EP2220381A1 - Hydraulic valve device - Google Patents

Hydraulic valve device

Info

Publication number
EP2220381A1
EP2220381A1 EP08802278A EP08802278A EP2220381A1 EP 2220381 A1 EP2220381 A1 EP 2220381A1 EP 08802278 A EP08802278 A EP 08802278A EP 08802278 A EP08802278 A EP 08802278A EP 2220381 A1 EP2220381 A1 EP 2220381A1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
spool
connection
control
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP08802278A
Other languages
German (de)
French (fr)
Other versions
EP2220381B1 (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 Filtertechnik GmbH
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 Hydac Filtertechnik GmbH filed Critical Hydac Filtertechnik GmbH
Publication of EP2220381A1 publication Critical patent/EP2220381A1/en
Application granted granted Critical
Publication of EP2220381B1 publication Critical patent/EP2220381B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool 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
    • F15B13/0416—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
    • F15B13/0418—Load sensing elements sliding within a hollow main valve spool
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/08—Assemblies of units, each for the control of a single servomotor only
    • 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
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87193—Pilot-actuated
    • Y10T137/87209—Electric
    • 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
    • Y10T137/8593—Systems
    • Y10T137/877—With flow control means for branched passages

Definitions

  • the invention relates to a hydraulic valve device, in particular LS flow control valve, having a fluid connection arrangement, comprising at least one pressure supply connection (P), a return connection (R), a section load-sensing connection (LS), two control connections (P'A) and (P '). B), two Nutzan say (A, B) and at least one movable control device for at least partially driving terminals of the fluid connection arrangement.
  • a hydraulic valve device in particular LS flow control valve, having a fluid connection arrangement, comprising at least one pressure supply connection (P), a return connection (R), a section load-sensing connection (LS), two control connections (P'A) and (P '). B), two Nutzan say (A, B) and at least one movable control device for at least partially driving terminals of the fluid connection arrangement.
  • LUDV valve arrangement in which a control valve forms a Zulaufmeßblende, which is followed by an individual pressure compensator.
  • a hydraulic consumer is actuated, which is connected to two consumer terminals of the control arrangement.
  • two pressure chambers of the consumer can be connected to each other and to a pressure medium source.
  • this connection of the two consumer connections via a pressure medium flow path, in which a check valve is arranged.
  • the well-known LUDV control represents a special case of a load sensing control in which the highest load pressure of the hydraulic consumers is reported to an adjustment pump and regulated so that in the pump line is applied to the pump pressure by a certain pressure difference .DELTA.P above the load pressure.
  • the individual pressure compensators are arranged downstream of the metering orifices and throttle the fluid flow between the metering orifice and the load to such an extent that the pressure after all metering orifices is equal to, or slightly above, the highest load pressure.
  • the greatest weakness of these hydraulic LS systems lies in their sensitivity to system oscillations in the load sensing control loop, among other things due to load changes at the respective consumer.
  • a directional valve is known as a hydraulic valve device for controlling the pressure and the flow of hydraulic oil from or to working ports of at least one fluid consumer, in which the pressure and the flow rate can be actuated by means of at least one drive a slide bore slidable control slide and thus operatively connected ring channels is controllable, wherein in a so-called.
  • Symmetry center of the valve assembly on a symmetry axis a tank connection ring channel (R) is arranged and on both sides more annular channels are arranged symmetrically.
  • an A-ring channel assigned to one working port, a first pump-pressure annular channel, a first load-sensing Ring channel and a first Endraum-ring channel and on the other side of the axis of symmetry associated with the other working port associated B-ring channel, a second pump pressure ring channel, a second load-sensing ring channel and a second Endraum-ring channel.
  • the first load-sensing ring channel is connected to the second load-sensing ring channel via a load-sensing connection line.
  • the invention has the object to further improve the known valve solutions to the effect that system vibrations in the load-sensing loop can be better controlled and that a constant current control for each connected hydraulic consumer is possible.
  • This object is achieved by a hydraulic valve device with the features of claim 1 in its entirety.
  • the LS-pressure (load pressure) then represents the reference variable for the upstream pressure compensator and can so far smooth the pressure oscillations, even before the pressure is forwarded to the subsequent spool of the respective control device, which then depending on its respective slide or piston position ensures the constant supply for each connected hydraulic consumer.
  • the pressure compensator is integrated within the spool, wherein both the pressure compensator and the spool are guided in a relative movement to each other within a valve housing longitudinally displaceable.
  • the pertinent coaxial arrangement of spool and pressure compensator is particularly space-saving and leads to small constructive valve housings, the pertinent arrangement is still particularly reliable.
  • both the pressure balance and the spool are spring-centered in a starting position, the pressure compensator of a LS-pressure can be controlled, which simultaneously led to a connection side of the spool is, in turn, by the control pressure of a pilot valve can be controlled and further wherein a tapped between spool and pressure compensator control port pressure acting in opposite directions to the LS-pressure acting on the pressure compensator.
  • Fig.2 shows the practical implementation of the circuit diagram of Figure 1 in a valve product, which is partially reproduced with its essential components once in longitudinal section and once in view.
  • the hydraulic valve device has a fluid connection arrangement denoted as a whole by 10, comprising a pressure supply connection P, a return connection R, a section load-sensing connection LS with LS m a ⁇ / two control connections P'A, P'B / two utility connections A. , B and two connected to each other independently pendent hydraulic motors 12 as consumers, which are connected to a common tank connection To.
  • the hydraulic valve device further comprises two as a whole designated 14 control means for at least partially driving connections of the Fluidanschluß- arrangement 10.
  • the respective control device 14 has each utility port A, B associated with a spool 16, which is preceded by a pressure compensator 18.
  • Spool 16 and pressure compensator 18 are constructed in the manner of proportional valves, wherein the respective spool 16 is provided with a kind throttle or aperture 20. Both the pressure balance 18 and the spool 16 are held according to the illustration of Fig.1 spring-centered in a starting position, the spool 16 for this purpose has a compression spring 22 and the pressure compensator 18, a further compression spring 24th
