EP0733743B1 - Flow distribution device, independent of the load pressure, for control valves in mobile working machines - Google Patents
Flow distribution device, independent of the load pressure, for control valves in mobile working machines Download PDFInfo
- Publication number
- EP0733743B1 EP0733743B1 EP96102897A EP96102897A EP0733743B1 EP 0733743 B1 EP0733743 B1 EP 0733743B1 EP 96102897 A EP96102897 A EP 96102897A EP 96102897 A EP96102897 A EP 96102897A EP 0733743 B1 EP0733743 B1 EP 0733743B1
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- European Patent Office
- Prior art keywords
- duct
- pressure
- compensator
- spring
- running
- Prior art date
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
- F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2221—Control of flow rate; Load sensing arrangements
- E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2296—Systems with a variable displacement pump
-
- 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
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
-
- 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
- F15B2211/3054—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and output member
-
- 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
- F15B2211/35—Directional control combined with flow control
- F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in control
-
- 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
-
- 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
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
-
- 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
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/78—Control of multiple output members
Definitions
- a device for load flow independent flow distribution for a spool valve for mobile construction and work machines with at least two downstream consumers is operatively connected and by at least one controllable Delivery pump provided flow according to the load pressure independent Principle of correspondingly controllable piston-type compensators one or more the consumer makes available and the highest of those due to the consumer Press the regulator of the feed pump is reported, the compensators on the one hand a pressure chamber that can be connected to the respective consumer and, on the other hand, one Include spring space, the consumer can be connected to the spring space via corresponding channels are and in the connecting line at least one occupying two defined positions Closure element is used.
- the single figure shows a schematic diagram of the schematic structure of a controller with a any number of consumers; in this example designed as a cylinder 1,2,3.
- the Cylinders 1,2,3 are controlled by a spool valve, which works on the principle of flow pressure-independent flow distribution is built, of which only the control openings 4,5,6 are shown. These control openings 4, 5, 6 can be changed by the driver.
- the compensator 10 designed as a piston, the slide section of which is assigned to the cylinder 1, is activated so that its oil flow can flow to this cylinder 1.
- the cylinder pressure p z1 which has to serve as an LS signal, transports itself through transverse channels 11 in the compensator piston 10 by lifting the closure element 12, which is spherical here, via line 13, on which the other compensator pistons 14, 15 are also connected in parallel , to pump controller 8.
- geometrically differently shaped closure elements, such as cones can also be used. This pressure acts via a longitudinally extending connecting channel 16 in the spring chamber 17.
- the spherical closure elements 30, 31 are pressed onto their seats 28, 29 by the higher pressure p z1 controlled via the line 13 pressed so that oil flow from line 13 to cylinders 2 and 3 is prevented.
- the spherical closure element 12 is lifted from its valve seat 32 as a result of the higher pressure prevailing in this compensator piston 10 and bears against a stop 33 of a closure element 34 inserted from above into the compensator piston 10, which at the same time guides the spring 18 in the spring chamber 17.
- each compensator piston 10, 14, 15 is provided with channels 37, 38, 39 running in the longitudinal direction and in each case two channels 11, 41, 42, 43, 44, 45 running transversely thereto.
- channels 16, 20, 21 are also incorporated in the longitudinal direction for connecting the cylinders 1, 2, 3 with the associated spring chamber 17, 22, 23.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
- Operation Control Of Excavators (AREA)
Abstract
Description
Die Erfindung betrifft eine Einrichtung zur lastdruckunabhängigen Durchflußverteilung bei einem Steuerschieber für mobile Bau- und Arbeitsmaschinen.The invention relates to a device for load pressure independent flow distribution at a Control spool for mobile construction and work machines.
