EP2871370A1 - Valve assembly - Google Patents
Valve assembly Download PDFInfo
- Publication number
- EP2871370A1 EP2871370A1 EP20140185252 EP14185252A EP2871370A1 EP 2871370 A1 EP2871370 A1 EP 2871370A1 EP 20140185252 EP20140185252 EP 20140185252 EP 14185252 A EP14185252 A EP 14185252A EP 2871370 A1 EP2871370 A1 EP 2871370A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- pressure
- load
- pressure compensator
- line
- 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
Links
- 230000000712 assembly Effects 0.000 claims abstract description 10
- 238000000429 assembly Methods 0.000 claims abstract description 10
- 238000006073 displacement reaction Methods 0.000 claims description 9
- 238000010586 diagram Methods 0.000 description 4
- 238000010276 construction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 210000003746 feather Anatomy 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0416—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
- F15B2211/3053—In combination with a pressure compensating valve
- F15B2211/30555—Inlet and outlet of the pressure compensating valve being connected to the directional control valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/605—Load sensing circuits
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/605—Load sensing circuits
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
- F15B2211/6052—Load sensing circuits having valve means between output member and the load sensing circuit using check valves
Definitions
- the invention relates to a valve arrangement according to the preamble of patent claim 1 and a control arrangement with such valve arrangements.
- Valve arrangements are known from the prior art, which are usually arranged in a one-piece disc-like housing and serve to supply a hydraulic consumer.
- control arrangement which thus supplies and controls various consumers of the mobile working machine.
- the control arrangement is powered by a variable displacement pump. Since the variable displacement pump must supply all consumers, this is done in response to a load-sensing pressure of a load-sensing line that extends through all valve assemblies of the control assembly. This is always the highest load pressure of all consumers.
- each valve arrangement has an individual pressure compensator arranged downstream of its metering orifice, which acts in the opening direction on the pressure after the respective metering orifice and in the closing direction on the highest load pressure of the load-sensing line (uniform for the control arrangement) becomes.
- the pressure compensator valve body is loaded in the opening direction with the pressure of the first connecting line, which is arranged downstream of the metering orifice.
- a disadvantage of such valve arrangements is that pressure medium can leak from the pump connection via the metering orifice into the first connection line.
- the pressure compensator valve body of the pressure compensator is displaced in the opening direction until this leakage is relieved via the additional connection of the pressure compensator in the load sensing line.
- the pressure compensator valve body then remains in this position when the pressure in the load-sensing line is low, that is, when no consumer is actuated.
- the claimed valve assembly is used to supply a hydraulic load and has a metering orifice with a main spool and a downstream of the metering orifice arranged pressure balance, which is connected via a first serving as a feed line connecting line with the metering orifice, and the pressure compensator valve body in the opening direction of the pressure of the connecting line and in the closing direction is acted upon by the load pressure of a load-sensing line.
- the valve assembly for a higher-level control arrangement is suitable, which supplies several consumers according to the principle of load-independent flow distribution (LUDV).
- an output of the pressure compensator is connected via a spring-loaded check valve to the load-sensing line.
- a further advantage is that in the case of a grouping of a plurality of valve arrangements (for example as valve disks) in a block via the respective non-return valve, the load-sensing selection is also provided without shuttle valves (known from the prior art).
- Another advantage is the fact that this solution can be retrofitted during commissioning or even later for individual consumers (for example, excavator functions).
- the pressure compensator valve body is acted upon by a weak spring in the closing direction.
- the pressure compensator can also be installed such that the closing direction is directed against the gravity of the pressure compensator valve body.
- the check valve is arranged in the pressure balance valve body.
- the load pressure of the supplied via the valve assembly according to the invention consumer which is present in the first connection line, via the load-sensing line of this pressure fluid flow path Valve arrangement are reported to a higher-level load sensing line of a higher-level control arrangement, so that this does not require load-sensing shuttle valves.
- the change in the pressure medium flow under load transfer can be reduced by the additional connection.
- the LS signal of the valve assembly with the greatest load pressure is then tapped by the pressure compensator, the pressure drop across the pressure compensator thereby does not reduce the LS signal.
- the additional connection can be used in one or more valve assemblies (valve discs) in the block.
- the additional connection can be formed by a longitudinal bore and by a transverse bore in the pressure balance valve body.
- the output of the pressure compensator is preferably returned via a second connecting line serving as a supply line to an input of a main valve comprising the metering orifice.
- the second connection line is a branched bridge line which connects the output of the pressure balance with two inputs of the main valve. So can be supplied via the main valve either one of two working ports of the valve assembly or the main valve.
- the main valve and the pressure compensator are arranged in a common housing. Then, the pressure compensator valve body can be arranged perpendicular to the main spool.
- One or a few or preferably all said lines of the valve arrangement according to the invention may be formed by respective channels in the housing.
- the control arrangement serves to supply at least two hydraulic consumers. It preferably has a variable displacement pump or a fixed displacement pump (for example in the case of backhoe loaders) and, for each consumer, a prescribed valve arrangement whose respective load-sensing line is connected to a higher-order load-sensing line of the control arrangement.