  • the respective pressure compensator 18 can be controlled by a LS pressure, which is designated in FIG. 1 with LSA or LSB.
  • the pertinent LS pressure LSA, LSB is also performed on a connection side 26 of the spool 16 at the same time.
  • the respective spool 16 is also against the action of the compression spring 22 of a control pressure XA, XB a known pilot valve PA, PB controlled, with a rank used between spool 16 and pressure balance 1 8 control port pressure P ⁇ , and P'B opposite to the LS-pressure LSA, LSB activates the pressure scale 1 8 activates.
  • the upcoming at the entrance of the pressure compensator 18 LS-pressure should be denoted by LSAI and LS ß i.
  • connection side 28 of the spool 1 6 is connected to a return port R and the LS-pressure LSA and LS B is controlled by a changeover valve 30 which is connected via a check valve 32 to LS max , wherein the check valve 32 in the direction of LS ma ⁇ opens.
  • the pilot valves PA, PB are connected to a control pressure PST as a supply source and further to the tank terminal TQ.
  • the presented in Figure 1 in the manner of a hydraulic circuit diagram hydraulic valve device is now shown there according to the longitudinal sectional view of Figure 2 as a constructive valve solution.
  • the valve device has a valve housing designated as a whole by 34, wherein the valve housing is realized in the manner of a modular construction concept.
  • pilot valves PA, PB are connected with their terminal housing parts 36 to the center housing 38, seen in the direction of the Fig.2 in the upper part of the center housing 38
  • Nutzan- the conclusions A, B are connected in the type of Einschraubpatronen and in the lower part of the center housing 38, this is penetrated by a through-passage 40 in which a total of the pump pressure P is present, which is connected via connecting lines 42 to a central channel bore 44 into which the two control devices 14 are inserted.
  • the central channel bore 44 extends transversely to a central longitudinal axis of the overall valve housing 34 and along this longitudinal axis not shown in detail is seen in the direction of the Fig.2 below the central channel bore 44 of the return port R, via a further connection line 46th opens into the center channel 44.
  • the center channel 44 is preferably formed in the form of a bore via connecting lines 48 fluidly connected to the Nutzan say A, B connected.
  • the designated in Fig.l with 32 check valve is also integrated in the valve housing 34, but this is not shown in detail for reasons of simplification.
  • the LS-ring channels LSA and LSB are connected to the shuttle valve 30, which separates the two pressures from each other.
  • the shuttle valve 30 is preferably designed as a circular plug-in part and is mounted on the so-called. Flange side (not shown) of the disc-like valve body 34.
  • the output terminal of the shuttle valve 30 leads via a pressure channel to the check valve 32, which seals against higher pressure in the LS message channel (LS max ). If the load pressure LSA or LSB is higher than the pressure in the signaling channel, then this pressure is reported on via the check valve 32 in the control block and from there on to a system pressure control, not shown, for the entire valve system.
  • the two control valves 16 are constructed identically and take in coaxial arrangement an internal, the valve diaphragm upstream pressure compensator 18, which are also identical in construction.
  • the spool 16 are held by fixed stops housing and their respective working spring (compression spring 22) in position.
  • the working spring (compression spring 22) is supported on the one hand against the housing 34 of the valve and on the other hand against a screw plug 50 which is screwed firmly to the spool 16. In the pertinent initial or neutral position of the respective spool 16 separates the working port A or B from the pump port P.
  • a variable valve orifice is formed in the form of first radial apertures 52 within the hollow slide valve. arrangement, consisting of spool 16 and pressure compensator 18, in which respect a sealing web P to A and P to B within the valve housing 34 is formed. Also, the internal pressure compensator 18 is continuously connected via second radial openings 54 in the spool 16 with the pump channel P. The spring chamber with the further compression spring 24 of the pressure compensator 18 is connected via third radial openings 56 in the control slide 16 constantly with the respective assignable LSA or LSB ring channel. In the neutral position, the third radial openings 56 of the spool 16 are additionally connected to the spring chamber with the compression spring 22 of the spool 16 pressure leading.
  • the spool 16 may be provided with fourth radial openings 57, the edge lying to the middle of the valve lying on the same axial length as the first openings (control edge 52). These pertinent fourth openings 57 have, unlike the first three breakthroughs, no corresponding passages in the control piston of the pressure compensator 18.
  • the correct orientation of corresponding openings with passages is ensured by an anti-rotation lock 58 in the form of a detent ball, which provides a radial lock so far between spool 16th and the control piston of the pressure compensator 18th
  • the control spring 24 presses the control piston of the pressure compensator 18 against the blind end of the control spool 16.
  • the pressure compensator piston is also designed as a hollow piston and has a second radial passage 60, which connects to the aperture 54 as a so-called P breakthrough in the spool 16 at the stroke against the pressure compensator spring 24 closes (control edge of the pressure compensator 18).
  • a first radial passage 62 is permanently connected to a valve orifice in the form of the first opening 52 in the spool 16.
  • the spring chamber of the pressure compensator 18 is through the third radial opening 56 connected to the respectively assignable third passage 64 of the spool 16 and also with longitudinal grooves 66 on the lateral surface of the control piston of the pressure compensator 18.
  • the pertinent longitudinal grooves 66 of which only one is shown by dashed lines in FIG. Channel to the control edge of the control piston and are - viewed at the periphery - between the radial openings and passages.
  • the respective longitudinal groove 66 has permanent connection with the fourth radial opening 57 in the spool 16.
  • the pertinent Leksnut für provides the LS reporting port from the working port in the spring chamber with the compression spring 24 of the pressure compensator 18.
  • the connection point 57 as shown in FIG .1 the branch point LSB and the breakthrough 56 forms on the one input control side of the pressure compensator 18, the signaling port LSBI, whereas the above-described LS-pressure LSB represents the sensing connection.
  • a pilot pressure is given via the pilot valves PA or PB, with a pilot valve serving as an electrohydraulic pressure reducing valve with central supply from a control oil circuit Pst, then the control slide 16 shifts against the spring force of the compression spring 22 in the direction of the R channel (compare FIG .2).
  • the valve diaphragm then begins to open an opening cross-section between pressure compensator 18 and respectively assignable working port A or B. Accordingly, the PV or PV pressure breaks down because one, because volume drains off.
  • the control spring 24 can then push the control piston in the direction of the opening control edge and oil flows from the pump port P until again a back pressure in front of the valve diaphragm arises, which is in equilibrium with the control spring and the reported load pressure.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Safety Valves (AREA)
  • Servomotors (AREA)

