EP2411679B1 - Hydraulic valve device - Google Patents

Hydraulic valve device Download PDF

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Publication number
EP2411679B1
EP2411679B1 EP20100703625 EP10703625A EP2411679B1 EP 2411679 B1 EP2411679 B1 EP 2411679B1 EP 20100703625 EP20100703625 EP 20100703625 EP 10703625 A EP10703625 A EP 10703625A EP 2411679 B1 EP2411679 B1 EP 2411679B1
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EP
European Patent Office
Prior art keywords
connector
load
fluid
valve device
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP20100703625
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German (de)
French (fr)
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EP2411679A1 (en
EP2411679B8 (en
Inventor
Winfried RÜB
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.)
Hydac Filtertechnik GmbH
Original Assignee
Hydac Fluidtechnik GmbH
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Publication date
Application filed by Hydac Fluidtechnik GmbH filed Critical Hydac Fluidtechnik GmbH
Publication of EP2411679A1 publication Critical patent/EP2411679A1/en
Publication of EP2411679B1 publication Critical patent/EP2411679B1/en
Application granted granted Critical
Publication of EP2411679B8 publication Critical patent/EP2411679B8/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—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
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7758—Pilot or servo controlled
    • Y10T137/7762—Fluid pressure type
    • Y10T137/7764—Choked or throttled pressure type

Definitions

  • a hydraulic control arrangement for controlling a hydraulic consumer in particular in the form of a mobile working device, said consumer by means of a continuously adjustable directional control valve assembly via a flow to a pump and a drain with a tank is connected, wherein a continuously adjustable directional control valve of the directional control valve assembly a basic position auf askt a circulation channel, via which the pump is connected to the tank and in which a circulation pressure compensator is arranged.
  • a continuously adjustable directional control valve of the directional control valve assembly a basic position auf askt a circulation channel, via which the pump is connected to the tank and in which a circulation pressure compensator is arranged.
  • In the control positions of the directional control valve of the circulation channel is zuu mortbar and a flow line to the pressure medium supply of the consumer auf mortbar.
  • the directional control valve arrangement has a drain valve disposed in the flow, the opening cross-section is independent of the control of the directional control valve is adjustable, a kind of separate drain groove is formed, which can be controlled depending on the operating conditions in a suitable manner regardless of the inlet cross-section.
  • a pressure for biasing the consumer can be set.
  • the volume flow can be predetermined via the inlet and then the speed of the consumer can be set by setting the outlet throttle valve.
  • a generic hydraulic valve device is known with a pressure sensing device, in which a slider is arranged as a movable control device in a housing bore and movable from a neutral position into two working positions, wherein the slider has a central collar portion and two thereof separated by a respective slide annular groove Endbunde and said bundles have on the sides facing each other on peripheral portions limited throttle profiles.
  • the housing bore has a pressure medium-supplyable pump annular groove, on both sides of each one connectable to a motor line engine annular groove and on both sides outside of each one connectable to the container container annular groove is present.
  • the pressure sensing device has at least one circumferentially offset on the slider circumference and connected via a connecting channel in the slide with a pressure sensing port pressure sensing port which is connected in the working position of the slide with the pressure-carrying lines to be sensed, but separated in the neutral position of her is.
  • At least one of the pressure-sensing openings is arranged in the central collar section for determining the inlet pressure in the pump annular groove, wherein a fixed throttle and in the connecting channel within the slide on the outside of the slide between a pressure sensing annular groove and the container annular groove in the housing bore a variable, is provided by the slide position dependent throttle, a smaller dead path of the slider between the neutral position and the working position is possible, resulting in a small-building overall Valve device leads.
  • the present invention seeks to provide a hydraulic valve device with a fine control is possible until it comes to actually moving the load connected to the respective Nutzanschluß.
  • a related object solves a hydraulic valve device with the features of claim 1 in its entirety.
  • a predefinable control pressure on the displaceable control device preferably in the form of a control slide, precludes a compensation pressure derived from the actual load pressure, which keeps the control device in the fine control range until the load connected to the utility connections A, B moves.
  • the control device can move into a position as wide open as it allows the back pressure from the accelerating load, the leakage current is increasingly switched off. If the leakage current is completely switched off, a volume control that is the same as with load-sensing valves is realized and the pressure control is switched off. In the transition area, pressure and volume flow control are superimposed.
  • control device in the form of a control slide fluid-carrying connection channels, which connect the pairwise mutually assignable load sensing and load signaling connections.
  • one of the connecting channels is formed as a central channel which is connected to one of the throttle points, wherein the other throttle point opens into an annular channel which is coaxial with the central channel arranged by an inner recess of the spool and an insert sleeve is limited is penetrated by the center channel.
  • control device is preceded by a pressure compensator, with which the so-called.
  • a pressure compensator with which the so-called.
  • Mengenabschneidung by a load sensing pressure limitation in the spring chamber of the pressure compensator is possible.
  • this function of Mengenabschneidung is not possible or to obtain only over appropriate additional valve constructions in a complex manner.
  • the control function of the pressure balance is improved by a relatively large discharge cross-section can open into the return port. In that regard, a so-called. Floating position for the overall arrangement is improved.
  • the Fig.1 shows a designated as a whole with 10 fluid port arrangement.
  • the dahi next fluid connection assembly 10 has a pressure supply terminal P, a return port, R, a load-sensing terminal LS, two control terminals P A 'and P B ' and two Nutzan nowadays A, B on.
  • the said fluid connections in the direction of the Fig.1 Seen from left to right P A ', P, R, P B ' and LS and the Nutzan getting A and B are housed in a control housing 12, wherein in the direction of the Fig.1 seen the lower end of the control housing 12 is provided with a conventional pressure compensator 14, on the structural design so far not discussed in more detail.
  • the pressure compensator 14 is connected upstream of the terminals P A ', P B ' and controls the control terminals P A ', P B ' according to the specification of the applied LS signal in this respect.
  • Mengenabschneidung is achieved by a LS-pressure limitation in the so-called spring chamber (not shown) of the pressure balance, with a encouragenabschneidung example, make sense if a steering cylinder connected to the Nutzan say A, B am Stop is and you want to cut off the inflow so far to avoid overloads.
  • control device 18 The designated as a whole with 16 control device as such is controlled in a known and therefore no longer described manner of conventional pilot valves, the sake of simpler representation in the Fig.1 are shown only insofar as their respective assignable pilot terminal housing 18,20 are addressed.
  • the two pilot valves supply at least for the control device 18 two counteracting control pressures X A and X B, respectively.
  • the said control device 16 has a viewing direction on the Fig.1 Seen horizontally displaceable spool 22, which in the Fig.1 is shown in its undeflected middle or neutral position.
  • the pertinent neutral position of the spool 22 is supported by two spring memory, which are designed as compression springs 24 and are integrated in a respective assignable spring chamber 26,28 in the assignable pilot port housings 18 and 20 respectively.
  • the simpler representation because of looking in the direction of Fig.1 seen for the left spring chamber 26, the compression spring 24 is not shown.
  • the pertinent structure is known in such hydraulic valve devices, so that in this respect will not be discussed here at this point.
  • the control device 16 with control slide 22 is provided with load-sensing connections LF A and LF B and load-indicating connections LM A and LM B , which are interconnected in pairs carrying fluid. And that is, as in particular the bottom view representation of Fig.1 after Fig.2 shows, the load sensing terminal LF A connected to the load signaling terminal LM A and the load sensing terminal LF B to the load signaling terminal LM B.
  • the latter are also referred to in technical language with signal lines are introduced in the form of radial transverse bores in the spool 22, and depending on which axial displacement position of the spool 22 occupies the said Load sensing and load signaling connections in fluid-conducting or blocking connection with the respectively assignable terminals of the fluid connection arrangement 10.
  • the load sensing and load signaling connections via fluid-carrying connection channels within the spool 22 in a assignable manner in conjunction with each other.
  • one of the connecting channels is designed as a central channel 30, which passes through the middle or longitudinal axis of the control spool 22 this completely and opens out at both ends to the outside.
  • the pertinent center channel 30 connects the load-sensing connection LF A to the load-signaling connection LM A in a fluid-conducting manner.
  • an annular channel 32 is provided, the right structural design is particularly apparent from the illustrations according to the Figure 3 and 4 results.
  • the pertinent annular channel 32 is inserted into an inner recess 34 of the spool 22 in the manner of a radial bore and bounded inwardly by the cylindrical outer periphery of an insert sleeve 36 which forms a part of the central channel 30 as a hollow cylinder.
  • the insert sleeve 36 is supported with its left end face on an introduced radial shoulder 38 in the spool 22 from.
  • a first throttle point da 1 introduced, which engages over the left frontal end of the spool 22 a piece in the center channel 30.
  • a second further restrictor db 1 is introduced on the opposite side, the configuration in particular in the Figure 3 and 4 is shown.
  • the pertinent throttle point db 1 is integrated in a screw plug 40 which is screwed via a threaded section 42 in an end-shaped recess of the spool 22.
  • valve plate 44 On the outer circumference of the pertinent screw plug 40 is overlapped by a kind of valve plate 44, under the action of the compression spring 24 in the direction of the Figure 3 and 4 seen that way is moved long in the neutral position until the valve plate 44 comes flush with its outer edge to the end face of the control housing 12, as in the Figure 3 and 4 shown.
  • the load-sensing connection LF A comes into coincidence with the Nutzanschluß A and the pressure applied there and then this via the center channel 30 and the load-sensing connection A to the load-sensing terminal LS, also formed in the manner of an annular channel, continue to report, as far as the load-signaling connection LM A enters the LS-ring channel.
  • the Lastmentlanschluß LF B enters the associated Nutzanschluß B and the sensed via the annular channel 32 pressure device via the load-sensing connection B in the annular channel with the nipples LS nipples LS.
  • the pertinent load sensing and signaling chain is then superimposed on the upcoming pilot valve generator pressure, which is present at the throttles da 1 and db 1 , respectively.
  • a third and fourth throttle since da 2 or db 2 may be introduced.
  • this can be realized via a conventional throttle, but also via a diaphragm.
  • the artificial Loadsensing pressure also acts on the above-described signal line and the connected throttles da 1 and db 1 back to the spool 22 and the spool 22 controls by its position and series connection (pressure divider circuit) of adjustable connection between P and user port A and the variable throttle to return port R the Pressure in the user port A. Due to the size of each variable throttle used, which depends on the spool stroke, the leakage current can be adjusted constructively to the stability of the pressure control.
  • the throttled pressure increases and the load will move accordingly.
  • the variable throttle can be turned off to the return port R, because now the acceleration phase is completed and the constant travel of the load is reached.
  • the encoder pressure X B now specifies how much volume flow must be supplied to the consumer so that the resulting dynamic pressure in A is not exceeded.