Bei Steuerschiebem nach dem Prinzip der lastdruckunabhängigen Durchflußverteilung (LUDV) gibt es unterschiedliche Möglichkeiten des Abgriffes und der Weiterleitung des sogenannten Load-Sensing (LS)-Signals . Einerseits gibt es die Möglichkeit, dieses Signal über ein aufwendiges in die Schiebersektionen integriertes System von Meldeleitungen das Load-Sensing-Signal an den Pumpenregler weiterzuleiten. Andererseits besteht die Möglichkeit, in die Kompensatorkolben weitere Kolben einzubauen, die mit einer relativ schwachen Feder ausgerüstet sind. Die Kompensatorkolben können auch so ausgebildet sein, daß sie über eine Steueröffnung das Load-Sensing-Signal weiterleiten. Die erstgenannte Ausführung ist aufwendig, während die beiden letztgenannten bezüglich der Signalabgabe derart empfindlich sind, daß über die Steuerkanten bei den kleinen Ölströmen ein druckgenaues Weiterleiten des Load-Sensing-Signals nicht immer gewährleistet ist. Dies bewirkt eine ungenaue Ansteuerung des Pumpenreglers, was sich wiederum negativ auf die Gesamtsteuerung, d.h. die Ansteuerung einzelner oder mehrerer Verbraucher auswirkt.With spool valves based on the principle of flow pressure independent flow distribution (LUDV) there are different ways of tapping and forwarding the so-called Load sensing (LS) signal. On the one hand, there is the possibility of using a complex signal system of signaling lines integrated in the slide sections, the load-sensing signal forward to the pump controller. On the other hand, there is the possibility in the compensator piston to install additional pistons equipped with a relatively weak spring are. The compensator pistons can also be designed so that they have a control opening forward the load sensing signal. The first version is complex, while the latter two are so sensitive to signaling that over the control edges with the small oil flows a pressure-accurate forwarding of the load-sensing signal is not always guaranteed. This causes inaccurate activation of the pump controller which in turn negatively affects overall control, i.e. the control of individual or multiple consumers.
Der Stand der Technik is beispeilsweise durch die US-A-5067389 repräsentiert.The prior art is represented, for example, by US-A-5067389.
Ziel des Erfindungsgegenstandes ist es, eine Einrichtung zur lastdruckunabhängigen Durchflußverteilung bei einem Steuerschieber für mobile Bau- und Arbeitsmaschinen dahingehend weiterzubilden, daß sich eine kostengünstige, einfache und störungsunanfällige Lösung ergibt, bei welcher der benötigte Ölstrom zuverlässig und druckgenau an den Pumpenregler weitergeleitet wird.The object of the invention is to provide a device for flow distribution independent of load pressure with a spool for mobile construction and work machines to further develop that there is a cost-effective, simple and trouble-free solution, in which the required oil flow is reliably and accurately passed on to the pump controller becomes.
Dieses Ziel wird erreicht durch eine Einrichtung zur lastdruckunabhängigen Durchflußverteilung bei einem Steuerschieber für mobile Bau- und Arbeitsmaschinen, der mit mindestens zwei nachgeschalteten Verbrauchern in Wirkverbindung steht und den durch mindestens eine regelbare Förderpumpe zur Verfügung gestellten Förderstrom nach dem lastdruckunabhängigen Prinzip über entsprechend ansteuerbare kolbenartige Kompensatoren einem oder mehreren der Verbraucher zur Verfügung stellt und der jeweils höchste der an den Verbrauchem anstehenden Drücke dem Regler der Förderpumpe gemeldet wird, wobei die Kompensatoren einerseits einen mit dem jeweiligen Verbraucher verbindbaren Druckraum und andererseits einen Federraum beinhalten, die Verbraucher über entsprechende Kanäle mit dem Federraum verbindbar sind und in die Verbindungsleitung mindestens ein zwei definierte Stellungen einnehmendes Verschlußelement eingesetzt ist. This goal is achieved by a device for load flow independent flow distribution for a spool valve for mobile construction and work machines, with at least two downstream consumers is operatively connected and by at least one controllable Delivery pump provided flow according to the load pressure independent Principle of correspondingly controllable piston-type compensators one or more the consumer makes available and the highest of those due to the consumer Press the regulator of the feed pump is reported, the compensators on the one hand a pressure chamber that can be connected to the respective consumer and, on the other hand, one Include spring space, the consumer can be connected to the spring space via corresponding channels are and in the connecting line at least one occupying two defined positions Closure element is used.