Abstract

The invention relates to a hydraulic valve device, especially an LS current regulating valve, comprising a fluid connection arrangement (10) containing a plurality of useful connections and supply connections, and at least one mobile control device (14) for at least partially controlling the connections of the fluid connection arrangement (10). As the respective control device (14) associated with a useful connection (A,b) comprises a control slide (16) upstream of which a pressure balance (18) is mounted in the fluid direction towards each useful connection (A, B), any system vibrations occurring in the load sensing regulating circuit can be better controlled and the respectively connected hydraulic consumer can be subjected to a constant current regulation.

Description

Hydraulische Ventilvorrichtung Hydraulic valve device
Die Erfindung betrifft eine hydraulische Ventilvorrichtung, insbesondere LS- Stromregelventil, mit einer Fluidanschlußanordnung, beinhaltend mindestens einen Druckversorgungsanschluß (P), - einen Rücklaufanschluß (R), einen Sektions-Loadsensinganschluß (LS), zwei Steueranschlüsse (P'A) und (P'B), zwei Nutzanschlüsse (A,B) und mindestens eine verfahrbare Steuereinrichtung zum zumindest teilwei- sen Ansteuern von Anschlüssen der Fluidanschlußanordnung.The invention relates to a hydraulic valve device, in particular LS flow control valve, having a fluid connection arrangement, comprising at least one pressure supply connection (P), a return connection (R), a section load-sensing connection (LS), two control connections (P'A) and (P '). B), two Nutzanschlüsse (A, B) and at least one movable control device for at least partially driving terminals of the fluid connection arrangement.
Durch die DE 10 2005 033 222 A1 ist eine sog. LUDV-Ventilanordnung bekannt, bei der ein Regelventil eine Zulaufmeßblende ausbildet, der eine Individualdruckwaage nachgeschaltet ist. Mittels der LUDV- Ventilanordnung wird ein hydraulischer Verbraucher angesteuert, der an zwei Verbraucheranschlüsse der Steueranordnung angeschlossen ist. Zum Einstellen eines Eilganges können zwei Druckräume des Verbrauchers miteinander und mit einer Druckmittelquelle verbunden werden. Um ein Absacken des Verbraucherdruckes zu verhindern, erfolgt diese Verbindung der beiden Verbraucheranschlüsse über einen Druckmittelströmungspfad, in dem ein Rückschlagventil angeordnet ist. Über das Wegeventil ist dabei nur die Verbindung zu einem der Verbraucheranschlüsse aufgesteuert; die Ver- bindung des anderen Verbraucheranschlusses mit der Druckmittelquelle und/oder dem erstgenannten Verbraucheranschluß ist im Eilgang nur über den Druckmittelströmungspfad und das geöffnete Rückschlagventil möglich. Mit der bekannten Lösung ist eine unbeabsichtigte Bewegung eines hydraulischen Verbrauchers in einer Eilgangstellung der Ventilanordnung verhindert. Die bekannte LUDV-Steuerung stellt einen Sonderfall einer Loadsensing-Steuerung dar, bei der der höchste Lastdruck der hydraulischen Verbraucher an eine Einstellpumpe gemeldet und diese so geregelt wird, dass in der Pumpenleitung ein um eine bestimmte Druckdifferenz ΔP über dem Lastdruck liegender Pumpendruck anliegt. Bei der bekannten LUDV- Steuerung sind die Individualdruckwaagen stromabwärts der Zumeßblen- den angeordnet und drosseln jeweils zwischen derZumeßblende und der Last den Fluidstrom so stark an, dass der Druck nach allen Zumeßblenden gleich, vorzugsweise gleich dem höchsten Lastdruck ist oder leicht über diesem liegt. Die größte Schwäche dahingehender hydraulischer LS- Systeme liegt in deren Empfindlichkeit gegen Systemschwingungen im Loadsensing-Regelkreis, unter anderem bedingt durch Lastwechsel am jeweiligen Verbraucher.From DE 10 2005 033 222 A1 a so-called. LUDV valve arrangement is known, in which a control valve forms a Zulaufmeßblende, which is followed by an individual pressure compensator. By means of the LUDV valve arrangement, a hydraulic consumer is actuated, which is connected to two consumer terminals of the control arrangement. To set a rapid traverse two pressure chambers of the consumer can be connected to each other and to a pressure medium source. In order to prevent sagging of the consumer pressure, this connection of the two consumer connections via a pressure medium flow path, in which a check valve is arranged. About the directional control valve only the connection to one of the consumer connections is opened; the Ver- Bonding of the other consumer connection with the pressure medium source and / or the first-mentioned consumer connection is possible in rapid traverse only via the pressure medium flow path and the open check valve. With the known solution, an unintentional movement of a hydraulic consumer in a rapid traverse position of the valve arrangement is prevented. The well-known LUDV control represents a special case of a load sensing control in which the highest load pressure of the hydraulic consumers is reported to an adjustment pump and regulated so that in the pump line is applied to the pump pressure by a certain pressure difference .DELTA.P above the load pressure. In the known LUDV control, the individual pressure compensators are arranged downstream of the metering orifices and throttle the fluid flow between the metering orifice and the load to such an extent that the pressure after all metering orifices is equal to, or slightly above, the highest load pressure. The greatest weakness of these hydraulic LS systems lies in their sensitivity to system oscillations in the load sensing control loop, among other things due to load changes at the respective consumer.
Durch die EP 1 370 773 B1 ist als hydraulische Ventilvorrichtung ein Wegeventil bekannt zur Steuerung des Druckes und des Flusses von Hydraulik- öl von bzw. zu Arbeitsanschlüssen mindestens eines Fluidverbrauchers, bei dem der Druck und der Durchfluß mittels eines durch mindestens einen Antrieb betätigbaren, in einer Schieberbohrung verschiebbaren Steuer- Schiebers und damit in Wirkverbindung stehenden Ringkanälen steuerbar ist, wobei in einem sog. Symmetriemittelpunkt der Ventilanordnung auf einer Symmetrieachse ein Tankanschluß-Ringkanal (R) angeordnet ist und beidseits sind weitere Ringkanäle symmetrisch angeordnet. Ferner ist für die Realisierung einer hydraulischen Pumpenansteuerung auf der einen Seite der genannten Symmetrieachse ein dem einen Arbeitsanschluß zugeordneter A-Ringkanal, ein erster Pumpendruck-Ringkanal, ein erster Load-Sensing- Ringkanal und ein erster Endraum-Ringkanal und auf der anderen Seite der Symmetrieachse ein dem anderen Arbeitsanschluß zugeordneter B- Ringkanal, ein zweiter Pumpendruck-Ringkanal, ein zweiter Load-Sensing- Ringkanal und ein zweiter Endraum-Ringkanal zugeordnet. Ferner ist der erste Load-Sensing-Ringkanal mit dem zweiten Load-Sensing-Ringkanal über eine Load-Sensing-Verbindungsleitung verbunden. Mit der bekannten Ventillösung ist eine Art Mengenteiler für die angeschlossenen Verbraucher erreicht, wobei bei dahingehenden Mengenteilerventilen die Druckwaagen nicht den Druckabfall über die Ventilblende regeln, sondern den höchsten Lastdruck des Systems übernehmen. Schwankende Druckverluste in der Speiseleitung stören dann direkt die verfügbare Druckdifferenz an der Reglerblende und verhindern dergestalt eine konstante Strom regelung.From EP 1 370 773 B1, a directional valve is known as a hydraulic valve device for controlling the pressure and the flow of hydraulic oil from or to working ports of at least one fluid consumer, in which the pressure and the flow rate can be actuated by means of at least one drive a slide bore slidable control slide and thus operatively connected ring channels is controllable, wherein in a so-called. Symmetry center of the valve assembly on a symmetry axis a tank connection ring channel (R) is arranged and on both sides more annular channels are arranged symmetrically. Furthermore, for the realization of a hydraulic pump control on one side of said symmetry axis, an A-ring channel assigned to one working port, a first pump-pressure annular channel, a first load-sensing Ring channel and a first Endraum-ring channel and on the other side of the axis of symmetry associated with the other working port associated B-ring channel, a second pump pressure ring channel, a second load-sensing ring channel and a second Endraum-ring channel. Furthermore, the first load-sensing ring channel is connected to the second load-sensing ring channel via a load-sensing connection line. With the known valve solution, a kind of flow divider for the connected consumers is achieved, with the appropriate flow divider valves, the pressure compensators do not regulate the pressure drop across the valve orifice, but take over the highest load pressure of the system. Fluctuating pressure losses in the supply line then directly interfere with the available pressure difference at the regulator panel and thus prevent a constant current regulation.