- the highest load pressure of all consumers supplied by the pump or a pressure derived therefrom always acts in the higher-level load sensing line and in the individual subordinate load sensing lines connected to it. This is achieved via the respective check valves of the valve arrangements or via a connection which is opened by the pressure balance valve body of the valve arrangement of the highest-load consumer.
- the control arrangement can be designed as a valve block, in which the housings of the individual valve arrangements are designed as valve disks and abut each other.
- a first throttle is arranged in front of or behind the check valve of each valve arrangement, and a second throttle is arranged between the superordinate load sensing line and a tank line of the control arrangement.
- a flow control valve may be provided which comprises the second throttle.
- FIG. 1 shows a circuit diagram of a control arrangement with a plurality of valve assemblies according to the invention 1.
- Each valve assembly 1 has two working ports A, B, to each of which a bidirectionally operable (not shown) hydraulic consumers can be connected.
- the valve arrangements 1 form a common pump line 2, a common tank line 4 and a common superordinate load-sensing line 6.
- the three lines 2, 4, 6 are formed by a respective continuous common channel section.
- the lines 2, 4, 6 are closed by a closure element 12 which bears against the housing of the last valve arrangement 1.
- An input element 8 connects an output port of a variable displacement pump 10 via pump ports P to the pump line 2.
- the input element 8 further connects a tank T via tank ports T to the tank line 4.
- the higher-order load-sensing line 6 of the input element 8 is connected via a throttle 16 to the tank connection T of the input element 8. This serves to relieve the control assembly when the flow rate is zero. This is the case, for example, when all valve assemblies 1 are in their neutral position.
- FIG. 2 shows a circuit diagram of the valve arrangement 1 according to the invention FIG. 1 , It has a designed as a 6/3-way valve main valve 18 with a continuously variable main spool 20 and designed as a 3/3-way valve pressure compensator 22 with a continuously adjustable pressure compensator valve body 24.
- a metering orifice 26 is opened for the connected to the working ports A, B consumers, so that pressure medium from the pump line 2 via the main valve 18, via a first connecting line 28, via the at least partially opened-up pressure compensator 22, via its output 29, can flow back to the main valve 18 via the serving as a return line second connecting line 30 and a load-holding valve 32.
- the pressure compensator valve body 24 is acted upon in the opening direction via a control line 34 with the pressure of the first connecting line 28, while it is acted upon in the closing direction via a subordinate load sensing line 35 to the pressure of the parent load sensing line 6. Also in the closing direction, a comparatively weak spring 36 acts.
- each pressure compensator 22 opens in its open position 38, a connection 39 from the first connection line 28 to the subordinate load sensing line 35 ,
- a discharge channel 40 is provided between the outlet 29 of the pressure compensator 22 or the second connecting line 30 and the subordinate load-sensing line 35. In this one are biased by a spring Check valve 42 and a throttle 44 is provided. The opening direction of the check valve 42 is directed from the output 29 and from the second connecting line 30 to the load-sensing line 35.
- FIG. 3 shows the valve assembly 1 according to the invention in a sectional view.
- the main valve 18 extends in FIG. 3 horizontally, while the pressure compensator 22 is received in a transverse bore and closed with a locking screw 48.
- the main valve 18, whose main slide in FIG. 3 not shown, and the pressure compensator 22 are arranged in a common housing 50.
- the pressure medium flows via the metering orifice 26 and via the first connecting line 28 to the pressure compensator 22, the pressure compensator valve body 24 in FIG. 3 is shown in its closed position.
- a connection from the first connecting line 28 to the output 29 is opened, so that the pressure medium via the second connecting line 30, as a branched bridge channel to the main valve 18th returns, can flow.
- the metering orifice 26 can be opened bidirectionally, it is possible to use the (in FIG. 3 not shown) main spool also be selected over which portion of the bridge channel 30 and on which side of the main valve 18, the pressure medium downstream of the pressure compensator 22 is continued. Accordingly, either the work port A or the Working port B is connected to the pressure compensator 22 while the other working port B or A is opened to the tank port T.
- the pressure compensator valve body 24 is approximately circular cylindrical and in this embodiment has an eccentrically a channel which forms the additional connection 39.
- a cross-bore portion of the connection 39 is arranged such that at a maximum opening of the pressure compensator 22 of the first connection channel 28 and thus the input of the pressure compensator 22 is connected to the subordinate load-sensing line 35. This happens when the affected valve assembly 1 supplies the highest-load consumer. This is an option.
- the check valve 42 is sufficient for the message of the LS signal.
- the load pressure of the first connecting line 28 is reported in the load-sensing line 35, so that this load pressure as the highest load pressure of the entire control arrangement (see. FIG. 1 ) applies.
- the spring-biased check valve 42 is arranged, whose input is arranged by a transverse bore to the output 29 of the pressure compensator 22 and the output in a load-sensing pressure chamber, which is formed between the end face of the pressure balance valve body 24 and the screw plug 48, and which is connected to the slave load sensing line 35.
- the input of the transverse bore is arranged on the pressure compensator valve body 24, that the connection via the discharge channel 40 and the check valve 42 regardless of the position of the pressure compensator valve body 24 is always given.
- valve arrangement with a main valve and an individual pressure compensator which together serve to supply a consumer, wherein a plurality of such valve arrangements are provided for supplying a plurality of consumers with load pressure-independent flow distribution.