Vorteilhafte Weiterbildungen des Erfindungsgegenstandes sind den Unteransprüchen zu entnehmen. Neben kugelförmigen Verschlußelementen können auch geometrisch anders geformte Elemente, wie z.B. Kegel, Verwendung finden.Advantageous further developments of the subject matter of the invention can be found in the subclaims. In addition to spherical closure elements, geometrically different shapes can also be used Elements such as Cone, find use.
Der Erfindungsgegenstand ist anwendbar für eine beliebige Anzahl von Verbrauchem, die über einen nach dem Prinzip der lastdruckunabhängigen Durchflußverteilung arbeitenden Steuerschieber angesteuert werden. Wesentlicher Vorteil eines kugel- oder kegelförmigen Verschlußelementes gegenüber einem Kolben ist, daß das kugel- oder kegelförmige Verschlußelement lediglich zwei definierte Stellungen kennt, nämlich 'offen' oder'geschlossen', während bei dem Einsatz eines Kolbens infolge der sich ständig ändernden Richtungswechsel sich lediglich ein sogenanntes Anschnäbeln an den Steuerkanten einstellt, was sich letztendlich in der ungünstigen Abgabe des benötigten Ölstromes widerspiegelt. Dieser Nachteil wird durch das erfindungsgemäße Verschlußelement wirksam behoben, da es nun möglich ist, durch den durch die Kugel- oder Kegelstellung "offen" freigegebenen Querschnitt einen ausreichenden Ölstrom an den Pumpenregler sowie die weiteren Kompensatoren abzugeben.The subject of the invention is applicable to any number of consumers who Via a flow distribution that works according to the principle of load pressure independent Control spool can be controlled. Significant advantage of a spherical or conical closure element compared to a piston is that the spherical or conical closure element knows only two defined positions, namely 'open' or 'closed', while when using a piston due to the constantly changing direction changes only a so-called snapping on the control edges, which is ultimately in the reflects unfavorable delivery of the required oil flow. This disadvantage is caused by the Closure element according to the invention effectively eliminated, since it is now possible by a sufficient cross-section released through the ball or cone position "open" Deliver oil flow to the pump controller and the other compensators.
Der Erfindungsgegenstand ist anhand eines Ausführungsbeispieles in der Zeichnung dargestellt und wird wie folgt beschrieben.The object of the invention is shown in the drawing using an exemplary embodiment and is described as follows.
Die einzige Figur zeigt als Prinzipskizze den schematischen Aufbau einer Steuerung mit einer
beliebigen Anzahl von Verbrauchern; in diesem Beispiel ausgebildet als Zylinder 1,2,3. Die
Zylinder 1,2,3 werden über einen Steuerschieber angesteuert, der nach dem Prinzip der
lastdruckunabhängigen Durchflußverteilung aufgebaut ist, von dem lediglich die Steueröffnungen
4,5,6 dargestellt sind. Diese Steueröffnungen 4,5,6 sind durch den Fahrer veränderbar.The single figure shows a schematic diagram of the schematic structure of a controller with a
