fed. As long as the load pressure has a level that does not respond to the pressure limiting valve 28, the bluff body 34 remains in a position below the position shown in Figure 3, in which the throttle cross section 52 may just be slightly open.

Bei Überschreiten des über das Druckbegrenzungsventil 28 eingestellten Maximaldruckes im Federraum 42 von 192 bar, d.h. einem am Verbraucher wirksamen maximalen Lastdruck von 200 bar (8 bar Vorspannfeder 14, 192 bar Druckbegrenzungsventil 28), öffnet das Druckbegrenzungsventil 28, so daß das dem Federraum 42 zufließende Steueröl über die Vorsteuerleitung 62 zum Tank 8 fließen und der Druck im Federraum 42 nicht weiter ansteigen kann. Der Vorsteuerkörper 34 kann dann gemäß Figur 4 über die in Figur 3 dargestellte Position hinausbewegt werden, so daß nach einem vorbestimmten Hub über die weitere Steuerkante 58 der Druckbegrenzungsanschluß 56 aufgesteuert wird. Es kann Druckmittel direkt über den Innenraum 40 und den Durchbruch 60 in die Tankleitung 46 und somit zum Tank 8 hin abströmen, so daß der Druck im Verbraucheranschluß A einen Wert knapp über 200 bar nicht überschreiten kann. Die Ventilanordnung befindet sich in ihrer Druckbegrenzungsfunktion.When exceeding the set via the pressure limiting valve 28 maximum pressure in the spring chamber 42 of 192 bar, ie a load effective maximum load pressure of 200 bar (8 bar biasing spring 14, 192 bar pressure relief valve 28), opens the pressure relief valve 28, so that the spring chamber 42 flowing Control oil flow via the pilot line 62 to the tank 8 and the pressure in the spring chamber 42 can not increase. The pilot body 34 can then be moved beyond the position shown in Figure 3 according to Figure 4, so that after a predetermined stroke on the further control edge 58 of the pressure limiting port 56 is opened. It can flow pressure medium directly through the interior 40 and the opening 60 in the tank line 46 and thus to the tank 8 out, so that the pressure in the consumer port A can not exceed a value just above 200 bar. The Valve arrangement is in its pressure limiting function.

Bei der erfindungsgemäßen Lösung sind somit das Stauventil 12 und das Druckbegrenzungsventil 16 ineinander integriert, wobei der Staukörper 34 als gemeinsames Ventilglied für beide Bauelemente wirkt. Der zu begrenzende Systemdruck kann auf einfache Weise über das Pilotventil 28 eingestellt werden, so daß die Ventilanordnung an unterschiedliche Betriebsbedingungen anpaßbar ist.In the solution according to the invention thus the accumulation valve 12 and the pressure relief valve 16 are integrated with each other, wherein the bluff body 34 acts as a common valve member for both components. The system pressure to be limited can be adjusted in a simple manner via the pilot valve 28, so that the valve arrangement can be adapted to different operating conditions.

Wie eingangs erwähnt, kann anstelle des elektrisch verstellbaren Druckbegrenzungsventils 28 auch eine Parallelschaltung von festeingestellten Druckbegrenzungsventilen oder eine ähnliche Ventilanordnung verwendet werden.As mentioned above, instead of the electrically adjustable pressure relief valve 28, a parallel connection of fixed pressure relief valves or a similar valve arrangement can be used.

Offenbart ist eine Ventilanordnung zur Versorgung eines hydraulischen Verbrauchers mit einem Druckmittel, wobei über ein Vorspannventil ein zur Verstellung einer Verstellpumpe erforderlicher Mindestdruck einstellbar ist. Der maximale Verbraucherdruck wird über ein Druckbegrenzungsventil begrenzt, wobei dem Druckbegrenzungsventil eine Pilotventilanordnung zugeordnet ist, über die der in Schließrichtung eines Staukörpers des Druckbegrenzungsventils wirksame Steuerdruck veränderbar ist.Disclosed is a valve arrangement for supplying a hydraulic consumer with a pressure medium, wherein a biasing valve for adjusting a variable displacement required minimum pressure is adjustable. The maximum consumer pressure is limited by a pressure limiting valve, wherein the pressure limiting valve is associated with a pilot valve arrangement, via which the effective in the closing direction of a bluff body of the pressure relief valve control pressure is variable.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Ventilanordnungvalve assembly
22
Verbraucherconsumer
44
Verstellpumpevariable
66
Stellgliedactuator
88th
Tanktank
1010
Druckleitungpressure line
1212
VorspannventilPre-load valve
1414
Vorspannfederbiasing spring
1616
DruckbegrenzungsventilanordnungPressure relief valve assembly
1818
PilotventilanordnungPilot valve assembly
2020
Steuerleitungcontrol line
2222
Vorsteuerventilpilot valve
2323
Vorsteuerventilpilot valve
2424
Vorsteuerventilpilot valve
2626
Wegeventilway valve
2828
elektrisch betätigbares Druckbegrenzungsventilelectrically actuated pressure relief valve
3030
Ventilgehäusevalve housing
3232
Ventilbohrungvalve bore
3434
Staukörperbaffle
3636
Ventilsitzvalve seat
3838
Düsejet
4040
Innenrauminner space
4242
Federraumspring chamber
4444
Vorspannanschlußbias terminal
4646
Tankleitungtank line
4848
Rückschlagventilcheck valve
5050
Schließfederclosing spring
5252
DrosselquerschnittThrottle cross section
5454
Umfangskanteperipheral edge
5656
DruckbegrenzungsanschlußPressure relief port
5858
weitere Steuerkantefurther control edge
6060
Durchbruchbreakthrough
6262
Vorsteuerleitungpilot line