- the individual pressure compensators are arranged downstream of the skin valve and acted upon by a control pressure of a parent load-sensing channel in the closing direction, while they are acted upon by the tapped behind the main valve supply pressure in the opening direction.
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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)
Abstract
Offenbart ist eine Ventilanordnung mit einem Hauptventi (l8) und einer Individualdruckwaage (22) die gemeinsam zur Versorgung eines Verbrauchers dienen, wobei mehrere derartige Ventilanordnungen zur Versorgung mehrere Verbraucher mit lastdruckunabhängiger Durchflussverteilung vorgesehen sind. Dem entsprechend sind die Individualdruckwaagen (22) stromab der Hautventils (18) angeordnet und von einem Steuerdruck einer übergeordneten Load-Sensing-Kanal (35) in Schließrichtung beaufschlagt, während sie vom hinter der Hauptventil (18) abgegriffene Versorgungsdruck (34) in Öffnungsrichtung beaufschlagt sind. Dabei ist im Druckwaagenventilschieber (24) zur Abfuhr von Leckage des Hauptventils - insbesondere wenn dies als Schieberventil ausgeführt ist - ein Rückschlagventil (42) vorgesehen, dessen Öffnungsrichtung vom Ausgang der Druckwaage (22) zum Load-Sensing-Kanal (35) gerichtet ist, und das unabhängig von der Position des Druckwaagenventilkörpers (24) stets verbunden ist.Disclosed is a valve arrangement with a Hauptventi (l8) and an individual pressure compensator (22) which together serve to supply a consumer, wherein a plurality of such valve assemblies are provided to supply multiple consumers with load pressure independent flow distribution. Accordingly, the individual pressure compensators (22) are arranged downstream of the skin valve (18) and acted upon by a control pressure of a superordinate load-sensing channel (35) in the closing direction, while it acts on the supply pressure (34) tapped behind the main valve (18) in the opening direction are. In this case, a check valve (42) is provided in the pressure compensator valve spool (24) for removing leakage of the main valve - in particular if this is designed as a slide valve, whose opening direction is directed from the output of the pressure compensator (22) to the load-sensing channel (35), and which is always connected regardless of the position of the pressure balance valve body (24).
Description
Die Erfindung betrifft eine Ventilanordnung gemäß dem Oberbegriff des Patentanspruchs 1 und eine Steueranordnung mit derartigen Ventilanordnungen.The invention relates to a valve arrangement according to the preamble of
Aus dem Stand der Technik sind Ventilanordnungen bekannt, die meistens in einem einstückigen scheibenartigen Gehäuse angeordnet sind und zur Versorgung eines hydraulischen Verbrauchers dienen. Dabei werden bei mobilen Arbeitsmaschinen wie zum Beispiel bei Baggern mehrere derartiger Ventilanordnungen zu einer Steueranordnung gruppiert, die somit verschiedenen Verbraucher der mobilen Arbeitsmaschine versorgt und steuert. Dazu wird die Steueranordnung von einer Verstellpumpe versorgt. Da die Verstellpumpe alle Verbraucher versorgen muss, geschieht dies in Abhängigkeit eines Load-Sensing-Drucks einer Load-Sensing-Leitung, die sich durch alle Ventilanordnungen der Steueranordnung erstreckt. Darin herrscht stets der höchste Lastdruck aller Verbraucher.Valve arrangements are known from the prior art, which are usually arranged in a one-piece disc-like housing and serve to supply a hydraulic consumer. In mobile working machines such as excavators, several such valve arrangements are grouped into a control arrangement which thus supplies and controls various consumers of the mobile working machine. For this purpose, the control arrangement is powered by a variable displacement pump. Since the variable displacement pump must supply all consumers, this is done in response to a load-sensing pressure of a load-sensing line that extends through all valve assemblies of the control assembly. This is always the highest load pressure of all consumers.
Gemäß dem Prinzip der lastunabhängigen Durchflussverteilung (LUDV) hat jede Ventilanordnung eine stromab ihrer Zumessblende angeordnete Individual-Druckwaage, die in Öffnungsrichtung von dem Druck nach der jeweiligen Zumessblende und in Schließrichtung vom (für die Steueranordnung einheitlichen) höchsten Lastdruck der Load-Sensing-Leitung beaufschlagt wird.According to the principle of load-independent flow distribution (LUDV), each valve arrangement has an individual pressure compensator arranged downstream of its metering orifice, which acts in the opening direction on the pressure after the respective metering orifice and in the closing direction on the highest load pressure of the load-sensing line (uniform for the control arrangement) becomes.