Description

Die Erfindung betrifft eine hydraulische Ventilvorrichtung mit einer Fluidanschlußanordnung, beinhaltend mindestens

  • einen Druckversorgungsanschluß P,
  • einen Rücklaufanschluß R,
  • einen Loadsensinganschluß LS,
  • zwei Steueranschlüsse PA' und PB' sowie
  • zwei Nutzanschlüsse A; B
und mit einer verfahrbaren Steuereinrichtung zum zumindest teilweise Ansteuern von Anschlüssen der Fluidanschlußanordnung, wobei die Steuereinrichtung von zwei entgegengesetzt wirkenden Pilotventilen ansteuerbar und federzentriert in ihrer Neutralstellung gehalten ist.The invention relates to a hydraulic valve device with a fluid connection arrangement, comprising at least
  • a pressure supply port P,
  • a return port R,
  • a load-sensing terminal LS,
  • two control terminals P A 'and P B ' and
  • two utility ports A; B
and with a movable control device for at least partially controlling connections of the fluid connection arrangement, wherein the control device is held by two oppositely acting pilot valves controllable and spring-centered in its neutral position.

Durch die EP 1 616 997 A1 ist eine hydraulische Steueranordnung zur Ansteuerung eines hydraulischen Verbrauchers bekannt, insbesondere in Form eines mobilen Arbeitsgerätes, wobei dieser Verbraucher mittels einer stetig einstellbaren Wegeventilanordnung über einen Vorlauf mit einer Pumpe und über einen Ablauf mit einem Tank verbindbar ist, wobei ein stetig einstellbares Wegeventil der Wegeventilanordnung in einer Grundposition einen Umlaufkanal aufsteuert, über den die Pumpe mit dem Tank verbunden ist und in dem eine Umlaufdruckwaage angeordnet ist. In den Steuerpositionen des Wegeventils ist der Umlaufkanal zusteuerbar und eine Vorlaufleitung zur Druckmittelversorgung des Verbrauchers aufsteuerbar. Dadurch, dass bei der bekannten Lösung die Wegeventilanordnung ein im Ablauf angeordnetes Ablaufdrosselventil hat, dessen Öffnungsquerschnitt unabhängig von der Ansteuerung des Wegeventils einstellbar ist, wird eine Art separate Ablaufnut gebildet, die je nach vorliegenden Betriebsbedingungen in geeigneter Weise unabhängig von dem Zulaufquerschnitt ansteuerbar ist. So läßt sich beispielsweise über das Ablaufdrosselventil im Ablauf ein Druck zum Vorspannen des Verbrauchers einstellen. Des weiteren kann beispielsweise der Volumenstrom über den Zulauf vorgegeben und dann durch Einstellung des Ablaufdrosselventils die Geschwindigkeit des Verbrauchers eingestellt werden.By the EP 1 616 997 A1 a hydraulic control arrangement for controlling a hydraulic consumer is known, in particular in the form of a mobile working device, said consumer by means of a continuously adjustable directional control valve assembly via a flow to a pump and a drain with a tank is connected, wherein a continuously adjustable directional control valve of the directional control valve assembly a basic position aufsteuert a circulation channel, via which the pump is connected to the tank and in which a circulation pressure compensator is arranged. In the control positions of the directional control valve of the circulation channel is zuusteuerbar and a flow line to the pressure medium supply of the consumer aufsteuerbar. Thereby, that in the known solution, the directional control valve arrangement has a drain valve disposed in the flow, the opening cross-section is independent of the control of the directional control valve is adjustable, a kind of separate drain groove is formed, which can be controlled depending on the operating conditions in a suitable manner regardless of the inlet cross-section. Thus, for example, via the outlet throttle valve in the process a pressure for biasing the consumer can be set. Furthermore, for example, the volume flow can be predetermined via the inlet and then the speed of the consumer can be set by setting the outlet throttle valve.