Claims (11)

  1. Valve arrangement for supplying a hydraulic consumer (2) with pressurised means, having a pressure connection (P), a consumer connection (A) and a stop member (34) which is pretensioned relative to a valve seat (36) by means of a pretensioning spring (14) which is arranged in a resilient space (42) and which, when a minimum pressure is reached in the pressure connection (P), controls a connection between the pressure connection (P) and the consumer connection (A) in an opening manner, and having a pressure limitation connection (56) which, by being controlled in an opening manner relative to the other two connections (P, A), allows the pressure in these connections to be limited to a maximum value, characterised in that the pressure limitation connection (56) can be controlled in an opening manner relative to the other two connections (P, A) by means of the stop member (34), in that the resilient space (42) is connected to the pressure connection (P) by means of a nozzle (38) and there are connected to the resilient space (42), on the one hand, a pilot valve arrangement (18, 28) and, on the other hand, a stop valve (48) by means of a throttle cross-section (52) which can be adjusted by the stop member (34).
  2. Valve arrangement according to patent claim 1, having a pressure limitation valve (16) for limiting the maximum consumer pressure, the pilot valve arrangement (18, 28) being associated with the pressure limitation valve (16) in order to modify the maximum consumer pressure which can be set by means of the pressure limitation valve (16).
  3. Valve arrangement according to patent claim 1 or 2, a connection between the pressure connection (P) and a tank connection (T) being able to be controlled in an opening manner by means of the pressure limitation connection (56).
  4. Valve arrangement according to any one of the preceding patent claims, the pilot valve arrangement (18, 28) being connected, by means of a pilot line (62), to the resilient space (42) which can be connected to the tank (8) by means of the adjustable throttle cross-section (52) and the stop valve (48).
  5. Valve arrangement according to any one of the preceding patent claims, the stop member (34) having a first control edge (54), by means of which the throttle cross-section (52) can be controlled in a closing manner as the consumer pressure increases.
  6. Valve arrangement according to patent claim 5, the stop member (34) having an additional control edge (58) by means of which the pressure limitation connection (56) can be controlled in an opening manner when the maximum consumer pressure set by means of the pilot valve arrangement (18, 28) is exceeded.
  7. Valve arrangement according to patent claim 6, the additional control edge (58) being formed by an aperture (60) in the cover of the stop member (34).
  8. Valve arrangement according to any one of the preceding patent claims, the control valve being a non-return valve (48).
  9. Valve arrangement according to any one of the preceding patent claims, the pilot valve arrangement having an electrically adjustable pressure limitation valve (28).
  10. Valve arrangement according to any one of patent claims 1 to 8, the pilot valve arrangement (18) having a plurality of pressure limitation valves (22, 23, 24) which can be optionally connected by means of a directional control valve (26).
  11. Valve arrangement according to any one of the preceding patent claims, the nozzle (38) being arranged in the base of the stop member (34).
EP20010119038 2000-08-17 2001-08-07 Valve assembly Expired - Lifetime EP1180598B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10040737A DE10040737A1 (en) 2000-08-17 2000-08-17 Valve arrangement for pressure medium supply hydraulic consumer has consumer pressure limitation valve with pilot valve unit
DE10040737 2000-08-17

Publications (3)

Publication Number Publication Date
EP1180598A2 EP1180598A2 (en) 2002-02-20
EP1180598A3 EP1180598A3 (en) 2003-04-16
EP1180598B1 true EP1180598B1 (en) 2006-11-08