In der Veröffentlichung "LUDV-Steuerblock in Scheibenbauweise", RD 64125 vom Februar 2011 der Anmelderin und in der
Nachteilig an derartigen Ventilanordnungen ist, dass Druckmittel vom Pumpenanschluss über die Zumessblende in die erste Verbindungsleitung lecken kann. Dadurch wird der Druckwaagenventilkörper der Druckwaage so lange in Öffnungsrichtung verschoben, bis diese Leckage über die zusätzliche Verbindung der Druckwaage in die Load-Sensing-Leitung entlastet wird. Der Druckwaagenventilkörper bleibt dann in dieser Stellung stehen, wenn der Druck in der Load-Sensing-Leitung gering ist, also wenn kein Verbraucher betätigt ist. Für ein optimales Ansprechverhalten des über die Ventilanordnung versorgten Verbrauchers soll der Druckwaagenventilkörper aber in der Stellung stehen bleiben, in der er einen minimalen Öffnungsquerschnitt zwischen der ersten Verbindungsleitung und dem Ausgang der Druckwaage gegeben ist (Nullüberdeckung).A disadvantage of such valve arrangements is that pressure medium can leak from the pump connection via the metering orifice into the first connection line. As a result, the pressure compensator valve body of the pressure compensator is displaced in the opening direction until this leakage is relieved via the additional connection of the pressure compensator in the load sensing line. The pressure compensator valve body then remains in this position when the pressure in the load-sensing line is low, that is, when no consumer is actuated. For optimal response of the supplied via the valve assembly consumer of the pressure balance valve body but should remain in the position in which it is given a minimum opening cross-section between the first connecting line and the output of the pressure compensator (zero coverage).
Diese Aufgabe wird gelöst durch eine Ventilanordnung mit den Merkmalen des Patentanspruchs 1 und durch eine Steueranordnung mit den Merkmalen des Patentanspruchs 9.This object is achieved by a valve arrangement having the features of
Die beanspruchte Ventilanordnung dient zur Versorgung eines hydraulischen Verbrauchers und hat eine Zumessblende mit einem Hauptschieber und eine stromab der Zumessblende angeordneten Druckwaage, die über eine erste als Zulaufleitung dienende Verbindungsleitung mit der Zumessblende verbundenen ist, und deren Druckwaagenventilkörper in Öffnungsrichtung vom Druck der Verbindungsleitung und in Schließrichtung vom Lastdruck einer Load-Sensing-Leitung beaufschlagt ist. Damit ist die Ventilanordnung für eine übergeordnete Steueranordnung geeignet, die mehrere Verbraucher nach dem Prinzip der lastunabhängigen Durchflussverteilung (LUDV) versorgt. Bei der erfindungsgemäßen Ventilanordnung ist ein Ausgang der Druckwaage über ein federbelastetes Rückschlagventil mit der Load-Sensing-Leitung verbunden.The claimed valve assembly is used to supply a hydraulic load and has a metering orifice with a main spool and a downstream of the metering orifice arranged pressure balance, which is connected via a first serving as a feed line connecting line with the metering orifice, and the pressure compensator valve body in the opening direction of the pressure of the connecting line and in the closing direction is acted upon by the load pressure of a load-sensing line. Thus, the valve assembly for a higher-level control arrangement is suitable, which supplies several consumers according to the principle of load-independent flow distribution (LUDV). In the valve arrangement according to the invention, an output of the pressure compensator is connected via a spring-loaded check valve to the load-sensing line.
Über das erfindungsgemäße Rückschlagventil zwischen dem Ausgang der Druckwaage und dem Load-Sensing-Kanal können Leckagen von der ersten Verbindungsleitung über die geöffnete Druckwaage, über den Ausgang der Druckwaage und über das erfindungsgemäße Rückschlagventil in die Load-Sensing-Leitung abfließen, sofern kein Verbraucher betätigt ist. Die Druckwaage öffnet sich dabei gerade soweit, dass sich die gewünschte Nullüberdeckung in einer Druckregelverbindung zwischen dem ersten Verbindungskanal und dem Ausgang ergibt. Damit ist der Druckwaagenventilkörper ideal positioniert. Wird nun die Zumessblende (wieder) geöffnet, erfolgt bei getriebenen Lasten am Verbraucher ein unmittelbarer Druckaufbau in der Load-Sensing-Leitung, da sich die Druckwaage weiter öffnet, und dabei das Druckmittel eines Druckraumes, der zwischen dem Druckwaagenventilkörper und einem Gehäuseabschnitt (zum Beispiel einer Verschlussschraube) angeordnet ist, in die Load-Sensing-Leitung schiebt. Bei treibenden Lasten wie zum Beispiel dem Stiel an einem Bagger wird das Druckmittel von der Verstellpumpe zum Verbraucher durch die initial geschlossene Druckwaage gedrosselt, und nicht wie bei initial geöffneter Druckwaage ungedrosselt durchgeleitet. Dadurch läuft der entsprechende Verbraucher langsamer los und ist damit dynamisch ähnlicher den getriebenen Lasten, die von der Dynamik des Load-Sensing-Signals und der Verstellpumpe abhängig sind. Ein weiterer Vorteil besteht darin, dass bei einer Gruppierung mehrer Ventilanordnungen (z.B. als Ventilscheiben) in einem Block über das jeweilige Rückschlagventil die Load-Sensing-Auswahl auch ohne (aus dem Stand der Technik bekannte) Wechselventile gegeben ist. Ein weiterer Vorteil ist darin zu sehen, dass diese Lösung während der Inbetriebnahme oder noch später für einzelne Verbraucher (zum Beispiel Baggerfunktionen) nachgerüstet werden kann.About the check valve according to the invention between the output of the pressure compensator and the load-sensing channel leaks from the first connecting line via the open pressure compensator, via the output of the pressure compensator and the check valve according to the invention in the load-sensing line flow, if no consumer actuated is. The pressure compensator just opens up to the point where the desired zero overlap results in a pressure control connection between the first connection channel and the outlet. Thus, the pressure compensator valve body is ideally positioned. If the metering orifice is (re) opened, a direct build-up of pressure in the load-sensing line takes place with driven loads on the load, because the pressure compensator continues to open, and the pressure medium of a pressure chamber connected between the pressure compensator valve body and a housing section (for example a screw plug) is placed in the load-sensing line pushes. When driving loads such as the handle on an excavator, the pressure medium from the variable displacement pump to the consumer is throttled by the initially closed pressure compensator, and not passed through unthrottled as initially open pressure compensator. As a result, the corresponding consumer starts slower and is thus dynamically more similar to the driven loads, which are dependent on the dynamics of the load-sensing signal and the variable displacement pump. A further advantage is that in the case of a grouping of a plurality of valve arrangements (for example as valve disks) in a block via the respective non-return valve, the load-sensing selection is also provided without shuttle valves (known from the prior art). Another advantage is the fact that this solution can be retrofitted during commissioning or even later for individual consumers (for example, excavator functions).