Durch die DE 38 02 672 C2 ist eine gattungsgemäße hydraulische Ventilvorrichtung bekannt mit einer Druckfühleinrichtung, bei der ein Schieber als verfahrbare Steuereinrichtung in einer Gehäusebohrung angeordnet und aus einer Neutralstellung in zwei Arbeitsstellungen bewegbar ist, wobei der Schieber einen mittleren Bundabschnitt und zwei hiervon durch je eine Schieber-Ringnut getrennte Endbunde aufweist und die genannten Bunde besitzen an den einander zugewandten Seiten auf Umfangsabschnitte beschränkte Drosselprofilierungen. Die Gehäusebohrung weist eine mit Druckmittel versorgbare Pumpen-Ringnut auf, zu deren beiden Seiten je eine mit einer Motorleitung verbindbare Motor-Ringnut und zu beiden Seiten außerhalb davon je eine mit dem Behälter verbindbare Behälter-Ringnut vorhanden ist. Die Druckfühleinrichtung weist mindestens eine am Schieberumfang gegenüber den Drosselprofilierungen in Umfangsrichtung versetzt angeordnete und über einen Verbindungskanal im Schieber mit einem Druckfühlanschluß verbundene Druckfühlöffnung auf, die in der Arbeitsstellung des Schiebers mit den zu fühlenden, druckführenden Leitungen verbunden ist, in der Neutralstellung aber von ihr abgetrennt ist. Dadurch, dass im mittleren Bundabschnitt zur Feststellung des Eingangsdruckes in der Pumpen-Ringnut mindestens eine der Druckfühlöffnungen angeordnet ist, wobei im Verbindungskanal innerhalb des Schiebers eine feste Drossel und an der Außenseite des Schiebers zwischen einer Fühldruck-Ringnut und der Behälter-Ringnut in der Gehäusebohrung eine variable, von der Schieberstellung abhängige Drossel vorgesehen ist, ist ein kleinerer Totweg des Schiebers zwischen der Neutralstellung und der Arbeitsstellung ermöglicht, was zu einer klein aufbauenden Gesamt-Ventilvorrichtung führt.By the DE 38 02 672 C2 a generic hydraulic valve device is known with a pressure sensing device, in which a slider is arranged as a movable control device in a housing bore and movable from a neutral position into two working positions, wherein the slider has a central collar portion and two thereof separated by a respective slide annular groove Endbunde and said bundles have on the sides facing each other on peripheral portions limited throttle profiles. The housing bore has a pressure medium-supplyable pump annular groove, on both sides of each one connectable to a motor line engine annular groove and on both sides outside of each one connectable to the container container annular groove is present. The pressure sensing device has at least one circumferentially offset on the slider circumference and connected via a connecting channel in the slide with a pressure sensing port pressure sensing port which is connected in the working position of the slide with the pressure-carrying lines to be sensed, but separated in the neutral position of her is. Due to the fact that at least one of the pressure-sensing openings is arranged in the central collar section for determining the inlet pressure in the pump annular groove, wherein a fixed throttle and in the connecting channel within the slide on the outside of the slide between a pressure sensing annular groove and the container annular groove in the housing bore a variable, is provided by the slide position dependent throttle, a smaller dead path of the slider between the neutral position and the working position is possible, resulting in a small-building overall Valve device leads.

Ausgehend von diesem Stand der Technik liegt der Erfindung die Aufgabe zugrunde, eine hydraulische Ventilvorrichtung zu schaffen, mit der eine Feinsteuerung möglich ist, bis es zum eigentlichen Bewegen der Last, angeschlossen am jeweiligen Nutzanschluß, kommt. Eine dahingehende Aufgabe löst eine hydraulische Ventilvorrichtung mit den Merkmalen des Patentanspruches 1 in seinerGesamtheit.Based on this prior art, the present invention seeks to provide a hydraulic valve device with a fine control is possible until it comes to actually moving the load connected to the respective Nutzanschluß. A related object solves a hydraulic valve device with the features of claim 1 in its entirety.

Dadurch; dass gemäß dem kennzeichnenden Teil des Patentanspruches 1 zwischen dem jeweiligen Pilotventil und der Steuereinrichtung mindestens eine Drosselstelle vorgesehen ist, die mit einem Lastfühlanschluß LFA sowie mit einem Lastmeldeanschluß LMA oder einem Lastfühlanschluß LFB sowie mit einem Lastmeldeanschluß LMB fluidführend verbunden ist, ist erreicht, dass einem vorgebbaren Ansteuerdruck an der verfahrbaren Steuereinrichtung, vorzugsweise in Form eines Steuerschiebers ausgebildet, ein vom tatsächlichen Lastdruck abgeleiteter Kompensationsdruck entgegensteht, der die Steuereinrichtung so lange im Feinsteuerbereich hält, bis die an den Nutzanschlüssen A, B angeschlossene Last sich bewegt. Dann kann die Steuereinrichtung in eine so weit geöffnete Position übergehen, wie es der Gegendruck aus der sich beschleunigenden Last erlaubt, wobei der Verluststrom zunehmend abgeschaltet wird. Wenn der Verluststrorn vollständig abgeschaltet ist, dann ist eine wie sonst bei Loadsensing-Ventilen vorliegende Volumensteuerung realisiert und die Drucksteuerung ist abgeschaltet. Im Übergangsbereich überlagern sich insoweit dann Druck- und Volumenstromsteuerung.Thereby; that is provided according to the characterizing part of claim 1 between the respective pilot valve and the control device at least one throttle point which is fluidly connected to a load-sensing terminal LF A and a load-indicating terminal LM A or a load-sensing connection LF B and a load-indicating terminal LM B , is reached in that a predefinable control pressure on the displaceable control device, preferably in the form of a control slide, precludes a compensation pressure derived from the actual load pressure, which keeps the control device in the fine control range until the load connected to the utility connections A, B moves. Then, the control device can move into a position as wide open as it allows the back pressure from the accelerating load, the leakage current is increasingly switched off. If the leakage current is completely switched off, a volume control that is the same as with load-sensing valves is realized and the pressure control is switched off. In the transition area, pressure and volume flow control are superimposed.

Bei einer bevorzugten Ausführungsform der erfindungsgemäßen Ventilvorrichtung weist dabei die Steuereinrichtung in Form eines Steuerschiebers fluidführende Verbindungskanäle auf, die die paarweise einander zuordenbaren Lastfühl- und Lastmeldeanschlüsse miteinander verbinden. Vorzugsweise und in besonders platzsparender Weise ist dabei einer der Verbindungskanäle als Mittenkanal ausgebildet, der an die eine der Drosselstellen angeschlossen ist, wobei die andere Drosselstelle in einen Ringkanal mündet, der koaxial zum Mittenkanal angeordnet von einer Innenausnehmung des Steuerschiebers und einer Einsatzhülse begrenzt ist, die von dem Mittenkanal durchgriffen ist.In a preferred embodiment of the valve device according to the invention in this case, the control device in the form of a control slide fluid-carrying connection channels, which connect the pairwise mutually assignable load sensing and load signaling connections. Preferably and in a particularly space-saving manner while one of the connecting channels is formed as a central channel which is connected to one of the throttle points, wherein the other throttle point opens into an annular channel which is coaxial with the central channel arranged by an inner recess of the spool and an insert sleeve is limited is penetrated by the center channel.