Ausgehend von diesem Stand der Technik liegt der Erfindung die Aufgabe zugrunde, die bekannten Ventillösungen dahingehend weiter zu verbessern, dass Systemschwingungen im Load-Sensing-Regelkreis besser beherrschbar sind und dass eine konstante Stromregelung für den jeweils angeschlossenen hydraulischen Verbraucher möglich ist. Eine dahingehende Aufgabe löst eine hydraulische Ventilvorrichtung mit den Merkmalen des Patentanspruches 1 in seiner Gesamtheit.Based on this prior art, the invention has the object to further improve the known valve solutions to the effect that system vibrations in the load-sensing loop can be better controlled and that a constant current control for each connected hydraulic consumer is possible. This object is achieved by a hydraulic valve device with the features of claim 1 in its entirety.
Dadurch, dass gemäß dem kennzeichnenden Teil des Patentanspruches 1 vorgesehen ist, dass die jeweilige Steuereinrichtung einem jeden Nutzanschluß A,B zugeordnet einen Steuerschieber aufweist, dem eine Druckwaa- ge in Fluidrichtung zum jeweiligen Nutzanschluß A,B vorgeschaltet ist, ist das hydraulische LS-System gegen Systemschwingungen weniger empfindlich. Aufgrund der vorgeschalteten Druckwaage kann diese einen entscheidenden Einfluß auf die Systemstabilität nehmen. Druckschwingungen werden häufig durch mechanische Schwingungen von nachgiebigen Strukturen bei den jeweils angeschlossenen hydraulischen Verbrauchern (Kranarme) erzeugt und dann durch den Lastfühlkreis (LS) auf die Druckwaage übertra- gen. Der LS-Druck (Lastmeldedruck) stellt dann insoweit die Führungsgröße für die vorgeschaltete Druckwaage dar und kann insoweit die Druckschwingungen glätten, noch bevor der Druck an den nachfolgenden Steuerschieber der jeweiligen Steuereinrichtung weitergeleitet wird, der dann in Abhängigkeit seiner jeweiligen Schieber- oder Kolbenposition die Konstantversorgung für den jeweils angeschlossenen hydraulischen Verbraucher sicherstellt.Characterized in that is provided according to the characterizing part of claim 1, that the respective control means each Nutzanschluß A, B associated with a spool, which is a Druckwaa- ge in the fluid direction to the respective Nutzanschluß A, B upstream, is the hydraulic LS system Less sensitive to system vibrations. Due to the upstream pressure compensator, this can have a decisive influence on the system stability. Pressure oscillations are often generated by mechanical vibrations of resilient structures in the respective connected hydraulic consumers (crane arms) and then transmitted to the pressure balance by the load-sensing circuit (LS). The LS-pressure (load pressure) then represents the reference variable for the upstream pressure compensator and can so far smooth the pressure oscillations, even before the pressure is forwarded to the subsequent spool of the respective control device, which then depending on its respective slide or piston position ensures the constant supply for each connected hydraulic consumer.
Neben der genannten Systemglättung wird durch die Fluidfolge von Druckwaage mit nachgeordnetem Steuerschieber sichergestellt, dass unabhängig von der Druckdifferenz an der Steuereinrichtung für den jeweiligen Verbraucher ein konstanter Nutzvolumenstrom zur Verfügung steht, so dass der Gesamtdurchfluß unabhängig von wechselnden Lastdrücken am Verbraucher konstant bleibt und insoweit einen funktionssicheren Betrieb für den jeweils angeschlossenen hydraulischen Verbraucher gewährleistet.In addition to the aforementioned system smoothing is ensured by the fluid sequence of pressure compensator with downstream spool that regardless of the pressure difference across the control device for the respective consumer a constant useful flow is available, so that the total flow remains constant regardless of changing load pressures on the consumer and so far a functionally reliable Operation guaranteed for each connected hydraulic consumer.
Bei einer bevorzugten Ausführungsform der erfindungsgemäßen Ventilvorrichtung ist die Druckwaage innerhalb des Steuerschiebers integriert, wobei sowohl die Druckwaage als auch der Steuerschieber in einer Relativbewe- gung zueinander innerhalb eines Ventilgehäuses längsverschiebbar geführt sind. Die dahingehende Koaxialanordnung von Steuerschieber und Druckwaage ist besonders platzsparend und führt zu klein aufbauenden Ventilgehäusen, wobei die dahingehende Anordnung dennoch besonders funktionssicher ist.In a preferred embodiment of the valve device according to the invention, the pressure compensator is integrated within the spool, wherein both the pressure compensator and the spool are guided in a relative movement to each other within a valve housing longitudinally displaceable. The pertinent coaxial arrangement of spool and pressure compensator is particularly space-saving and leads to small constructive valve housings, the pertinent arrangement is still particularly reliable.
Als besonders funktionssicher hat es sich ferner erwiesen, wenn bei einer bevorzugten Ausführungsform der erfindungsgemäßen Ventilvorrichtung sowohl die Druckwaage als auch der Steuerschieber federzentriert in einer Ausgangsstellung gehalten sind, wobei die Druckwaage von einem LS- Druck ansteuerbar ist, der gleichzeitig auf eine Anschlußseite des Steuerschiebers geführt ist, der wiederum von dem Steuerdruck eines Pilotventils ansteuerbar ist und wobei ferner ein zwischen Steuerschieber und Druckwaage abgegriffener Steueranschlußdruck gegenläufig zum LS-Druck wirkend die Druckwaage ansteuert.As a particularly reliable function, it has also proven, when in a preferred embodiment of the valve device according to the invention, both the pressure balance and the spool are spring-centered in a starting position, the pressure compensator of a LS-pressure can be controlled, which simultaneously led to a connection side of the spool is, in turn, by the control pressure of a pilot valve can be controlled and further wherein a tapped between spool and pressure compensator control port pressure acting in opposite directions to the LS-pressure acting on the pressure compensator.
Weitere vorteilhafte Ausführungsformen der erfindungsgemäßen Ventilvorrichtung sind Gegenstand der sonstigen Unteransprüche.Further advantageous embodiments of the valve device according to the invention are the subject of the other dependent claims.
Im folgenden wird die erfindungsgemäße Lösung anhand eines Ausführungsbeispiels näher erläutert. Dabei zeigen in prinzipieller und nicht maß- stäblicher Darstellung dieIn the following, the solution according to the invention is explained in more detail using an exemplary embodiment. In a schematic and not to scale representation, the