Family

ID=7653094

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20010119038 Expired - Lifetime EP1180598B1 (en) 2000-08-17 2001-08-07 Valve assembly

Country Status (2)

Country Link
EP (1) EP1180598B1 (en)
DE (2) DE10040737A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112007001972A5 (en) * 2006-09-14 2009-05-28 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydraulic system for supplying a hydraulic fluid to a consumer
DE102016122392A1 (en) * 2016-11-21 2018-05-24 Schwing Gmbh Slurry pump with adjustable limitation of the delivery pressure

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2120125A1 (en) * 1971-04-24 1972-11-16 Robert Bosch Gmbh, 7000 Stuttgart Hydraulic system
NL169628C (en) * 1971-06-29 1982-08-02 Ind En Handelmaatschappij Kopp CONTROL DEVICE FOR LAST-DEPENDENT CONTROL OF HYDRAULIC DRIVE DEVICES.
DE2249743A1 (en) * 1972-10-11 1974-04-18 Kloeckner Humboldt Deutz Ag VALVE UNIT
DE3603988C2 (en) * 1984-11-28 1994-12-08 Zahnradfabrik Friedrichshafen Control device for two hydraulic actuating devices, each of which is supplied by a high-pressure pump via a current branch
DE4211551C2 (en) * 1992-04-06 1998-03-26 Rexroth Mannesmann Gmbh Variable pump with a pressure limiting and a pressure connection valve
DE4335495A1 (en) * 1992-10-27 1994-04-28 Bosch Gmbh Robert Gritter or sander vehicle hydraulic appts. control device - measures pressure and revs. rate of hydromotor and controls valve to provide correct pressure of fluid
DE4334167A1 (en) * 1993-10-07 1995-04-13 Rexroth Mannesmann Gmbh Hydraulic system for loading a hydraulic consumer with a regulated consumer pressure and choke valve in particular for use in such a hydraulic system
JPH10131751A (en) * 1996-10-29 1998-05-19 Aisin Seiki Co Ltd Tandem pump device
DE19729693A1 (en) * 1997-07-11 1999-01-14 Claas Industrietechnik Gmbh Hydraulic control for switchable connecting elements, in particular for an externally switched clutch on a drive motor

Also Published As

Publication number Publication date
DE50111399D1 (en) 2008-03-13
EP1180598A3 (en) 2003-04-16
DE10040737A1 (en) 2002-02-28
EP1180598A2 (en) 2002-02-20

Similar Documents

Publication Publication Date Title
EP0638746B1 (en) Pilot stage for a pressure control valve
DE4431330B4 (en) Seat valve with force feedback control
EP0294776A1 (en) Control circuit for a hydraulic adjusting device
EP0016719B1 (en) Hydraulic motor control device
EP0958455B1 (en) Hydraulic control circuit for a priority and for a secondary hydraulic consumer
DE60304663T2 (en) Hydraulic valve device
EP1625307A1 (en) Valve
WO2007096030A1 (en) Hydraulic control arrangement
DE10019254C2 (en) Pressure control valve
DE19524900C2 (en) Pilot operated pressure relief valve
DE2843576A1 (en) PUMP CONTROL ARRANGEMENT
DE4112065C2 (en) Pilot operated pressure cut-off valve with adjustable switching pressure difference
EP2126371B1 (en) Valve arrangement
DE3320047C2 (en)
EP0115590A2 (en) Hydraulic control device
EP1180598B1 (en) Valve assembly
DE3422164C2 (en) Hydraulic system with at least two consumers of hydraulic energy
WO2003087585A1 (en) Hydraulic control system using load-sensing technology
DE19632368A1 (en) Electrohydraulic regulation path valve for controlling hydraulic setting motor
EP0624732B1 (en) Hydraulic control device
DE4026849C2 (en) Valve arrangement for generating a control pressure in a hydraulic system
EP1686268B1 (en) Hydraulic control device
EP1481167B1 (en) Valve arrangement
EP1452744B1 (en) Hydraulic control device
DE3239965A1 (en) Electro-hydraulic control arrangement

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO SI

17P Request for examination filed

Effective date: 20030515

AKX Designation fees paid

Designated state(s): DE FR GB IT

17Q First examination report despatched

Effective date: 20040628

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20061116

EN Fr: translation not filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20070809

REF Corresponds to:

Ref document number: 50111399

Country of ref document: DE

Date of ref document: 20080313

Kind code of ref document: P

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070622

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20061108

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20120823

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20120824

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20121024

Year of fee payment: 12

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20130807

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140301

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50111399

Country of ref document: DE

Effective date: 20140301

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130807

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130807