Bei einer weiteren bevorzugten Ausführungsform der erfindungsgemäßen Lösung ist der Steuereinrichtung eine Druckwaage vorgeschaltet, mit der die sog. Mengenabschneidung durch eine Loadsensing-Druckbegrenzung im Federraum der Druckwaage möglich ist. Bei den im Stand der Technik bekannten Lösungen mit nachgeschalteter Druckwaage ist diese Funktion der Mengenabschneidung nicht möglich oder nur über entsprechende Ventilzusatzkonstruktionen in aufwendiger Weise zu erhalten. Insbesondere ist die Regelfunktion der Druckwaage verbessert, indem ein relativ großer Abflußquerschnitt in den Rücklaufanschluß münden kann. Insoweit ist auch eine sog. Schwimmstellung für die Gesamtanordnung verbessert.In a further preferred embodiment of the solution according to the invention the control device is preceded by a pressure compensator, with which the so-called. Mengenabschneidung by a load sensing pressure limitation in the spring chamber of the pressure compensator is possible. In the known in the prior art solutions with downstream pressure compensator this function of Mengenabschneidung is not possible or to obtain only over appropriate additional valve constructions in a complex manner. In particular, the control function of the pressure balance is improved by a relatively large discharge cross-section can open into the return port. In that regard, a so-called. Floating position for the overall arrangement is improved.

Im folgenden wird die erfindungsgemäße hydraulische Ventilvorrichtung anhand eines Ausführungsbeispiels nach der Zeichnung näher erläutert. Dabei zeigen in prinzipieller und nicht maßstäblicher Darstellung die

Fig. 1
in der Art eines Längsschnittes eine stirnseitige Draufsicht auf die wesentlichen Komponenten der Ventilvorrichtung, jedoch ohne eingesetzte Pilotventile;
Fig. 2
in der Art eines Längsschnittes eine frei geschnittene Unteransicht des Gegenstandes nach der Fig.1;
Fig. 3
eine vergrößerte Darstellung des Ausschnittkreises X nach der Fig.2;
Fig. 4
eine vergrößerte Darstellung des Ausschnittkreises X nach der Fig.1.
In the following the hydraulic valve device according to the invention will be explained in more detail using an exemplary embodiment according to the drawing. This show in principle and not to scale representation of the
Fig. 1
in the manner of a longitudinal section, a frontal plan view of the essential components of the valve device, but without pilot valves used;
Fig. 2
in the manner of a longitudinal section, a free-cutting bottom view of the object according to the Fig.1 ;
Fig. 3
an enlarged view of the cutting circle X after the Fig.2 ;
Fig. 4
an enlarged view of the cutting circle X after the Fig.1 ,

Die Fig.1 zeigt eine als Ganzes mit 10 bezeichnete Fluidanschlußanordnung. Die dahi ngehende Fluidanschlußanordnung 10 weist einen Druckversorgungsanschluß P, einen Rücklaufanschluß, R, einen Loadsensinganschluß LS, zwei Steueranschlüsse PA' und PB' sowie zwei Nutzanschlüsse A,B auf. Die genannten Fluidanschlüsse in Blickrichtung auf die Fig.1 von links nach rechts gesehen PA', P, R, PB' und LS sowie die Nutzanschlüsse A und B sind in einem Steuergehäuse 12 untergebracht, wobei in Blickrichtung auf die Fig.1 gesehen das untere Ende des Steuergehäuses 12 mit einer an sich üblichen Druckwaage 14 versehen ist, auf deren konstruktiven Aufbau insoweit nicht mehr näher eingegangen wird. Jedoch ist die Druckwaage 14 den Anschlüssen PA', PB' vorgeschaltet und steuert die Steueranschlüsse PA', PB' nach Vorgabe des anliegenden LS-Signals insoweit an. Mit der dahingehend vorgeschalteten Druckwaage 14 ist die Funktion einer sog. Mengenabschneidung durch eine LS-Druckbegrenzung im sog. Federraum (nicht dargestellt) der Druckwaage erreicht, wobei eine Mengenabschneidung beispielsweise dann Sinn machen kann, wenn ein Lenkzylinder angeschlossen an die Nutzanschlüsse A,B am Anschlag steht und man zur Vermeidung von Überlastungen die Zuflußmenge insoweit "abschneiden" möchte.The Fig.1 shows a designated as a whole with 10 fluid port arrangement. The dahi next fluid connection assembly 10 has a pressure supply terminal P, a return port, R, a load-sensing terminal LS, two control terminals P A 'and P B ' and two Nutzanschlüsse A, B on. The said fluid connections in the direction of the Fig.1 Seen from left to right P A ', P, R, P B ' and LS and the Nutzanschlüsse A and B are housed in a control housing 12, wherein in the direction of the Fig.1 seen the lower end of the control housing 12 is provided with a conventional pressure compensator 14, on the structural design so far not discussed in more detail. However, the pressure compensator 14 is connected upstream of the terminals P A ', P B ' and controls the control terminals P A ', P B ' according to the specification of the applied LS signal in this respect. With the thus upstream pressure compensator 14, the function of a so-called. Mengenabschneidung is achieved by a LS-pressure limitation in the so-called spring chamber (not shown) of the pressure balance, with a Mengenabschneidung example, make sense if a steering cylinder connected to the Nutzanschlüsse A, B am Stop is and you want to cut off the inflow so far to avoid overloads.

Die als Ganzes mit 16 bezeichnete Steuereinrichtung als solche wird in bekannter und daher nicht mehr näher beschriebener Art und Weise von üblichen Pilotventilen angesteuert, die der einfacheren Darstellung wegen in der Fig.1 nur insoweit aufgezeigt sind, als ihre jeweils zuordenbaren Pilotanschlußgehäuse 18,20 angesprochen sind. Ausgangsseitig liefern die beiden Pilotventile jedenfalls für die Steuereinrichtung 18 zwei gegenläufig wirkende Steuerdrücke XA bzw. XB.The designated as a whole with 16 control device as such is controlled in a known and therefore no longer described manner of conventional pilot valves, the sake of simpler representation in the Fig.1 are shown only insofar as their respective assignable pilot terminal housing 18,20 are addressed. On the output side, the two pilot valves supply at least for the control device 18 two counteracting control pressures X A and X B, respectively.

Die genannte Steuereinrichtung 16 weist einen in Blickrichtung auf die Fig.1 gesehen horizontal verschiebbaren Steuerschieber 22 auf, der in der Fig.1 in seiner nicht ausgelenkten Mitten- oder Neutralstellung dargestellt ist. Die dahingehende Neutralstellung des Steuerschiebers 22 wird noch durch zwei Federspeicher unterstützt, die als Druckfedern 24 ausgebildet sind und in einem jeweils zuordenbaren Federraum 26,28 in den zuordenbaren Pilotanschlußgehäusen 18 bzw. 20 integriert sind. Der einfacheren Darstellung wegen wurde in Blickrichtung auf die Fig.1 gesehen für den linken Federraum 26 die Druckfeder 24 nicht eingezeichnet. Auch der dahingehende Aufbau ist bei solchen hydraulischen Ventilvorrichtungen bekannt, so dass insoweit an dieser Stelle hierauf nicht mehr näher eingegangen wird.The said control device 16 has a viewing direction on the Fig.1 Seen horizontally displaceable spool 22, which in the Fig.1 is shown in its undeflected middle or neutral position. The pertinent neutral position of the spool 22 is supported by two spring memory, which are designed as compression springs 24 and are integrated in a respective assignable spring chamber 26,28 in the assignable pilot port housings 18 and 20 respectively. The simpler representation because of looking in the direction of Fig.1 seen for the left spring chamber 26, the compression spring 24 is not shown. Also, the pertinent structure is known in such hydraulic valve devices, so that in this respect will not be discussed here at this point.