Bei einer bevorzugten Weiterbildung ist der Druckwaagenventilkörper über eine schwache Feder in Schließrichtung beaufschlagt. Damit kann die Druckwaage auch derart verbaut werden, dass die Schließrichtung gegen die Schwerkraft des Druckwaagenventilkörpers gerichtet ist.In a preferred embodiment of the pressure compensator valve body is acted upon by a weak spring in the closing direction. Thus, the pressure compensator can also be installed such that the closing direction is directed against the gravity of the pressure compensator valve body.
Bei einer kompakt bauenden Weiterbildung ist das Rückschlagventil im Druckwaagenventilkörper angeordnet.In a compact design development, the check valve is arranged in the pressure balance valve body.
Wenn der Druckwaagenventilkörper in seiner Öffnungsstellung eine zusätzliche Verbindung von der ersten Verbindungsleitung zur Load-Sensing-Leitung aufsteuert, kann auf diesem Druckmittelströmungspfad der Lastdruck des über die erfindungsgemäße Ventilanordnung versorgten Verbrauchers, der in der ersten Verbindungsleitung ansteht, über die Load-Sensing-Leitung der Ventilanordnung an eine übergeordnete Load-Sensing-Leitung einer übergeordneten Steueranordnung gemeldet werden, so dass diese keine Load-Sensing-Wechselventile benötigt. Insbesondere kann durch die zusätzliche Verbindung die Veränderung des Druckmittelstroms bei Lastübernahme reduziert werden. Das LS-Signal der Ventilanordnung mit dem größten Lastdruck wird dann von der Druckwaage abgegriffen, der Druckabfall über die Druckwaage verringert dadurch nicht das LS-Signal. Die zusätzliche Verbindung kann bei einem oder mehreren Ventilanordnungen (Ventilscheiben) im Block eingesetzt werden.When the pressure compensator valve body opens in its open position an additional connection from the first connecting line to the load-sensing line, the load pressure of the supplied via the valve assembly according to the invention consumer, which is present in the first connection line, via the load-sensing line of this pressure fluid flow path Valve arrangement are reported to a higher-level load sensing line of a higher-level control arrangement, so that this does not require load-sensing shuttle valves. In particular, the change in the pressure medium flow under load transfer can be reduced by the additional connection. The LS signal of the valve assembly with the greatest load pressure is then tapped by the pressure compensator, the pressure drop across the pressure compensator thereby does not reduce the LS signal. The additional connection can be used in one or more valve assemblies (valve discs) in the block.
Bei einer vorrichtungstechnisch einfachen Ausgestaltung kann die zusätzliche Verbindung von einer Längsbohrung und von einer Querbohrung im Druckwaagenventilkörper gebildet sein.In a simple device configuration, the additional connection can be formed by a longitudinal bore and by a transverse bore in the pressure balance valve body.
Der Ausgang der Druckwaage ist vorzugsweise über eine zweite als Zulaufleitung dienende Verbindungsleitung zu einem Eingang eines die Zumessblende umfassenden Hauptventils zurückgeführt.The output of the pressure compensator is preferably returned via a second connecting line serving as a supply line to an input of a main valve comprising the metering orifice.
Vorzugsweise ist die zweite Verbindungsleitung eine verzweigte Brückenleitung, die den Ausgang der Druckwaage mit zwei Eingängen des Hauptventils verbindet. So kann über das Hauptventil wahlweise einer von zwei Arbeitsanschlüssen der Ventilanordnung oder des Hauptventils versorgt werden.Preferably, the second connection line is a branched bridge line which connects the output of the pressure balance with two inputs of the main valve. So can be supplied via the main valve either one of two working ports of the valve assembly or the main valve.
Bei einer bevorzugten Weiterbildung sind das Hauptventil und die Druckwaage in einem gemeinsamen Gehäuse angeordnet. Dann kann der Druckwaagenventilkörper senkrecht zum Hauptschieber angeordnet werden.In a preferred embodiment, the main valve and the pressure compensator are arranged in a common housing. Then, the pressure compensator valve body can be arranged perpendicular to the main spool.