Fig.1 in der Art eines hydraulischen Schaltplans den prinzipiellenFig.1 in the manner of a hydraulic circuit diagram the principal
Aufbau der hydraulischen Ventilvorrichtung in Form eines LS- Stromregelventils;Structure of the hydraulic valve device in the form of a LS flow control valve;
Fig.2 die praktische Umsetzung des Schaltplans nach der Fig.1 in einem Ventilprodukt, das teilweise mit seinen wesentlichen Komponenten einmal im Längsschnitt und einmal in Ansicht wiedergegeben ist;Fig.2 shows the practical implementation of the circuit diagram of Figure 1 in a valve product, which is partially reproduced with its essential components once in longitudinal section and once in view.
Fig.3 eine vergrößerte Darstellung einer geschnitten dargestellten3 shows an enlarged view of a section shown
Längsansicht einer in Blickrichtung auf die Fig.2 gesehen rechten Steuereinrichtung mit Druckwaage und Steuerschieber.Longitudinal view of a viewed in the direction of FIG. 2 right control device with pressure balance and spool.
Die hydraulische Ventilvorrichtung nach der Fig.1 weist eine als Ganzes mit 10 bezeichnete Fluidanschlußanordnung auf, beinhaltend einen Druckversorgungsanschluß P, einen Rücklaufanschluß R, einen Sektions- Loadsensinganschluß LS mit LSmaχ/ zwei Steueranschlüsse P'A, P'B/ zwei Nutzanschlüsse A,B sowie zwei daran angeschlossene voneinander unab- hängige Hydromotoren 12 als Verbraucher, die an einen gemeinsamen Tankanschluß To angeschlossen sind. Die hydraulische Ventilvorrichtung weist ferner zwei als Ganzes mit 14 bezeichnete Steuereinrichtungen auf zum zumindest teilweise Ansteuern von Anschlüssen der Fluidanschluß- anordnung 10. Die jeweilige Steuereinrichtung 14 weist jedem Nutzanschluß A,B zugeordnet einen Steuerschieber 16 auf, dem eine Druckwaage 18 vorgeschaltet ist. Steuerschieber 16 sowie Druckwaage 18 sind in der Art von Proportionalventilen aufgebaut, wobei der jeweilige Steuerschieber 16 mit einer Art Drossel oder Blende 20 versehen ist. Sowohl die Druck- waage 18 als auch der Steuerschieber 16 sind gemäß der Darstellung nach der Fig.1 federzentriert in einer Ausgangsstellung gehalten, wobei der Steuerschieber 16 hierfür eine Druckfeder 22 aufweist und die Druckwaage 18 eine weitere Druckfeder 24.The hydraulic valve device according to FIG. 1 has a fluid connection arrangement denoted as a whole by 10, comprising a pressure supply connection P, a return connection R, a section load-sensing connection LS with LS m aχ / two control connections P'A, P'B / two utility connections A. , B and two connected to each other independently pendent hydraulic motors 12 as consumers, which are connected to a common tank connection To. The hydraulic valve device further comprises two as a whole designated 14 control means for at least partially driving connections of the Fluidanschluß- arrangement 10. The respective control device 14 has each utility port A, B associated with a spool 16, which is preceded by a pressure compensator 18. Spool 16 and pressure compensator 18 are constructed in the manner of proportional valves, wherein the respective spool 16 is provided with a kind throttle or aperture 20. Both the pressure balance 18 and the spool 16 are held according to the illustration of Fig.1 spring-centered in a starting position, the spool 16 for this purpose has a compression spring 22 and the pressure compensator 18, a further compression spring 24th
Die jeweilige Druckwaage 18 ist von einem LS-Druck ansteuerbar, der in der Fig. 1 mit LSA bzw. LSB bezeichnet ist. Der dahingehende LS-Druck LSA, LSB ist gleichzeitig auch auf eine Anschlußseite 26 des Steuerschiebers 16 geführt. Der jeweilige Steuerschieber 16 ist ferner entgegen der Wirkung der Druckfeder 22 von einem Steuerdruck XA, XB eines an sich bekannten Pilotventils PA, PB ansteuerbar, wobei ein zwischen Steuerschieber 16 und Druckwaage 1 8 abgegriffener Steueranschlußdruck PΑ, und P'B gegenläufig zum LS-Druck LSA, LSB wirkend die Druckwaage 1 8 ansteuert. Der direkt am Eingang der Druckwaage 18 anstehende LS-Druck soll dabei mit LSAI bezeichnet sein sowie mit LSßi.The respective pressure compensator 18 can be controlled by a LS pressure, which is designated in FIG. 1 with LSA or LSB. The pertinent LS pressure LSA, LSB is also performed on a connection side 26 of the spool 16 at the same time. The respective spool 16 is also against the action of the compression spring 22 of a control pressure XA, XB a known pilot valve PA, PB controlled, with a abge used between spool 16 and pressure balance 1 8 control port pressure PΑ, and P'B opposite to the LS-pressure LSA, LSB activates the pressure scale 1 8 activates. The upcoming at the entrance of the pressure compensator 18 LS-pressure should be denoted by LSAI and LS ß i.
Eine weitere Anschlußseite 28 des Steuerschiebers 1 6 ist an einen Rücklaufanschluß R angeschlossen und der LS-Druck LSA und LSB ist über ein Wechsel ventil 30 ansteuerbar, das über ein Rückschlagventil 32 an LSmax angeschlossen ist, wobei das Rückschlagventil 32 in Richtung von LSmaχ öffnet. Die Pilotventile PA, PB sind an einen Steuerdruck PST als Versorgungsquelle angeschlossen und weiter an den Tankanschluß TQ. Die in der Fig.1 in der Art eines hydraulischen Schaltplans vorgestellte hdraulische Ventilvorrichtung ist nun gemäß der Längsschnittdarstellung nach der Fig.2 dort als konstruktive Ventillösung aufgezeigt. Die Ventilvor- richtung weist ein als Ganzes mit 34 bezeichnetes Ventilgehäuse auf, wobei das Ventilgehäuse in der Art eines modularen Baukastenkonzeptes realisiert ist. Insbesondere sind die Pilotventile PA, PB mit ihren Anschlußgehäuseteilen 36 an das Mittengehäuse 38 angeschlossen, wobei in Blickrichtung auf die Fig.2 gesehen im oberen Bereich des Mittengehäuses 38 die Nutzan- Schlüsse A, B in der Art von Einschraubpatronen angeschlossen sind und im unteren Bereich des Mittengehäuses 38 ist dieses von einem Durchgangskanal 40 durchgriffen, in dem insgesamt der Pumpendruck P ansteht, der über Anschlußleitungen 42 an eine Mittenkanalbohrung 44 angeschlossen ist, in die die beiden Steuereinrichtungen 14 eingesetzt sind. Ebenso wie der Durchgangskanal 40 erstreckt sich auch die Mittenkanalbohrung 44 quer zu einer Mittenlängsachse des Gesamtventilgehäuses 34 und entlang dieser nicht näher dargestellten Mitten längsachse ist in Blickrichtung auf die Fig.2 gesehen unterhalb der Mittenkanalbohrung 44 der Rücklaufanschluß R angeordnet, der über eine weitere Anschlußleitung 46 in den Mittenkanal 44 ausmündet. Ferner ist der Mittenkanal 44 vorzugsweise in Form einer Bohrung ausgebildet über Verbindungsleitungen 48 fluidführend an die Nutzanschlüsse A, B angeschlossen. Das in der Fig.l mit 32 bezeichnete Rückschlagventil ist gleichfalls in dem Ventilgehäuse 34 integriert, was aber aus Vereinfachungsgründen nicht näher dargestellt ist.Another connection side 28 of the spool 1 6 is connected to a return port R and the LS-pressure LSA and LS B is controlled by a changeover valve 30 which is connected via a check valve 32 to LS max , wherein the check valve 32 in the direction of LS ma χ opens. The pilot valves PA, PB are connected to a control pressure PST as a supply source and further to the tank terminal TQ. The presented in Figure 1 in the manner of a hydraulic circuit diagram hydraulic valve device is now shown there according to the longitudinal sectional view of Figure 2 as a constructive valve solution. The valve device has a valve housing designated as a whole by 34, wherein the valve housing is realized in the manner of a modular construction concept. In particular, the pilot valves PA, PB are connected with their terminal housing parts 36 to the center housing 38, seen in the direction of the Fig.2 in the upper part of the center housing 38 Nutzan- the conclusions A, B are connected in the type of Einschraubpatronen and in the lower part of the center housing 38, this is penetrated by a through-passage 40 in which a total of the pump pressure P is present, which is connected via connecting lines 42 to a central channel bore 44 into which the two control devices 14 are inserted. As well as the passageway 40, the central channel bore 44 extends transversely to a central longitudinal axis of the overall valve housing 34 and along this longitudinal axis not shown in detail is seen in the direction of the Fig.2 below the central channel bore 44 of the return port R, via a further connection line 46th opens into the center channel 44. Further, the center channel 44 is preferably formed in the form of a bore via connecting lines 48 fluidly connected to the Nutzanschlüsse A, B connected. The designated in Fig.l with 32 check valve is also integrated in the valve housing 34, but this is not shown in detail for reasons of simplification.