Die Steuereinrichtung 16 mit Steuerschieber 22 ist mit Lastfühlanschlüssen LFA und LFB sowie mit Lastmeldeanschlüssen LMA und LMB versehen, die paarweise miteinander fluidführend verschaltet sind. Und zwar ist, wie dies insbesondere die Unteransichtsdarstellung von Fig.1 nach der Fig.2 zeigt, der Lastfühlanschluß LFA mit dem Lastmeldeanschluß LMA verbunden und der Lastfühlanschluß LFB mit dem Lastmeldeanschluß LMB. Die genannten Fühlanschlüsse und Meldeanschlüsse, die letztere auch fachsprachlich mit Signalleitungen bezeichnet werden, sind in Form von radialen Querbohrungen in den Steuerschieber 22 eingebracht, und je nachdem, welche axiale Verfahrstellung der Steuerschieber 22 einnimmt, kommen die genannten Lastfühl- und Lastmeldeanschlüsse in fluidführende oder sperrende Verbindung mit den jeweils zuordenbaren Anschlüssen der Fluidanschlußanordnung 10. Insbesondere sind die Lastfühl- und Lastmeldeanschlüsse über fluidführende Verbindungskanäle innerhalb des Steuerschiebers 22 in zuordenbarer Weise in Verbindung miteinander. So ist einer der Verbindungskanäle als Mittenkanal 30 ausgebildet, der entlang der Mitten- oder Verschiebelängsachse des Steuerschiebers 22 diesen vollständig durchgreift und zu beiden Enden hin ins Freie ausmündet. Der dahingehende Mittenkanal 30 verbindet in fluidführender Weise den Lastfühlanschluß LFA mit dem Lastmeldeanschluß LMA. Koaxial zum Mittenkanal 30 angeordnet ist ferner ein Ringkanal 32 vorgesehen, dessen rechte konstruktive Ausgestaltung sich insbesondere aus den Darstellungen nach den Fig.3 und 4 ergibt. Der dahingehende Ringkanal 32 ist in eine Innenausnehmung 34 des Steuerschiebers 22 in der Art einer Radialbohrung eingebracht und nach innen hin von dem zylindrischen Außenumfang einer Einsatzhülse 36 begrenzt, die als Hohlzylinder ausgebildet einen Teil des Mittenkanals 30 führt. In Blickrichtung auf die Fig.2 gesehen stützt sich dabei die Einsatzhülse 36 mit ihrer linken Stirnseite an einem eingebrachten Radialabsatz 38 im Steuerschieber 22 ab.The control device 16 with control slide 22 is provided with load-sensing connections LF A and LF B and load-indicating connections LM A and LM B , which are interconnected in pairs carrying fluid. And that is, as in particular the bottom view representation of Fig.1 after Fig.2 shows, the load sensing terminal LF A connected to the load signaling terminal LM A and the load sensing terminal LF B to the load signaling terminal LM B. Said Fühlanschlüsse and signal ports, the latter are also referred to in technical language with signal lines are introduced in the form of radial transverse bores in the spool 22, and depending on which axial displacement position of the spool 22 occupies the said Load sensing and load signaling connections in fluid-conducting or blocking connection with the respectively assignable terminals of the fluid connection arrangement 10. In particular, the load sensing and load signaling connections via fluid-carrying connection channels within the spool 22 in a assignable manner in conjunction with each other. Thus, one of the connecting channels is designed as a central channel 30, which passes through the middle or longitudinal axis of the control spool 22 this completely and opens out at both ends to the outside. The pertinent center channel 30 connects the load-sensing connection LF A to the load-signaling connection LM A in a fluid-conducting manner. Coaxial with the central channel 30 is also an annular channel 32 is provided, the right structural design is particularly apparent from the illustrations according to the Figure 3 and 4 results. The pertinent annular channel 32 is inserted into an inner recess 34 of the spool 22 in the manner of a radial bore and bounded inwardly by the cylindrical outer periphery of an insert sleeve 36 which forms a part of the central channel 30 as a hollow cylinder. In the direction of the Fig.2 Seen here, the insert sleeve 36 is supported with its left end face on an introduced radial shoulder 38 in the spool 22 from.

Wie sich weiter aus den Fig. 1 und 2 ergibt, ist in Blickrichtung auf diese auf der linken Seite eine erste Drosselstelle da1 eingebracht, die über das linke stirnseitige Ende des Steuerschiebers 22 ein Stück weit in den Mittenkanal 30 eingreift. Als Gegenpart ist auf der gegenüberliegenden Seite eine zweite weitere Drosselstelle db1 eingebracht, deren Ausgestaltung insbesondere in den Fig.3 und 4 aufgezeigt ist. Die dahingehende Drosselstelle db1 ist in einer Verschlußschraube 40 integriert, die über eine Gewindestrecke 42 in eine stirnförmige Ausnehmung des Steuerschiebers 22 eingeschraubt ist. Außenumfangsseitig wird die dahingehende Verschlußschraube 40 von einer Art Ventilteller 44 übergriffen, die unter der Einwirkung der Druckfeder 24 in Blickrichtung auf die Fig.3 und 4 gesehen so lange in die Neutralstellung bewegt wird, bis der Ventilteller 44 mit seinem Außenrand in bündigem Abschluß mit der Stirnseite des Steuergehäuses 12 kommt, wie in den Fig.3 und 4 dargestellt.How to get out of the Fig. 1 and 2 results, in the direction of this on the left side a first throttle point da 1 introduced, which engages over the left frontal end of the spool 22 a piece in the center channel 30. As a counterpart, a second further restrictor db 1 is introduced on the opposite side, the configuration in particular in the Figure 3 and 4 is shown. The pertinent throttle point db 1 is integrated in a screw plug 40 which is screwed via a threaded section 42 in an end-shaped recess of the spool 22. On the outer circumference of the pertinent screw plug 40 is overlapped by a kind of valve plate 44, under the action of the compression spring 24 in the direction of the Figure 3 and 4 seen that way is moved long in the neutral position until the valve plate 44 comes flush with its outer edge to the end face of the control housing 12, as in the Figure 3 and 4 shown.

