EP2220381B1 - Hydraulic valve device - Google Patents
Hydraulic valve device Download PDFInfo
- Publication number
- EP2220381B1 EP2220381B1 EP20080802278 EP08802278A EP2220381B1 EP 2220381 B1 EP2220381 B1 EP 2220381B1 EP 20080802278 EP20080802278 EP 20080802278 EP 08802278 A EP08802278 A EP 08802278A EP 2220381 B1 EP2220381 B1 EP 2220381B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- connection
- pressure
- control
- pressure compensator
- 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
Links
Images
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 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 Nutzanêtn A and B.
- the two spool 16 are constructed identically and take in coaxial arrangement an internal, the valve diaphragm upstream pressure compensator 18, which are also identical in construction. Like in the Fig.2 shown, in 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.
- the pertinent longitudinal grooves 66 of which in the Figure 3 dashed lines only one is shown extending in the direction R 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 control slide 16.
- the pertinent Leksnut für provides the LS reporting connection from the working connection in the spring chamber with the compression spring 24 of the pressure compensator 18.
- the connection point 57 corresponds to the connection point 57 as shown in the Fig.1
- the branch point LS B and the opening 56 on the one input control side of the pressure compensator 18 forms the signaling connection LS B
- the above-described LS pressure LS B represents the sensing connection.
Landscapes
- 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)
Description
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 teilweisen Ansteuern von Anschlüssen der Fluidanschlußanordnung.
- a pressure supply port (P),
- a return connection (R),
- a section load-sensing connector (LS),
- two control terminals (P ' A ) and (P' B ),
- two service connections (A, B) and
- at least one movable control device for at least partially controlling connections of the fluid connection arrangement.
Durch die
Durch die
Bei der ein Wegeventil aufweisenden Ventilvorrichtung ist der Radialdurchbruch des Druckwaagenkolbens so angeordnet, dass durch diesen Radialdurchbruch und den zweiten Ventilkolben-Radialdurchbruch eine Verbindung vom Innenraum zum Pumpendruck-Ringkanal aufsteuerbar ist, wobei der zweite Ventilkolben-Radialdurchbruch eine Steuerkante darstellt, über die eine Verbindung vom Innenraum zum Load-Sensing-Ringkanal aufsteuerbar ist, und wobei unmittelbar an den zweiten Ventilkolben-Radialdurchbruch eine Ringnut anschließt, die in der Neutralstellung eine Verbindung vom Innenraum zum Load-Sensing-Ringkanal herstellt. Auf diese Weise soll erreicht werden, dass die Druckwaage unempfindlich gegen durch unterschiedliche Mengenströme verursachte unterschiedliche Strömungskräfte ist und zudem eine Bewegung des hydraulischen Verbrauchers in der Stellung "neutral" verhindert werden.In the valve device having a directional control valve, the radial opening of the pressure compensator piston is arranged so that a through this radial opening and the second valve piston radial breakthrough Connection can be opened from the interior to the pump pressure ring channel, wherein the second valve piston radial opening represents a control edge, via which a connection from the interior to the load-sensing ring channel can be opened, and wherein immediately adjoins the second valve piston radial opening an annular groove in the neutral position establishes a connection from the interior to the load-sensing ring channel. In this way, it should be achieved that the pressure compensator is insensitive to different flow forces caused by different flow rates and, moreover, prevents movement of the hydraulic load in the "neutral" position.