Die in Blickrichtung auf die Fig.2 gesehen horizontal verlaufende Steuerschieberachse des jeweiligen Steuerschiebers 16, gebildet durch die Mittenkanalbohrung 44 im Mittengehäuse 38, ist insoweit auf beiden Seiten mit dem jeweiligen Pilotgehäuse als Anschlußgehäuseteil 36 für das Zufüh- ren des Ansteuerdruckes XA, XB dichtend verschlossen. Außerhalb der Ventilmitte liegt der Rücklaufkanal R und vom Rücklaufkanal R gesehen reihen sich nach außen auf der einen Seite A,P und LSA an und auf der gegenüberliegenden Seite B, P und LSB- Wie bereits dargestellt, sind die LS-Ringkanäle LSA und LSB mit dem Wechselventil 30 verbunden, das die beiden Drücke voneinander trennt. Das Wechselventil 30 ist vorzugsweise als kreisrundes Einsteckteil ausgebildet und wird auf der sog. Flanschseite (nicht dargestellt) des scheibenartigen Ventilkörpers 34 montiert. Der Ausgangsanschluß des Wechselventils 30 führt über einen Druckkanal zum Rückschlagventil 32, das gegen höheren Druck im LS-Meldekanal (LSmax) abdichtet. Wird der Lastdruck LSA oder LSB höher als der Druck im Meldekanal, dann wird die- ser Druck über das Rückschlagventil 32 im Steuerblock weitergemeldet und von da aus weiter bis zu einer nicht näher dargestellten Systemdruckregelung für das gesamte Ventilsystem.The horizontally extending control spool axis of the respective control spool 16, as seen in the direction of FIG. 2, formed by the central channel bore 44 in the middle housing 38, is sealingly closed on both sides with the respective pilot housing as connection housing part 36 for the supply of the control pressure XA, XB , Outside the valve center is the return channel R and rows seen from the return channel R. As shown earlier, the LS-ring channels LSA and LSB are connected to the shuttle valve 30, which separates the two pressures from each other. The shuttle valve 30 is preferably designed as a circular plug-in part and is mounted on the so-called. Flange side (not shown) of the disc-like valve body 34. The output terminal of the shuttle valve 30 leads via a pressure channel to the check valve 32, which seals against higher pressure in the LS message channel (LS max ). If the load pressure LSA or LSB is higher than the pressure in the signaling channel, then this pressure is reported on via the check valve 32 in the control block and from there on to a system pressure control, not shown, for the entire valve system.
Der gesamte Raum in Form des Durchgangskanals 40 im unteren Teil des Mittengehäuses 38 steht unter Pumpendruck P und von diesem Raum führt jeweils eine Kanalleitung zur Hohlraumachse des jeweils zuordenbaren Steuerschiebers 16 neben die Ringkanäle, die zu den Nutzanschlüssen A und B führen. Die beiden Steuerschieber 16 sind identisch aufgebaut und nehmen in koaxialer Anordnung eine innenliegende, der Ventilblende vor- geschaltete Druckwaage 18 auf, die auch insoweit miteinander baugleich sind. Wie in der Fig.2 dargestellt, sind in Neutralstellung die Steuerschieber 16 durch gehäusefeste Anschläge und ihre jeweilige Arbeitsfeder (Druckfeder 22) in ihrer Stellung gehalten. Die Arbeitsfeder (Druckfeder 22) stützt sich dabei einerseits gegen das Gehäuse 34 des Ventils ab und andererseits gegen eine Verschlußschraube 50, die mit dem Steuerschieber 16 fest verschraubt ist. In der dahingehenden Ausgangs- oder Neutralstellung trennt der jeweilige Steuerschieber 16 den Arbeitsanschluß A oder B vom Pumpenanschluß P ab.The entire space in the form of the through-channel 40 in the lower part of the middle housing 38 is under pump pressure P and from this space each leads a channel line to the cavity axis of each assignable spool 16 in addition to the ring channels that lead to the Nutzanschlüssen A and B. The two control valves 16 are constructed identically and take in coaxial arrangement an internal, the valve diaphragm upstream pressure compensator 18, which are also identical in construction. As shown in Figure 2, in the neutral position, the spool 16 are held by fixed stops housing and their respective working spring (compression spring 22) in position. The working spring (compression spring 22) is supported on the one hand against the housing 34 of the valve and on the other hand against a screw plug 50 which is screwed firmly to the spool 16. In the pertinent initial or neutral position of the respective spool 16 separates the working port A or B from the pump port P.
Wie insbesondere die Fig.3 zeigt, ist eine variable Ventilblende gebildet in Form von ersten radialen Durchbrüchen 52 innerhalb der Hohlschieber- anordnung, bestehend aus Steuerschieber 16 und Druckwaage 18, wobei insoweit ein Dichtsteg P zu A und P zu B innerhalb des Ventilgehäuses 34 entsteht. Auch ist die innenliegende Druckwaage 18 über zweite radiale Durchbrüche 54 im Steuerschieber 16 ständig mit dem Pumpenkanal P verbunden. Die Federkammer mit der weiteren Druckfeder 24 der Druckwaage 18 ist über dritte radiale Durchbrüche 56 im Steuerschieber 16 ständig mit dem jeweils zuordenbaren LSA- oder LSB- Ringkanal verbunden. In der Neutralstellung sind die dritten radialen Durchbrüche 56 des Steuerschiebers 16 zusätzlich mit dem Federraum mit der Druckfeder 22 des Steuerschiebers 16 druckführend verbunden. Das geschieht durch korrespondierende Radialdurchgänge im Regelkolben der Druckwaage 18 und insoweit ist der genannte Federraum der Druckwaage 18 dann in Neutralstellung entlastet. Der Steuerschieber 16 kann mit vierten radialen Durchbrüchen 57 versehen sein, deren zur Ventilmitte liegende Kante auf glei- eher axialer Länge liegt wie die ersten Durchbrüche (Steuerkante 52). Diese dahingehenden vierten Durchbrüche 57 haben, anders als die ersten drei Durchbrüche, keine korrespondierenden Durchgänge im Regelkolben der Druckwaage 18. Die lagerichtige Orientierung von korrespondierenden Durchbrüchen mit Durchgängen ist durch eine Verdrehsicherung 58 in Form einer Rastkugel gewährleistet, die insoweit eine Radialsicherung bietet zwischen Steuerschieber 16 und dem Regelkolben der Druckwaage 18.As FIG. 3 in particular shows, a variable valve orifice is formed in the form of first radial apertures 52 within the hollow slide valve. arrangement, consisting of spool 16 and pressure compensator 18, in which respect a sealing web P to A and P to B within the valve housing 34 is formed. Also, the internal pressure compensator 18 is continuously connected via second radial openings 54 in the spool 16 with the pump channel P. The spring chamber with the further compression spring 24 of the pressure compensator 18 is connected via third radial openings 56 in the control slide 16 constantly with the respective assignable LSA or LSB ring channel. In the neutral position, the third radial openings 56 of the spool 16 are additionally connected to the spring chamber with the compression spring 22 of the spool 16 pressure leading. This is done by corresponding radial passages in the control piston of the pressure compensator 18 and so far said spring chamber of the pressure compensator 18 is then relieved in neutral position. The spool 16 may be provided with fourth radial openings 57, the edge lying to the middle of the valve lying on the same axial length as the first openings (control edge 52). These pertinent fourth openings 57 have, unlike the first three breakthroughs, no corresponding passages in the control piston of the pressure compensator 18. The correct orientation of corresponding openings with passages is ensured by an anti-rotation lock 58 in the form of a detent ball, which provides a radial lock so far between spool 16th and the control piston of the pressure compensator 18th