Bei der Ausschnittsdarstellung nach der Fig.3, die der Vergrößerung des Kreises X in Fig.2 entspricht, ist die Einsatzhülse 36 nach rechts so weit aus dem Steuerschieber 22 herausgeführt, so dass das freie stirnseitige Ende der Einsatzhülse 36 in Anlage kommt mit der Außenstirnwandfläche der Verschlußschraube 40. Unter Freilassen der Radial- oder Querbohrung als Lastmeldeanschluß LMA ist der sonstige Mittenkanal 30 in Richtung der Drosselstelle db1 fluiddicht mit einem Sperrstopfen 46 verschlossen. Dergestalt wird sichergestellt, dass der über den Mittenkanal 30 weitergegebene Lastfühldruck des Lastfühlanschlusses LFA nicht an die zweite Drosselstelle db1 gelangen kann. Wie die demgegenüber um 90° gedrehte Längsschnittdarstellung nach der Fig.4 zeigt, mündet aber die Drosselstelle db1 über den Anschlußkanal 48 in Form einer zylindrischen Verbreiterung im Steuerschieber 22 in den Ringkanal 32, so dass insoweit eine fluidführende Verbindung besteht zwischen dem Lastfühlanschluß LFB und dem Lastmeldeanschluß LMB. Diese Anschlüsse haben wiederum keine Verbindung mit der Drosselstelle da1 und die Darstellung nach der Fig.4 entspricht von der vergrößerten Kreisdarstellung X her der Darstellung nach der Fig.1. Zur Absperrung des Mittenkanals 30 gegenüber dem Anschlußkanal 48 dient ein weiterer fluiddichter Sperrstopfen 50, der zwischen dem Lastmeldeanschluß LMA und dem Anschlußkanal 48 innerhalb der Einsatzhülse 36 angeordnet ist.In the sectional view after the Figure 3 that increase the circle X in Fig.2 corresponds, the insert sleeve 36 to the right so far out of the spool 22, so that the free end face of the insert sleeve 36 comes into abutment with the Außenstirnwandfläche the screw plug 40. Under release of the radial or transverse bore as a load indicator LM A is the other center channel 30 in the direction of the throttle point db 1 fluid-tight with a stopper 46 closed. In this way, it is ensured that the load-sensing pressure of the load-sensing connection LF A transmitted via the center channel 30 can not reach the second throttle point db 1 . As opposed to the rotated by 90 ° longitudinal section after the Figure 4 shows, but opens the throttle point db 1 via the connecting channel 48 in the form of a cylindrical widening in the spool 22 in the annular channel 32, so far as a fluid-conducting connection between the load sensing terminal LF B and the load signaling terminal LM B. These connections in turn have no connection with the throttle point da 1 and the representation after the Figure 4 corresponds to the representation of the enlarged circle X ago forth Fig.1 , To shut off the central channel 30 relative to the connecting channel 48 is another fluid-tight locking plug 50, which is disposed between the load signaling terminal LM A and the connection channel 48 within the insert sleeve 36.

Wird nun in Blickrichtung auf die Fig.1 bis 4 gesehen der Steuerschieber 22 aus seiner Neutralstellung in eine linke Arbeitsstellung bewegt, kommt der Lastfühlanschluß LFA in Überdeckung mit dem Nutzanschluß A und dem dort anstehenden Druck und kann diesen dann über den Mittenkanal 30 und den Lastmeldeanschluß A an den Loadsensinganschluß LS, gleichfalls ausgebildet in der Art eines Ringkanals, weitermelden, da insoweit der Lastmeldeanschluß LMA in den LS-Ringkanal einfährt. Im umgekehrten Fall, also bei Bewegung des Steuerschiebers 22 von seiner Mittenstellung nach rechts, fährt der Lastfühlanschluß LFB in den zugeordneten Nutzanschluß B ein und der über den Ringkanal 32 erfühlte Druck gerät über den Lastmeldeanschluß B in den Ringkanal mit dem Loadsensi nganschluß LS. Die dahingehende Lastfühl- und Meldekette wird dann noch über den anstehenden Pilotventilgeberdruck, der an den Drosseln da1 bzw. db1 ansteht, überlagert. Wie insoweit die Fig.1 ausschließlich zeigt, kann dann noch zwischen jeweils eingesetztem Pilotventil und dem Federraum 26 bzw. 28 noch eine dritte und vierte Drosselstelle da2 bzw. db2 eingebracht sein. Soweit im Nachfolgenden von Drosselstelle die Rede ist, kann diese über eine konventionelle Drossel, aber auch über eine Blende realisiert sein.Now in view of the Fig.1 to 4 seen the spool 22 moves from its neutral position to a left working position, the load-sensing connection LF A comes into coincidence with the Nutzanschluß A and the pressure applied there and then this via the center channel 30 and the load-sensing connection A to the load-sensing terminal LS, also formed in the manner of an annular channel, continue to report, as far as the load-signaling connection LM A enters the LS-ring channel. In the opposite case, so when movement of the spool 22 from its center position to the right, the Lastfühlanschluß LF B enters the associated Nutzanschluß B and the sensed via the annular channel 32 pressure device via the load-sensing connection B in the annular channel with the nipples LS nipples LS. The pertinent load sensing and signaling chain is then superimposed on the upcoming pilot valve generator pressure, which is present at the throttles da 1 and db 1 , respectively. How so far the Fig.1 shows only then still between each inserted pilot valve and the spring chamber 26 and 28, a third and fourth throttle since da 2 or db 2 may be introduced. As far as throttling point is mentioned in the following, this can be realized via a conventional throttle, but also via a diaphragm.

Im folgenden wird in der Art einer Funktionsbeschreibung der spezifische Aufbau der erfindungsgemäßen hydraulischen Ventilvorrichtung noch näher erläutert.In the following, the specific structure of the hydraulic valve device according to the invention will be explained in more detail in the manner of a functional description.