Eine oder einige oder vorzugsweise alle genannten Leitungen der erfindungsgemäßen Ventilanordnung können von jeweiligen Kanälen in dem Gehäuse gebildet sein.One or a few or preferably all said lines of the valve arrangement according to the invention may be formed by respective channels in the housing.
Die erfindungsgemäße Steueranordnung dient zur Versorgung von mindestens zwei hydraulischen Verbrauchern. Sie hat vorzugsweise eine Verstellpumpe oder auch eine Konstantpumpe (z.B. bei Baggerladern) und für jeden Verbraucher eine vorbeschriebene Ventilanordnung, deren jeweilige Load-Sensing-Leitung an eine übergeordnete Load-Sensing-Leitung der Steueranordnung angeschlossen ist. In der übergeordneten Load-Sensing-Leitung und in den einzelnen daran angeschlossenen untergeordneten Load-Sensing-Leitungen wirkt stets der höchste Lastdruck aller von der Pumpe versorgten Verbraucher oder ein davon abgeleiteter Druck. Dies wird über die jeweiligen Rückschlagventile der Ventilanordnungen erreicht oder über eine Verbindung, die vom Druckwaagenventilkörper der Ventilanordnung des lasthöchsten Verbrauchers aufgesteuert wird.The control arrangement according to the invention serves to supply at least two hydraulic consumers. It preferably has a variable displacement pump or a fixed displacement pump (for example in the case of backhoe loaders) and, for each consumer, a prescribed valve arrangement whose respective load-sensing line is connected to a higher-order load-sensing line of the control arrangement. The highest load pressure of all consumers supplied by the pump or a pressure derived therefrom always acts in the higher-level load sensing line and in the individual subordinate load sensing lines connected to it. This is achieved via the respective check valves of the valve arrangements or via a connection which is opened by the pressure balance valve body of the valve arrangement of the highest-load consumer.
Die Steueranordnung kann als Ventilblock ausgebildet sein, in dem die Gehäuse der einzelnen Ventilanordnungen als Ventilscheiben ausgebildet sind und aneinander anliegen.The control arrangement can be designed as a valve block, in which the housings of the individual valve arrangements are designed as valve disks and abut each other.
Bei einer besonders bevorzugten Weiterbildung der erfindungsgemäßen Steueranordnung ist vor oder hinter dem Rückschlagventil jeder Ventilanordnung eine erste Drossel angeordnet, und zwischen der übergeordneten Load-Sensing-Leitung und einer Tankleitung der Steueranordnung ist eine zweite Drossel angeordnet. Dadurch ist der Druck in der Load-Sensing-Leitung niedriger als am Ausgang der jeweiligen Druckwaage, so dass der dem lasthöchsten Verbraucher zugeordnete Druckwaagenventilkörper auch dann in der Öffnungsstellung bleibt, wenn insbesondere in der von der Druckwaage gesteuerten Druckregelverbindung zwischen der ersten Verbindungsleitung und dem Ausgang der Druckwaage entgegen gesetzt wirkende Strömungskräfte auftreten.In a particularly preferred development of the control arrangement according to the invention, a first throttle is arranged in front of or behind the check valve of each valve arrangement, and a second throttle is arranged between the superordinate load sensing line and a tank line of the control arrangement. As a result, the pressure in the load-sensing line is lower than at the outlet of the respective pressure compensator, so that the pressure-compensating valve body associated with the highest load consumer also remains in the open position, especially if the pressure control connection between the first connecting line and the outlet is controlled by the pressure compensator the pressure compensator counteracting acting flow forces occur.
Dabei kann ein Stromregelventil vorgesehen sein, das die zweite Drossel umfasst.In this case, a flow control valve may be provided which comprises the second throttle.
Im Folgenden wird anhand der Figuren ein Ausführungsbeispiel der Erfindung detailliert beschrieben. Es zeigen
-
einen Schaltplan einer Steueranordnung mit mehreren erfindungsgemäßen Ventilanordnungen;Figur 1 -
einen Schaltplan einer der Ventilanordnungen ausFigur 2 ; undFigur 1 -
Figur 3 die Ventilanordnung aus in einer geschnittenen Darstellung.Figur 2
-
FIG. 1 a circuit diagram of a control arrangement with a plurality of valve assemblies according to the invention; -
FIG. 2 a circuit diagram of one of the valve assembliesFIG. 1 ; and -
FIG. 3 the valve assemblyFIG. 2 in a cut view.