any number of consumers; in this example designed as a
Unter der Annahme, daß der Zylinder 1 dem höchsten Lastdruck pz1 unterworfen ist, wird die
Verstellpumpe 7 den Förderstrom mit einem um den Load-Sensing-Differenzdruck ΔpLS ihres
Reglers 8 höheren Druck ausgeben. Es gilt: pp = pz1 + ΔpLS.Assuming that the cylinder 1 is subjected to the highest load pressure p z1 , the variable displacement pump 7 will output the delivery flow with a pressure higher by the load-sensing differential pressure Δp LS of its
Durch den um den Steuerdruckabfall in der Steueröffnung 4 verminderten Pumpendruck, der
im Druckraum 9 wirkt, wird der als Kolben ausgebildete Kompensator 10, dessen Schiebersektion
dem Zylinder 1 zugeordnet ist, aufgesteuert, so daß sein Ölstrom diesem Zylinder 1 zufließen
kann. Gleichzeitig pflanzt sich der Zylinderdruck pz1, der als LS-Signal zu dienen hat, über
quer verlaufende Kanäle 11 im Kompensatorkolben 10 unter Anheben des hier kugelförmig
ausgebildeten Verschlußelementes 12 über die Leitung 13, an welcher in Parallelschaltung
auch die übrigen Kompensatorkolben 14,15 liegen, zum Pumpenregler 8 fort. Wie bereits dargelegt,
können auch geometrisch anders geformte Verschlußelemente, wie z.B. Kegel, zur
Anwendung gelangen. Dieser Druck wirkt über einen in Längsrichtung verlaufenden Verbindungskanal
16 auch im Federraum 17. Damit wirken der Lastdruck pz1 und der Äquivalenzdruck
der Feder 18 dem Druck im Raum 9 entgegen, so daß sich der Kompensatorkolben 10
selbsttätig so einstellt, daß über die sich bildende Drosselstelle 19 der Förderstrom auf den
Lastdruck pz1 vermindert wird. Der Druckabfall an der Drosselstelle 19 entspricht hierbei dem
Äquivalenzdruck der Feder 18 (dieser ist relativ gering, 1 bis 8 bar).Due to the reduced pump pressure in the control opening 4 pump pressure, which acts in the
Der Lastdruck Pz1 des Zylinders 1 wird über die Leitung 13 auch den weiteren Kompensatorkolben
14,15 zugeführt. Über die in Längsrichtung verlaufenden Verbindungskanäle 20,21 steht
dieser Druck auch in den Federräumen 22,23 der Kompensatoren 14 und 15 an. In den Druckräumen
24,25 wirkt der gleiche um den Druckabfall durch die Steueröffnungen 5,6 verminderte
Pumpendruck pp, wobei entsprechend dem LUDV-Prinzip die Druckabfälle in den Steueröffnungen
4,5,6 aller Verbraucher 1,2,3 gleich sind. Dadurch wird der Druck in den Druckräumen
24,25 durch die sich nach dem Druckwaagenprinzip einstellenden Drosselöffnungen 26,27 auf
die gegenüber dem Druck pz1 im Zylinder 1 niedriger liegenden Drücke pz2 bzw. pz3 in den Zylindern
2,3 vermindert. Da in den zu den Kugelsitzen 28,29 führenden quer verlaufenden Kanälen
42,44 nur die Zyliderdrücke pz2 und pz3 herrschen, werden die kugelförmigen Verschlußelemente
30,31 durch den über die Leitung 13 eingesteuerten höheren Druck pz1 auf ihre Sitze
28,29 gedrückt, so daß ein Ölfluß von der Leitung 13 zu den Zylindem 2 und 3 verhindert wird.