Eine hydraulische Ventilvorrichtung gemäß dem Oberbegriff des Anspruchs 1 ist aus
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 Druckwaage in Fluidrichtung zum jeweiligen Nutzanschluß A,B vorgeschaltet ist, wobei die jeweilige Druckwaage von einem LS-Druck ansteuerbar ist, der gleichzeitig auch auf eine Anschlussseite des jeweiligen Steuerschiebers geführt ist, und wobei jeweils ein zwischen Steuerschieber und Druckwaage abgegriffener Steueranschlussdruck gegenläufig zum LS-Druck wirkend die Druckwaage ansteuert und wobei die LS-Drücke führende Ringkanäle mit einem Wechselventil verbunden sind, das die beiden LS-Drücke voneinander trennt, 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 übertragen. 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 according to the characterizing part of claim 1 is provided that the respective control means associated with each user port A, B has a spool, which is preceded by a pressure compensator in the fluid direction to the respective user port A, B, wherein the respective pressure compensator of an LS Pressure can be controlled, which is also performed on a connection side of the respective spool, and wherein in each case a tapped between spool and pressure balance control port pressure opposite to the LS-pressure acting on the pressure balance and wherein the LS-pressure conducting ring channels are connected to a shuttle valve, the the two LS pressures separate, the hydraulic LS system is less sensitive to system vibrations. Due to the upstream pressure compensator this can have a decisive influence on system stability. Pressure oscillations are often generated by mechanical vibrations of resilient structures in the respective connected hydraulic consumers (crane arms) and then transmitted through the load-sensing circuit (LS) on the pressure compensator. The LS-pressure (load message pressure) is then the reference variable for the upstream pressure compensator and can smooth the pressure oscillations, even before the pressure is forwarded to the subsequent spool of the respective control device, then the constant supply depending on its respective slide or piston position ensures 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 Relativbewegung 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 proved, if 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 is simultaneously guided on a connection side of the spool, which in turn is controlled by the control pressure of a pilot valve and further wherein a between spool and pressure balance abgegeder control connection pressure opposite to the LS-pressure acting the pressure compensator activates.
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 maßstäblicher Darstellung die
- Fig.1
- in der Art eines hydraulischen Schaltplans den prinzipiellen Aufbau der hydraulischen Ventilvorrichtung in Form eines LS-Stromregelventils;
- 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.3
- eine vergrößerte Darstellung einer geschnitten dargestellten Längsansicht einer in Blickrichtung auf die
Fig.2 gesehen rechten Steuereinrichtung mit Druckwaage und Steuerschieber.
- Fig.1
- in the manner of a hydraulic circuit diagram, the basic structure of the hydraulic valve device in the form of a LS flow control valve;
- Fig.2
- the practical implementation of the circuit diagram after the
Fig.1 in a valve product, partially with its essential components once in longitudinal section and once in view is reproduced; - Figure 3
- an enlarged view of a longitudinal view shown in section in the direction of the
Fig.2 seen right control device with pressure balance and spool.
Die hydraulische Ventilvorrichtung nach der
Die in der
The in the
Die in Blickrichtung auf die
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 vorgeschaltete Druckwaage 18 auf, die auch insoweit miteinander baugleich sind. Wie in der
Wie insbesondere die
Im drucklosen Zustand drückt die Regelfeder 24 den Regelkolben der Druckwaage 18 gegen das Sacklochende des Steuerschiebers 16. Der dahingehende 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
Wenn der Pumpendruck über den Pumpenanschluß P ansteht, dann wirkt dieser Druck auch in der P'A- oder P'B- Kammer der Druckwaage 18 und drückt den Regelkolben gegen die Feder, bis die korrespondierende Steuerkante schließt, so dass der P'A- oder P'B- 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
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.
Claims (10)
- A hydraulic valve device, in particular an LS flow control valve, with a fluid connection arrangement (10), comprising at least- a pressure supply connection (P),- a return flow connection (R),- a section load sensing connection (LS),- two control connections (P'A and P'B),- two utility connections (A, B) and- at least one displaceable control means (14) for at least partially triggering connections of the fluid connection arrangement (10),the respective control means (14) assigned to each utility connection (A, B) having a control slide valve (16) to which a pressure compensator (18) is connected upstream in the fluid direction to the respective utility connection (A, B), the respective pressure compensator (18) being able to be triggered by an LS pressure (LSA, LSB) which is also routed at the same time to one connection side (26) of the respective control slide valve (16), a control connection pressure (P'A, P'B) tapped respectively between the control slide valve (16) and the pressure compensator (18) triggering the pressure compensator (18) by acting in the opposite direction to the LS pressure (LSA, LSB), characterised in that the annular channels guiding the LS pressures (LSA, LSB) are connected to a shuttle valve (30) which separates the two LS pressures (LSA, LSB) from one another.