Im drucklosen Zustand drückt die Regelfeder 24 den Regelkolben der Druckwaage 18 gegen das Sacklochende des Steuerschiebers 16. Der da- hingehende Druckwaagekolben ist ebenfalls als Hohlkolben ausgebildet und hat einen zweiten radialen Durchgang 60, der die Verbindung mit dem Durchbruch 54 als sog. P-Durchbruch im Steuerschieber 16 beim Hub gegen die Druckwaagenfeder 24 verschließt (Steuerkante der Druckwaage 18). Ein erster radialer Durchgang 62 ist mit einer Ventilblende in Form des ersten Durchbruches 52 im Steuerschieber 16 ständig verbunden. Die Federkammer der Druckwaage 18 ist durch den dritten radialen Durchbruch 56 mit dem jeweils zuordenbaren dritten Durchgang 64 des Steuerschiebers 16 verbunden und außerdem mit Längsnuten 66 auf der Mantelfläche des Regelkolbens der Druckwaage 18. Die dahingehenden Längsnuten 66, von denen in der Fig.3 strichliniert nur eine dargestellt ist, erstrecken sich in Richtung R-Kanal bis zur Steuerkante des Regelkolbens und liegen - am Umfang betrachtet - zwischen den radialen Durchbrüchen und Durchgängen. Die jeweilige Längsnut 66 hat dabei ständige Verbindung mit dem vierten radialen Durchbruch 57 im Steuerschieber 16. Die dahingehende Längsnutverbindung stellt den LS-Meldeanschluß vom Arbeitsanschluß in die Federkammer mit der Druckfeder 24 der Druckwaage 18 dar. Dabei entspricht die Anschlußstelle 57 gemäß Darstellung nach der Fig.1 dem Abzweigpunkt LSB und der Durchbruch 56 bildet auf der einen Eingangssteuerseite der Druckwaage 18 den Meldeanschluß LSBI aus, wohingegen der vorstehend bezeichnete LS-Druck LSB den Fühlanschluß darstellt.In the unpressurized state, the control spring 24 presses the control piston of the pressure compensator 18 against the blind end of the control spool 16. The pressure compensator piston is also designed as a hollow piston and has a second radial passage 60, which connects to the aperture 54 as a so-called P breakthrough in the spool 16 at the stroke against the pressure compensator spring 24 closes (control edge of the pressure compensator 18). A first radial passage 62 is permanently connected to a valve orifice in the form of the first opening 52 in the spool 16. The spring chamber of the pressure compensator 18 is through the third radial opening 56 connected to the respectively assignable third passage 64 of the spool 16 and also with longitudinal grooves 66 on the lateral surface of the control piston of the pressure compensator 18. The pertinent longitudinal grooves 66, of which only one is shown by dashed lines in FIG. Channel to the control edge of the control piston and are - viewed at the periphery - between the radial openings and passages. The respective longitudinal groove 66 has permanent connection with the fourth radial opening 57 in the spool 16. The pertinent Längsnutverbindung provides the LS reporting port from the working port in the spring chamber with the compression spring 24 of the pressure compensator 18. In this case corresponds to the connection point 57 as shown in FIG .1 the branch point LSB and the breakthrough 56 forms on the one input control side of the pressure compensator 18, the signaling port LSBI, whereas the above-described LS-pressure LSB represents the sensing connection.
Wenn der Pumpendruck über den Pumpenanschluß P ansteht, dann wirkt dieser Druck auch in der PV oder PV Kammer der Druckwaage 18 und drückt den Regelkolben gegen die Feder, bis die korrespondierende Steuerkante schließt, so dass der PΑ- oder PV Druck genau auf den Betrag der Regelfeder 24 der Druckwaage 18 eingeregelt ist. Es ist selbstredend, dass die erwähnten radialen Durchbrüche und Durchgänge, wie in Fig.3 auch dargestellt, mehrfach entlang der Außenumfänge von Steuerschieber 16 und Regelkolben der Druckwaage 18 angeordnet sein können.When the pump pressure is present across the pump port P, then this pressure also acts in the PV or PV chamber of the pressure compensator 18 and pushes the control piston against the spring until the corresponding control edge closes, so that the PΑ or PV pressure exactly on the amount of Control spring 24 of the pressure compensator 18 is adjusted. It is self-evident that the mentioned radial openings and passages, as also shown in FIG. 3, can be arranged several times along the outer peripheries of the spool 16 and control spool of the pressure compensator 18.
Wird nun über die Pilotventile PA oder PB ein Pilotdruck vorgegeben, wobei als Pilotventil ein elektrohydraulisches Druckreduzierventil dienen soll, mit zentraler Versorgung aus einem Steuerölkreis Pst, dann verschiebt sich der Steuerschieber 16 gegen die Federkraft der Druckfeder 22 in Richtung R- Kanal (vgl. Fig.2). Die Ventilblende beginnt dann dabei einen Öffnungs- querschnitt zwischen Druckwaage 18 und jeweils zuordenbarem Arbeitsanschluß A oder B zu öffnen. Demgemäß bricht der PV oder PV Druck je- weils ein, weil Volumen abfließt. Die Regelfeder 24 kann dann den Regelkolben in Richtung öffnender Steuerkante schieben und es fließt Öl aus dem Pumpenanschluß P nach, bis wieder ein Staudruck vor der Ventilblende entsteht, der im Kräftegleichgewicht mit der Regelfeder und dem gemel- deten Lastdruck ist. Der Lastdruck wird dann vom vierten radialen Durchbruch 57 des Steuerschiebers 16 in die Längsnut 66, die gleichfalls mehrfach sich um den Umfang des Regelkolbens erstrecken kann, gemeldet und von dort durch den dritten radialen Durchbruch 64 im Regelkolben in die Federkammer mit der weiteren Druckfeder 24 geführt. Mit der erfindungs- gemäßen Lösung ist eine systemstabile Ventilvorrichtung vorgegeben, die platzsparend eine LS-Stromregelfunktion erfüllt. If now a pilot pressure is given via the pilot valves PA or PB, with a pilot valve serving as an electrohydraulic pressure reducing valve with central supply from a control oil circuit Pst, then the control slide 16 shifts against the spring force of the compression spring 22 in the direction of the R channel (compare FIG .2). The valve diaphragm then begins to open an opening cross-section between pressure compensator 18 and respectively assignable working port A or B. Accordingly, the PV or PV pressure breaks down because one, because volume drains off. The control spring 24 can then push the control piston in the direction of the opening control edge and oil flows from the pump port P until again a back pressure in front of the valve diaphragm arises, which is in equilibrium with the control spring and the reported load pressure. The load pressure is then reported by the fourth radial opening 57 of the spool 16 in the longitudinal groove 66, which can also extend several times around the circumference of the control piston, and from there through the third radial opening 64 in the control piston in the spring chamber with the other compression spring 24 , With the solution according to the invention, a system-stable valve device is specified which, in a space-saving manner, fulfills an LS flow control function.