In Neutralstellung gemäß der Darstellung nach der Fig.1 sind der Druckanschluß P sowie die Nutzanschlüsse A und B voneinander gesperrt, wobei man eine solche Ausführung auch mit geschlossener Mittenstellung bezeichnen kann. Ferner ist die Loadsensing-Leitung mit dem Rücklauf R verbunden, also entlastet. Zwei weitere Signalleitungen in Form des Lastmeldeanschlusses LMA und des Lastmeldeanschlusses LMB sind mit dem Loadsensinganschluß LS verbunden. In der gezeigten Neutralstellung sind beide Signalleitungen mit LS verbunden, in den Arbeitsstellungen immer diejenige, die auf den drucklosen Pilotdruckraum führt. Der Pilotdruckraum ist insoweit identisch mit der jeweiligen Federkammer in Form der Federräume 26,28. Wird in Neutralstellung ein Geberdruck (= Ansteuerdruck) XB, XA aktiviert, dann fließt kurzzeitig ein Steuerölstrom über die Drossel db2 sowie db1 und die Signalleitung LMB über den Lastfühlanschluß LFB nach dem Rücklaufanschluß R, bis der sich aufbauende Druck im zweiten Federraum 28 (XB-Seite) den Steuerschieber 22 in eine Zwischenstellung schiebt. Dann wird die dahingehende Signalleitung abgesperrt und es entsteht insoweit kein Steuerölverlust. Diese Zwischenstellung stellt den sog. Feinsteuerbereich dar. Die Verbindung vom Druckversorgungsanschluß P nach Nutzanschluß A ist jetzt nur wenig geöffnet. Die Signalleitung LMA ist wiederum durch die Drossel da1 vom Federraum 26 getrennt und der Federraum 26 vom Geberdruckanschluß XA (XB) durch die Drossel da2. Da im beschriebenen Zustand (XB ist aktiviert) der Geberanschluß XA drucklos ist, kann das unter Druck stehende Medium von der Last über den LS-Anschluß in die parallel angeschlossene Signalleitung drücken und von dort als Signalstrom über die Drosseln da1 und da2 in den drucklosen Anschluß XA abfließen. Der Lastdruck wird dabei im wesentlichen in zwei Stufen abgebaut, und zwar von "LS" nach "Druck"im Federraum 26 an der Drossel da1 und von dort nach "XB = To = 0" über die Drossel da2. Der entstehende Zwischendruck im Federraum 26 wirkt dem ansteuernden Geberdruck XB dann entgegen. Die Steuerschieberposition wird somit bestimmt durch die Differenz des Geberdruckes XB und dem Zwischendruck X'A in der Federkammer 26 am Anschluß XA.In neutral position as shown in the Fig.1 are the pressure port P and the Nutzanschlüsse A and B locked from each other, where you can designate such a version with closed center position. Furthermore, the load-sensing line is connected to the return R, so relieved. Two further signal lines in the form of the load-signaling connection LM A and the load-signaling connection LM B are connected to the load-sensing connection LS. In the neutral position shown, both signal lines are connected to LS, in the working positions always the one that leads to the unpressurized pilot pressure chamber. The pilot pressure chamber is so far identical to the respective spring chamber in the form of the spring chambers 26,28. If an encoder pressure (= control pressure) X B , X A is activated in neutral position, then a control oil flow flows briefly via the throttle db 2 and db 1 and the signal line LM B via the load-sensing connection LF B to the return connection R until the pressure builds up in the second Spring chamber 28 (X B side) pushes the spool 22 in an intermediate position. Then the pertinent signal line is shut off and there is so far no loss of control oil. This intermediate position represents the so-called fine control range. The connection from the pressure supply connection P to the utility connection A is now only slightly open. The signal line LM A is in turn separated by the throttle da 1 from the spring chamber 26 and the spring chamber 26 from the encoder pressure port X A (X B ) through the throttle da 2 . Since in the described state (X B is activated), the transmitter port X A is depressurized, the pressurized medium from the load through the LS port in the parallel connected signal line press and from there as a signal flow through the throttles da 1 and da 2 drain into the pressure-free connection X A. The load pressure is thereby reduced substantially in two stages, namely from "LS" to "pressure" in the spring chamber 26 at the throttle da 1 and from there to "X B = T o = 0" via the throttle da 2 . The resulting intermediate pressure in the spring chamber 26 counteracts the triggering encoder pressure X B then. The spool position is thus determined by the difference of the transmitter pressure X B and the intermediate pressure X ' A in the spring chamber 26 at the terminal X A.

In der Zwischenstellung des Feinsteuerbereichs fließt also einerseits ein Signalstrom in die Federkammer 26 bei XA und stellt proportional zum Lastdruck den Steuerschieber 22 in Richtung "Neutral" und andererseits fließt ein Verluststrom vom Arbeitsanschluß A zum Rücklaufanschluß R. Steht der Verbraucher A still, dann stellt sich im Anschluß A ein Druck ein, der bestimmt ist durch die Reihenschaltung der Verbindung von P nach A und der Verstelldrossel zum Rücklaufanschluß R. Damit ist ein Regelkreis entstanden, der vom Geberdruck XB angesteuert wird. Bei stillstehendem Verbraucher ist die sich einstellende künstliche Last um den Betrag der geregelten Druckdifferenz der vorgeschalteten Druckwaage 14 niedriger als der Pumpendruck am Druckversorgungsanschluß P. Die Pumpe wird deshalb, wie üblich, in Loadsensingsystemen angesteuert. Der künstlische Loadsensingdruck wirkt auch über die oben beschriebene Signalleitung und die angeschlossenen Drosseln da1 und db1 auf den Steuerschieber 22 zurück und der Steuerschieber 22 regelt durch seine Position und Reihenschaltung (Druckteilerschaltung) von einstellbarer Verbindung zwischen P und Nutzanschluß A sowie der Verstelldrossel nach Rücklaufanschluß R den Druck im Nutzanschluß A. Durch die Größe der jeweils eingesetzten Verstelldrossel, die vom Schieberhub abhängt, kann der Verluststrom um die Stabilität der Druckregelung konstruktiv eingestellt werden.In the intermediate position of Feinsteuerbereichs therefore flows on the one hand, a signal flow in the spring chamber 26 at X A and provides proportional to the load pressure the spool 22 in the direction of "neutral" and on the other hand flows a leakage current from the working port A to the return port R. If the consumer A is still, then in the terminal A, a pressure which is determined by the series connection of the connection from P to A and the variable throttle to the return port R. Thus, a control loop has arisen, which is controlled by the encoder pressure X B. When the load is stopped, the self-adjusting artificial load by the amount of the regulated pressure difference of the upstream pressure compensator 14 is lower than the pump pressure at the pressure supply port P. The pump is therefore, as usual, driven in load sensing systems. The artificial Loadsensing pressure also acts on the above-described signal line and the connected throttles da 1 and db 1 back to the spool 22 and the spool 22 controls by its position and series connection (pressure divider circuit) of adjustable connection between P and user port A and the variable throttle to return port R the Pressure in the user port A. Due to the size of each variable throttle used, which depends on the spool stroke, the leakage current can be adjusted constructively to the stability of the pressure control.

Wird der Geberdruck weiter erhöht, dann verstellt man den Schieber 22 aus seinem Fei nsteuerbereich heraus, der angedrosselte Druck steigt und die Last wird sich entsprechend bewegen. Bei weiterer Verstellung kann die Verstelldrossel zum Rücklaufanschluß R abgeschaltet werden, weil jetzt die Beschleunigungsphase beendet ist und die konstante Fahrt der Last erreicht ist. Der Geberdruck XB gibt jetzt vor, wieviel Volumenstrom dem Verbraucher zugeführt werden darf, damit der sich einstellende Staudruck in A nicht überschritten wird.If the encoder pressure is further increased, then one adjusts the slide 22 out of his Fei nsteuerbereich out, the throttled pressure increases and the load will move accordingly. Upon further adjustment, the variable throttle can be turned off to the return port R, because now the acceleration phase is completed and the constant travel of the load is reached. The encoder pressure X B now specifies how much volume flow must be supplied to the consumer so that the resulting dynamic pressure in A is not exceeded.

Mit der erfindungsgemäßen hydraulischen Ventilvorrichtung ist es also möglich, den Feinsteuerbereich des Steuerschiebers 22 auszunutzen, um den Druck mittels eines Verluststroms zu regeln. Dergestalt steht dem Ansteuerdruck am Steuerschieber 22 ein vom tatsächlichen Lastdruck abgeleiteter Kompensationsdruck entgegen und hält den Steuerschieber 22 so lange im Feinsteuerbereich, bis die Last angeschlossen an den Nutzanschlüssen A, B sich bewegt. Dergestalt kann man Verlustströme zunehmend abschalten und bei vollständiger Abschaltung ist eine Volumenstromsteuerung, wie sie bei LS-Ventilen üblich ist, realisiert. Die Drucksteuerung ist dann abgeschaltet, wobei im Übergangsbereich sich Druck und Volumensteuerung überlagern.With the hydraulic valve device according to the invention, it is thus possible to use the fine control range of the spool valve 22 to regulate the pressure by means of a leakage current. In this way, the control pressure on the spool valve 22 is counteracted by a compensation pressure derived from the actual load pressure and keeps the spool valve 22 in the fine control range until the load connected to the useful connections A, B moves. In this way, one can increasingly switch off leakage currents and at full shutdown is a flow control, as is common in LS valves, realized. The pressure control is then switched off, superimposed pressure and volume control in the transition area.