Ein Eingangselement 8 verbindet einen Ausgangsanschluss einer Verstellpumpe 10 über Pumpenanschlüsse P mit der Pumpenleitung 2. Das Eingangselement 8 verbindet weiterhin einen Tank T über Tankanschlüsse T mit der Tankleitung 4.An input element 8 connects an output port of a
Wie mit Bezug zur
Die übergeordnete Load-Sensing-Leitung 6 des Eingangselements 8 ist über eine Drossel 16 mit dem Tankanschluss T des Eingangselements 8 verbunden. Diese dient dazu, die Steueranordnung zu entlasten, wenn die Durchflussmenge Null ist. Dies ist z.B. der Fall, wenn alle Ventilanordnungen 1 in ihrer neutralen Position sind.The higher-order load-
Der Druckwaagenventilkörper 24 ist in Öffnungsrichtung über eine Steuerleitung 34 mit dem Druck der ersten Verbindungsleitung 28 beaufschlagt, während er in Schließrichtung über eine untergeordnete Load-Sensing-Leitung 35 mit dem Druck der übergeordneten Load-Sensing-Leitung 6 beaufschlagt ist. Ebenfalls in Schließrichtung wirkt eine vergleichsweise schwache Feder 36.The pressure
Bei der Steueranordnung gemäß
Erfindungsgemäß ist zwischen dem Ausgang 29 der Druckwaage 22 bzw. der zweiten Verbindungsleitung 30 und der untergeordneten Load-Sensing-Leitung 35 ein Entlastungskanal 40 vorgesehen. In diesem sind ein durch eine Feder vorgespanntes Rückschlagventil 42 und eine Drossel 44 vorgesehen. Die Öffnungsrichtung des Rückschlagventils 42 ist vom Ausgang 29 bzw. von der zweiten Verbindungsleitung 30 zur Load-Sensing-Leitung 35 gerichtet.According to the invention, a
Wenn im Betrieb der erfindungsgemäßen Ventilanordnung 1 ihr Hauptventil 18 in die in
Vom Pumpenanschluss P strömt das Druckmittel über die Zumessblende 26 und über die erste Verbindungsleitung 28 zur Druckwaage 22, deren Druckwaagenventilkörper 24 in
Der Druckwaagenventilkörper 24 ist etwa kreiszylindrisch ausgebildet und hat bei diesem Ausführungsbeispiel einen exzentrisch einen Kanal, der die zusätzliche Verbindung 39 bildet. Ein Querbohrungsabschnitt der Verbindung 39 ist derart angeordnet, dass bei einer maximalen Öffnung der Druckwaage 22 der erste Verbindungskanal 28 und damit der Eingang der Druckwaage 22 mit der untergeordneten Load-Sensing-Leitung 35 verbunden wird. Dies geschieht, wenn die betroffene Ventilanordnung 1 den lasthöchsten Verbraucher versorgt. Dies ist eine Option. Das Rückschlagventil 42 ist ausreichend für die Meldung des LS-Signals. Zusammenfassend ist festzustellen, dass der Lastdruck der ersten Verbindungsleitung 28 in die Load-Sensing-Leitung 35 gemeldet wird, so dass dieser Lastdruck als höchster Lastdruck der gesamten Steueranordnung (vgl.
Konzentrisch im Druckwaagenventilkörper 24 ist das federvorgespannte Rückschlagventil 42 angeordnet, dessen Eingang durch eine Querbohrung mit dem Ausgang 29 der Druckwaage 22 und dessen Ausgang in einem Load-Sensing-Druckraum angeordnet ist, der zwischen der Stirnseite des Druckwaagenventilkörpers 24 und der Verschlussschraube 48 gebildet ist, und der mit der untergeordneten Load-Sensing-Leitung 35 verbunden ist. Dabei ist der Eingang der Querbohrung derart am Druckwaagenventilkörper 24 angeordnet, dass die Verbindung über den Entlastungskanal 40 und über das Rückschlagventil 42 unabhängig von der Position des Druckwaagenventilkörpers 24 stets gegeben ist.Concentric in the pressure
Offenbart ist eine Ventilanordnung mit einem Hauptventil und einer Individualdruckwaage die gemeinsam zur Versorgung eines Verbrauchers dienen, wobei mehrere derartige Ventilanordnungen zur Versorgung mehrere Verbraucher mit lastdruckunabhängiger Durchflussverteilung vorgesehen sind. Dem entsprechend sind die Individualdruckwaagen stromab der Hautventils angeordnet und von einem Steuerdruck einer übergeordneten Load-Sensing-Kanal in Schließrichtung beaufschlagt, während sie vom hinter der Hauptventil abgegriffene Versorgungsdruck in Öffnungsrichtung beaufschlagt sind. Dabei ist im Druckwaagenventilschieber zur Abfuhr von Leckage des Hauptventils - insbesondere wenn dies als Schieberventil ausgeführt ist - ein Rückschlagventil vorgesehen, dessen Öffnungsrichtung vom Ausgang der Druckwaage zum Load-Sensing-Kanal gerichtet ist, und das unabhängig von der Position des Druckwaagenventilkörpers stets verbunden ist.Disclosed is a valve arrangement with a main valve and an individual pressure compensator which together serve to supply a consumer, wherein a plurality of such valve arrangements are provided for supplying a plurality of consumers with load pressure-independent flow distribution. Accordingly, the individual pressure compensators are arranged downstream of the skin valve and acted upon by a control pressure of a parent load-sensing channel in the closing direction, while they are acted upon by the tapped behind the main valve supply pressure in the opening direction. It is in the pressure compensator valve spool for removal leakage of the main valve - in particular when this is designed as a slide valve - a check valve provided, the opening direction of which is directed from the output of the pressure compensator to the load-sensing channel, and which is always connected regardless of the position of the pressure compensator valve body.