- The valve device according to Claim 1, characterised in that the pressure compensator (18) is integrated within the control slide valve (16) and that both the pressure compensator (18) and the control slide valve (16) are guided such as to be longitudinally displaceable in relative motion to one another within a valve housing (34).
- The valve device according to Claim 1 or 2, characterised in that both the pressure compensator (18) and the control slide valve (16) are held spring-centred in an initial position.
- The valve device according to Claim 3, characterised in that a further connection side (28) of the control slide valve (16) is connected to the return flow connection (R) which is guided essentially along a middle axis in the valve housing (34) and which runs in the initial position of the control means (14) between the opposite pairs of control slide valves (16) with the pressure compensator (18).
- The valve device according to any of Claims 1 to 4, characterised in that the shuttle valve (30) routes the higher of the two LS pressures (LSA, LSB) to a check valve (32).
- The valve device according to any of Claims 1 to 5, characterised in that a utility connection (A, B) is connected to the control slide valve (16) such as to convey fluid.
- The valve device according to any of Claims 1 to 6, characterised in that both the control slide valve (16) and the pressure compensator (18) have hollow pistons that a guided within one another and that are provided at least partially with radial fluid openings (52, 54, 56, 57) and fluid passages (60, 62, 64) and that some of said fluid openings and fluid passages form a sensing connection (LSA, LSB) and a reporting connection (LSA1, LSB1).
- The valve device according to Claim 7, characterised in that the sensing connection (LSA, LSB) and the reporting connection (LSA1, LSB1) are interconnected by means of a longitudinal groove (66).
- The valve device according to any of Claims 1 to 8, characterised in that the pressure compensator (18) is held by means of a locking element (58) relative to the assignable control slide valve (16).
- The valve device according to any of Claims 1 to 9, characterised in that as part of the valve housing (34) there is a through channel (40) as a distributor which, connected to the pump connection (P), supplies the respective control means (14) with fluid.
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)
Publication Number | Publication Date |
---|---|
EP2220381A1 EP2220381A1 (en) | 2010-08-25 |
EP2220381B1 true EP2220381B1 (en) | 2014-06-18 |
Family
ID=40220677
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20080802278 Not-in-force EP2220381B1 (en) | 2007-11-14 | 2008-09-17 | Hydraulic valve device |
Country Status (5)
Country | Link |
---|---|
US (1) | US8479769B2 (en) |
EP (1) | EP2220381B1 (en) |
JP (1) | JP5462177B2 (en) |
DE (1) | DE102007054134A1 (en) |
WO (1) | WO2009062564A1 (en) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009021103A1 (en) * | 2009-05-13 | 2010-11-18 | Hydac Filtertechnik Gmbh | Hydraulic valve device |
DE102009052257A1 (en) * | 2009-11-06 | 2011-05-12 | Claas Industrietechnik Gmbh | valve assembly |
DE102010051690A1 (en) * | 2010-11-17 | 2012-05-24 | Hydac Filtertechnik Gmbh | Hydraulic valve device |
FR2999623B1 (en) * | 2012-12-18 | 2015-02-27 | Fluid System | HYDRAULIC DISPENSER WITH INTEGRATED PRESSURE BALANCE AND MOTORIZED ENGINE EQUIPPED WITH SUCH A DISTRIBUTOR |