Claims (10)

  1. A hydraulic valve device with a fluid connector arrangement (10) containing at least
    - a pressure supply connector (P),
    - a return flow connector (R),
    - a load sensing connector (LS),
    - two control connectors (PA' and PB'), and
    - two utility connectors (A, B), and
    with a displaceable control means (16) for at least partially triggering connectors of the fluid connector arrangement (10), the control means (16) being triggerable by two pilot valves acting in opposite directions and being held spring-centered in its neutral position, characterised in that between the respective pilot valve and the control means there is at least one throttle point (da1, db1) which is connected to a load detecting connector (LFA) and to a load indicating connector (LMA) or a load detecting connector (LFB) as well as to a load indicating connector (LMB) to conduct fluid.
  2. The valve device according to Claim 1, characterised in that the control means (16) has a valve spool (22) with fluid-conducting connecting channels which connect to one another the load sensing and load indicating connectors (LFA, LMA; LFB, LMB) which can be assigned in pairs to one another.
  3. The valve device according to Claim 2, characterised in that one of the connecting channels is made as a central channel (30) which is connected to one of the throttle points (da1) and that the other throttle point (db1) discharges into an annular channel (32) which, arranged coaxially to the central channel (30), is bordered by an inner recess (34) of the valve spool (22) and an insert sleeve (36) through which the central channel (30) extends.
  4. The valve device according to Claim 3, characterised in that in the spring-centered neutral position of the valve spool (22) the two load detecting connectors (LFA, LFB) are outside the annular channels with the utility connectors (A, B) and the annular channel of the load sensing connector (LS) is located between the assignable load indicating connectors (LMA, LMB).
  5. The valve device according to Claim 3 or 4, characterised in that the throttle point (da1) is connected via the central channel (30) to the load detecting connector (LFA) and the loading indicating connector (LMA) and that the throttle point (db1) is connected via the annular channel (32) to the load detecting connector (LFB) and the load indicating connector (LMB) to conduct fluid.
  6. The valve device according to Claim 5, characterised in that the second throttle point (db1) is separated fluid-tight via a sealing part (46) from the central channel (30) with the load indicating connector (LMA) and discharges into a connecting channel (48) to which the annular channel (32) with the load indicating connector (LMB) is connected to conduct fluid.
  7. The valve device according to any of Claims 1 to 6, characterised in that the fluid connector arrangement (10) in the control housing (12) runs in the following sequence:
    - control connector (P'A)
    - utility connector (A)
    - return flow connector (R)
    - utility connector (B)
    - control connector (P'B) and
    - load sensing connector (LS).
  8. The valve device according to Claim 7, characterised in that the first throttle point (da1) adjacently to the control connector (PA') projects into the central channel (30) of the valve spool (22) and that the second throttle point (db1) adjacently to the load sensing connector (LS) discharges into the valve spool (22) with limitation of the connector channel (48).
  9. The valve device according to any of Claims 1 to 8, characterised in that for spring centering of the valve spool (22) two compression springs (24) are used which are located in spring chambers (26, 28) of the device and which in the direction of the connection sites to the pilot valves each have another throttle point (da2, db2).
  10. The valve device according to any of Claims 1 to 9, characterised in that a pressure compensator (14) which at least partially triggers the fluid connector arrangement (10) concomitantly is connected upstream of the control means (16) with its fluid connectors.
EP20100703625 2009-03-27 2010-02-09 Hydraulic valve device Not-in-force EP2411679B8 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910015384 DE102009015384B3 (en) 2009-03-27 2009-03-27 Hydraulic valve device
PCT/EP2010/000777 WO2010108570A1 (en) 2009-03-27 2010-02-09 Hydraulic valve device

Publications (3)

Publication Number Publication Date
EP2411679A1 EP2411679A1 (en) 2012-02-01
EP2411679B1 true EP2411679B1 (en) 2013-03-27
EP2411679B8 EP2411679B8 (en) 2013-05-15

Family

ID=42111507

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20100703625 Not-in-force EP2411679B8 (en) 2009-03-27 2010-02-09 Hydraulic valve device

Country Status (6)

Country Link
US (1) US20120006427A1 (en)
EP (1) EP2411679B8 (en)
JP (1) JP2012522188A (en)
DE (1) DE102009015384B3 (en)
DK (1) DK2411679T3 (en)
WO (1) WO2010108570A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016061427A (en) * 2014-09-22 2016-04-25 Ｋｙｂ株式会社 Selector valve
GB2532152B (en) * 2016-01-21 2017-04-19 Mooney Katherine Constructional element
US10281934B2 (en) * 2016-06-16 2019-05-07 Parker-Hannifin Corporation Hydraulic control valve with controlled flow and valve safety disable

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2050646B (en) * 1979-06-15 1983-04-13 Sperry Rand Corp Hydraulic actuator controls
US4343152A (en) * 1980-05-16 1982-08-10 Caterpillar Tractor Co. Load sensing porting arrangement
FR2546576B1 (en) * 1983-05-26 1987-09-25 Bennes Marrel SPEED LIMITING DEVICE FOR FITTING A HYDRAULIC CIRCUIT, PARTICULARLY EQUIPPED WITH THE DRAWER OF A HYDRAULIC DISTRIBUTOR
US4693272A (en) * 1984-02-13 1987-09-15 Husco International, Inc. Post pressure compensated unitary hydraulic valve
FR2562632B1 (en) * 1984-04-18 1986-12-12 Bennes Marrel PROPORTIONAL TYPE HYDRAULIC VALVE WITH INFORMATION ON THE HIGHEST PRESSURES IN THE CIRCUITS OF USE
US4738279A (en) * 1985-12-17 1988-04-19 Linde Aktiengesellschaft Multiway valves with load feedback
DE3644269A1 (en) * 1986-12-23 1988-07-07 Rexroth Mannesmann Gmbh 2-WAY VALVE
DE8801058U1 (en) * 1988-01-29 1988-03-10 Danfoss A/S, Nordborg, Dk
JPH07103882B2 (en) * 1989-03-22 1995-11-08 株式会社小松製作所 Hydraulic valve with pressure compensation
DE19542371A1 (en) * 1995-11-14 1997-05-15 Bosch Gmbh Robert Valve block with passages for fluid
US6148856A (en) * 1998-03-19 2000-11-21 Linde Aktiengesellschaft Control valve
DE102004033891A1 (en) * 2004-07-13 2006-02-16 Bosch Rexroth Aktiengesellschaft Hydraulic control arrangement
EP1619105B1 (en) * 2004-07-22 2007-09-05 Eaton S.r.l. Anti-saturation valve assembly for load sensing hydraulic system

Also Published As

Publication number Publication date
US20120006427A1 (en) 2012-01-12
DK2411679T3 (en) 2013-04-22
EP2411679A1 (en) 2012-02-01
WO2010108570A1 (en) 2010-09-30
EP2411679B8 (en) 2013-05-15
JP2012522188A (en) 2012-09-20
DE102009015384B3 (en) 2010-09-16

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