- 11
- Ventilanordnungvalve assembly
- 22
- Pumpenleitungpump line
- 44
- Tankleitungtank line
- 66
- (übergeordnete) Load-Sensing-Leitung(higher-level) load-sensing line
- 88th
- Eingangselementinput element
- 1010
- Verstellpumpevariable
- 1212
- Verschlusselementclosure element
- 1616
- Drosselthrottle
- 1818
- Hauptventilmain valve
- 2020
- Hauptschiebermain slide
- 2222
- Druckwaagepressure compensator
- 2424
- DruckwaagenventilkörperPressure balance valve body
- 2626
- Zumessblendemetering orifice
- 2828
- erste Verbindungsleitungfirst connection line
- 2929
- Ausgangoutput
- 3030
- zweite Verbindungsleitung, Brückenkanalsecond connecting line, bridge channel
- 3232
- LasthalteventilLoad-holding valve
- 3434
- Steuerleitungcontrol line
- 3535
- (untergeordnete) Load-Sensing-Leitung(subordinate) load-sensing line
- 3636
- Federfeather
- 3838
- Öffnungsstellungopen position
- 3939
- Verbindungconnection
- 4040
- Entlastungskanalrelief channel
- 4242
- Rückschlagventilcheck valve
- 4444
- Drosselthrottle
- 4646
- DruckregelverbindungPressure control connection
- 4848
- VerschlussschraubeScrew
- 5050
- Gehäusecasing
- A, BA, B
- Arbeitsanschlussworking port
- LSLS
- Load-Sensing-AnschlussLoad sensing connection
- PP
- Pumpenanschlusspump connection
- TT
- Tank, TankanschlussTank, tank connection
Claims (11)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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DE201310220748 DE102013220748A1 (en) | 2013-10-15 | 2013-10-15 | valve assembly |
Publications (2)
Publication Number | Publication Date |
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EP2871370A1 true EP2871370A1 (en) | 2015-05-13 |
EP2871370B1 EP2871370B1 (en) | 2019-02-27 |
Family
ID=51564528
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP14185252.5A Active EP2871370B1 (en) | 2013-10-15 | 2014-09-18 | Valve assembly |
Country Status (3)
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EP (1) | EP2871370B1 (en) |
CN (1) | CN104564875A (en) |
DE (1) | DE102013220748A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR3057309A1 (en) * | 2016-10-10 | 2018-04-13 | Robert Bosch Gmbh | HYDRAULIC CONTROL CIRCUIT |
EP3771322A1 (en) * | 2019-07-31 | 2021-02-03 | PÖTTINGER Landtechnik GmbH | Agricultural machine |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102018204854A1 (en) * | 2018-03-29 | 2019-10-02 | Robert Bosch Gmbh | Valve assembly with a main spool and two spools |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5305789A (en) | 1992-04-06 | 1994-04-26 | Rexroth-Sigma | Hydraulic directional control valve combining pressure compensation and maximum pressure selection for controlling a feed pump, and multiple hydraulic control apparatus including a plurality of such valves |
DE19831595A1 (en) * | 1998-07-14 | 2000-01-20 | Mannesmann Rexroth Ag | Hydraulic switch to control consumer by non-load-dependent flow distribution, with control device supplying extra load in closing direction when limit of regulating piston of pressure meter is exceeded |
EP2078868A2 (en) * | 2008-01-09 | 2009-07-15 | Husco International, Inc. | Hydraulic control valve system with isolated pressure compensation |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0758082B2 (en) * | 1990-06-22 | 1995-06-21 | 株式会社ゼクセル | Hydraulic control valve device |
-
2013
- 2013-10-15 DE DE201310220748 patent/DE102013220748A1/en not_active Withdrawn
-
2014
- 2014-09-18 EP EP14185252.5A patent/EP2871370B1/en active Active
- 2014-10-14 CN CN201410539735.1A patent/CN104564875A/en active Pending
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5305789A (en) | 1992-04-06 | 1994-04-26 | Rexroth-Sigma | Hydraulic directional control valve combining pressure compensation and maximum pressure selection for controlling a feed pump, and multiple hydraulic control apparatus including a plurality of such valves |
DE19831595A1 (en) * | 1998-07-14 | 2000-01-20 | Mannesmann Rexroth Ag | Hydraulic switch to control consumer by non-load-dependent flow distribution, with control device supplying extra load in closing direction when limit of regulating piston of pressure meter is exceeded |
EP2078868A2 (en) * | 2008-01-09 | 2009-07-15 | Husco International, Inc. | Hydraulic control valve system with isolated pressure compensation |
Non-Patent Citations (1)
Title |
---|
"LUDV-STEUERBLOCK IN SCHEIBENBAUWEISE (RD64125/02.11)", FIRMENSCHRIFT BOSCH REXROTH AG, 31 March 2011 (2011-03-31), LOHR AM MAIN, XP002737941 * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR3057309A1 (en) * | 2016-10-10 | 2018-04-13 | Robert Bosch Gmbh | HYDRAULIC CONTROL CIRCUIT |
EP3771322A1 (en) * | 2019-07-31 | 2021-02-03 | PÖTTINGER Landtechnik GmbH | Agricultural machine |
Also Published As
Publication number | Publication date |
---|---|
EP2871370B1 (en) | 2019-02-27 |
DE102013220748A1 (en) | 2015-05-07 |
CN104564875A (en) | 2015-04-29 |
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