DE102017200418A1 (en) * | 2017-01-12 | 2018-07-12 | Robert Bosch Gmbh | Valve assembly for dual-circuit summation |
JP7028760B2 (en) * | 2018-12-28 | 2022-03-02 | Ckd株式会社 | Spool valve |
EP3901501A1 (en) * | 2020-04-26 | 2021-10-27 | Hamilton Sundstrand Corporation | Servo valve |
JP2023135264A (en) * | 2022-03-15 | 2023-09-28 | 川崎重工業株式会社 | Valve block, and multi-control valve device comprising the same |
Family Cites Families (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3984979A (en) * | 1973-07-06 | 1976-10-12 | Tadeusz Budzich | Load responsive fluid control valves |
US3911942A (en) * | 1974-03-28 | 1975-10-14 | Gen Signal Corp | Compensated multifunction hydraulic system |
US4187877A (en) * | 1975-01-13 | 1980-02-12 | Commercial Shearing Inc. | Compensated work port fluid valves |
JPS5997302A (en) * | 1982-11-25 | 1984-06-05 | Kayaba Ind Co Ltd | Oil pressure control circuit |
US4617798A (en) * | 1983-04-13 | 1986-10-21 | Linde Aktiengesellschaft | Hydrostatic drive systems |
DE4036720C2 (en) * | 1990-11-17 | 2001-09-13 | Linde Ag | Control circuit for the load-independent distribution of a pressure medium flow |
JP3289852B2 (en) * | 1993-08-12 | 2002-06-10 | 株式会社小松製作所 | Direction control valve for flow rate support |
DE4416285A1 (en) | 1994-05-07 | 1995-11-09 | Bosch Gmbh Robert | Electropneumatic valve device |
DE19646445A1 (en) * | 1996-11-11 | 1998-05-14 | Rexroth Mannesmann Gmbh | Valve arrangement |
US5715865A (en) * | 1996-11-13 | 1998-02-10 | Husco International, Inc. | Pressure compensating hydraulic control valve system |
US5791142A (en) * | 1997-03-27 | 1998-08-11 | Husco International, Inc. | Hydraulic control valve system with split pressure compensator |
DE19929024A1 (en) | 1999-06-25 | 2000-12-28 | Bosch Gmbh Robert | Vehicle-mounted device for dosing and distributing scattered material has mass flow control device with single hydraulically operated control element for both dosing and distribution functions |
EP1370773B1 (en) | 2001-03-21 | 2005-06-22 | Bucher Hydraulics GmbH | Control valve |
WO2002088550A1 (en) * | 2001-04-17 | 2002-11-07 | Bucher Hydraulics Gmbh | Directional control valve comprising an internal pressure regulator |
DE10135298A1 (en) * | 2001-07-24 | 2003-02-13 | Bosch Rexroth Ag | valve assembly |
DE10334056A1 (en) * | 2003-07-25 | 2005-02-10 | Bosch Rexroth Ag | way valve |
DE102005022891A1 (en) * | 2005-04-05 | 2006-10-12 | Bosch Rexroth Aktiengesellschaft | Hydraulic control arrangement and control block |
DE102005033222B4 (en) | 2005-07-15 | 2012-05-16 | Bosch Rexroth Aktiengesellschaft | LUDV valve assembly |
-
2007
- 2007-11-14 DE DE200710054134 patent/DE102007054134A1/en not_active Withdrawn
-
2008
- 2008-09-17 US US12/734,290 patent/US8479769B2/en not_active Expired - Fee Related
- 2008-09-17 WO PCT/EP2008/007750 patent/WO2009062564A1/en active Application Filing
- 2008-09-17 EP EP20080802278 patent/EP2220381B1/en not_active Not-in-force
- 2008-09-17 JP JP2010533448A patent/JP5462177B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
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US8479769B2 (en) | 2013-07-09 |
JP5462177B2 (en) | 2014-04-02 |
EP2220381A1 (en) | 2010-08-25 |
US20100307621A1 (en) | 2010-12-09 |
DE102007054134A1 (en) | 2009-05-20 |
WO2009062564A1 (en) | 2009-05-22 |
JP2011503479A (en) | 2011-01-27 |
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