Claims

P a t e n t a n s p r ü c h e Patent claims
1. Hydraulische Ventilvorrichtung, insbesondere LS-Stromregelventil, mit einer Fluidanschlußanordnung (10), beinhaltend mindestens - einen Druckversorgungsanschluß (P), einen Rücklaufanschluß (R), einen Sektions-Loadsensinganschluß (LS), - zwei Steueranschlüsse (PΑ und P'B), zwei Nutzanschlüsse (A,B) und - mindestens eine verfahrbare Steuereinrichtung (14) zum zumindest teilweisen Ansteuern von Anschlüssen der Fluidanschlußanordnung (10), dadurch gekennzeichnet, dass die jeweilige Steuereinrichtung (14) einem jeden Nutzanschluß (A,B) zugeordnet einen Steuerschieber (16) aufweist, dem eine Druckwaage (18) in Fluidrichtung zum jeweiligen1. Hydraulic valve device, in particular LS flow control valve, with a fluid connection arrangement (10), comprising at least - a pressure supply connection (P), a return connection (R), a section load-sensing connection (LS), - two control connections (PΑ and P'B) , two Nutzanschlüsse (A, B) and - at least one movable control device (14) for at least partially controlling terminals of the fluid connection assembly (10), characterized in that the respective control means (14) associated with each Nutzanschluß (A, B) a control slide (16), which a pressure compensator (18) in the fluid direction to the respective
Nutzanschluß (A, B) vorgeschaltet ist.Nutz connection (A, B) is connected upstream.
2. Ventil Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass die Druckwaage (18) innerhalb des Steuerschiebers (16) integriert ist und dass sowohl die Druckwaage (18) als auch der Steuerschieber (16) in einer Relativbewegung zueinander innerhalb eines Ventilgehäuses (34) längsverschiebbar geführt sind.2. Valve device according to claim 1, characterized in that the pressure compensator (18) within the spool (16) is integrated and that both the pressure compensator (18) and the spool (16) in a relative movement to each other within a valve housing (34) are guided longitudinally displaceable.
3. Ventilvorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass sowohl die Druckwaage (18) als auch der Steuerschieber (16) federzentriert in einer Ausgangsstellung gehalten sind, dass die Druckwaage (18) von einem LS-Druck (LSA, LSB) ansteuerbar ist, der gleichzeitig auf eine Anschlußseite (26) des Steuerschiebers (16) geführt ist, der von dem Steuerdruck (XA, XB) eines Pilotventils (PA, PB) ansteuerbar ist, und dass ein zwischen Steuerschieber (16) und Druckwaage (18) abge- griffener Steueranschlußdruck (P'A/ P'B) gegenläufig zum LS-Druck (LSA, LSB) wirkend die Druckwaage (18) ansteuert.3. A valve device according to claim 1 or 2, characterized in that both the pressure compensator (18) and the spool (16) are spring-centered held in a starting position, that the pressure compensator (18) of a LS-pressure (LSA, LSB) controlled is at the same time on a connection side (26) of the spool (16) is guided by the control pressure (X A , XB) of a pilot valve (PA, PB) is controlled, and that between a spool (16) and pressure compensator (18 ) griffener control port pressure (P ' A / P'B) opposite to the LS-pressure (LSA, LSB) acting the pressure compensator (18) controls.
4. Ventilvorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass eine weitere Anschlußseite (28) des Steuerschiebers (16) an den Rücklaufanschluß (R) angeschlossen ist, der im wesentlichen entlang einer Mittenachse im Ventilgehäuse (34) geführt ist und der in der Ausgangsstellung der Steuereinrichtung (14) zwischen den gegenüberliegenden Paaren von Steuerschieber (16) mit Druckwaage (18) verläuft.4. A valve device according to claim 3, characterized in that a further connection side (28) of the spool (16) to the return port (R) is connected, which is guided substantially along a central axis in the valve housing (34) and in the starting position of Control device (14) extends between the opposing pairs of spool (16) with pressure compensator (18).
5. Ventilvorrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass der jeweilige LS-Druck (LSA, LSB) für die Druckwaage (18) zu einem Wechselventil (30) geführt wird, das den höheren der beiden LS-Drücke (LSA, LSB) an ein Rückschlagventil (32) leitet.5. Valve device according to one of claims 1 to 4, characterized in that the respective LS-pressure (LSA, LSB) for the pressure compensator (18) to a shuttle valve (30) is guided, the higher of the two LS-pressures (LSA , LSB) to a check valve (32) passes.
6. Ventilvorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass an den Steuerschieber (16) fluidführend ein Nutzanschluß (A, B) angeschlossen ist.6. Valve device according to one of claims 1 to 5, characterized in that at the spool (16) fluid carrying a Nutzanschluß (A, B) is connected.
7. Ventilvorrichtung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass sowohl der Steuerschieber (16) als auch die Druckwaage (18) ineinandergeführte Hohlkolben aufweisen, die zumindest teilweise mit radialen Fluiddurchbrüchen (52,54,56,57) sowie Fluiddurchgängen (60,62,64) versehen sind und dass ein Teil der genannten Fluiddurch- brüche bzw. Fluiddurchgänge einen Fühlanschluß (LSA, LSB) und einen7. Valve device according to one of claims 1 to 6, characterized in that both the spool (16) and the pressure compensator (18) have nested hollow piston, which at least partially with radial fluid openings (52,54,56,57) and fluid passages ( 60,62,64) are provided and that a part of said fluid openings or fluid passages a sensing connection (LSA, LSB) and a
Meldeanschluß (LSA1, LSB-I) ausbilden.Form signaling connection (LS A 1, LSB-I).
8. Ventilvorrichtung nach Anspruch 7, dadurch gekennzeichnet, dass der8. Valve device according to claim 7, characterized in that the
Fühlanschluß (LSA, LSB) und der Meldeanschluß (LSAI, LSB-I) mittels einer Längsnut (66) miteinander in Verbindung sind. Sensing connection (LS A , LSB) and the signaling connection (LSAI, LSB-I) by means of a longitudinal groove (66) are interconnected.
9. Ventilvorrichtung nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass die Druckwaage (18) gegenüber dem zuordenbaren Steuerschieber (16) mittels einer Verdrehsicherung (58) gehalten ist.9. Valve device according to one of claims 1 to 8, characterized in that the pressure compensator (18) relative to the assignable spool valve (16) by means of a rotation (58) is held.
10. Ventilvorrichtung nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass als Teil des Ventilgehäuses (34) ein Durchgangskanal (40) als Verteiler vorgesehen ist, der an den Pumpenanschluß (P) angeschlossen die jeweilige Steuereinrichtung (14) mit Fluid versorgt. 10. Valve device according to one of claims 1 to 9, characterized in that as part of the valve housing (34) has a through passage (40) is provided as a manifold, which is connected to the pump port (P), the respective control device (14) supplied with fluid.
EP20080802278 2007-11-14 2008-09-17 Hydraulic valve device Not-in-force EP2220381B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710054134 DE102007054134A1 (en) 2007-11-14 2007-11-14 Hydraulic valve device
PCT/EP2008/007750 WO2009062564A1 (en) 2007-11-14 2008-09-17 Hydraulic valve device

Publications (2)

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EP2220381A1 true EP2220381A1 (en) 2010-08-25
EP2220381B1 EP2220381B1 (en) 2014-06-18

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EP20080802278 Not-in-force EP2220381B1 (en) 2007-11-14 2008-09-17 Hydraulic valve device

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US (1) US8479769B2 (en)
EP (1) EP2220381B1 (en)
JP (1) JP5462177B2 (en)
DE (1) DE102007054134A1 (en)
WO (1) WO2009062564A1 (en)

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Also Published As

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JP5462177B2 (en) 2014-04-02
WO2009062564A1 (en) 2009-05-22
US8479769B2 (en) 2013-07-09
US20100307621A1 (en) 2010-12-09
JP2011503479A (en) 2011-01-27
EP2220381B1 (en) 2014-06-18
DE102007054134A1 (en) 2009-05-20

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