Das kugelförmige Verschlußelement 12 ist in diesem Beispiel infolge des in diesem Kompensatorkolben
10 herrschenden höheren Druckes von seinem Ventilsitz 32 abgehoben und liegt an
einem Anschlag 33 eines von oben in den Kompensatorkolben 10 eingeführten Abschlußelementes
34 an, das gleichzeitig im Federraum 17 die Feder 18 führt. Das kugelförmige Verschlußelement
12,30,31 ist somit in Abhängigkeit des sich am jeweiligen Kompensator
10,14,15 einstellenden höheren Druckes zwischen seinen beiden definierten Stellungen
32,33;28,35;29,36 hin und her bewegbar. Jeder Kompensatorkolben 10,14,15 ist - wie bereits
dargelegt - mit in Längsrichtung verlaufenden Kanälen 37,38,39 sowie jeweils zwei quer dazu
verlaufenden Kanälen 11,41;42,43;44,45 versehen. Im jeweiligen Abschlußelement 34,46,47
sind ebenfalls in Längsrichtung verlaufende Kanäle 16,20,21 zur Verbindung der Zylinder 1,2,3
mit der zugehörigen Federkammer 17,22,23 eingearbeitet.The load pressure P z1 of the cylinder 1 is also fed to the further compensator pistons 14, 15 via the
Die Vorteile des Erfindungsgegenstandes sind durch folgende Merkmale gekennzeichnet:
- die Querschnitte in den Load-Sensing-
11,42,44 sowie die von denMeldeleitungen 12,30,31kugelförmigen Verschlußelementen 37,38,39 können ohne nennenswerten Druckabfall den durch denfreigegebenen Querschnitte Pumpenregler 8 und/oder durch dieEntspannungsblende 48 in denTank 49 abfließenden Ölstrom durchleiten. - die Signalgabe ist absolut präzise und zuverlässig, da das
12,30,31 lediglich zweikugelförmige Verschlußelement 32,33;28,35 sowie 29,36 (offen - geschlossen) aufweist und der LS-Strom nicht über Steuerkanten sich einregelnder Kolben abfließt.definierte Stellungen - die Leitungsführung ist stark vereinfacht.
- the cross-sections in the load-
11, 42, 44 and thesensing signal lines 37, 38, 39 released by thecross-sections 12, 30, 31 can be reduced by thespherical closure elements pump regulator 8 and / or through theexpansion orifice 48 without significant pressuredrop Pass tank 49 through the flowing oil flow. - the signaling is absolutely precise and reliable, since the
12, 30, 31 only has twospherical closure element 32, 33, 28, 35 and 29, 36 (open - closed) and the LS current does not flow out via control edges of the regulating pistons .defined positions - the routing is greatly simplified.
Claims (9)
- Device for load-independent flow distribution in a control valve for mobile construction and working machines, which valve is in operative connection with at least two downstream loads (1, 2, 3) and, in accordance with the load-independent principle, by way of suitably activatable piston-like compensators (10,14,15) makes available to one or more of the loads (1, 2, 3) the delivery flow provided by at least one controllable delivery pump (7), and each time the highest of the pressures present at the loads (1 or 2 or 3) is relayed to the controller (8) of the delivery pump (7), wherein the compensators (10, 14, 15) at one side contain a pressure chamber (9, 24, 25) which is arranged to be connected to the relevant load (1, 2, 3) and at the other side contain a spring chamber (17, 22, 23), the loads are arranged to be connected by way of corresponding ducts (11, 37, 16; 42, 38, 20; 44, 39, 21) to the spring chamber (17, 22, 23) and at least one sealing element (12, 30, 31) occupying just two defined positions (32, 33; 28, 35; 29, 36) is inserted in the connecting line (37, 16; 38, 20; 39, 21).
- Device according to claim 1, characterised in that the sealing element (12, 30, 31) is a sphere.
- Device according to claim 1, characterised in that the sealing element has a conical seating surface.
- Device according to one or more of claims 1 to 3, characterised in that each compensator (10, 14, 15) contains at least one longitudinally running duct (37, 16; 38, 20; 39, 21) and at least two ducts (11, 41; 42, 43; 44, 45) running transversely thereto, wherein the longitudinally running closeable duct (37, 16; 38, 20; 39, 21) connects the loads (1, 2, 3) and the respective spring chambers (17, 22, 23) to one another, when one of the compensators (10 or 14 or 15) is displaced, one of the transversely running ducts (11 or 42 or 44) transmits the pressure signal present at the compensator to the longitudinally running duct (37 or 38 or 39), and a further transversely running duct (41 or 43 or 45) transmits this signal via a line (13) on the one hand to the spring chambers (22, 23 or 17, 22 or 17, 23) of the further compensators (14, 15; 10, 14; 10, 15) and on the other hand to the controller (8) of the pump (7).
- Device according to one or more of claims 1 to 4, characterised in that the sealing element (12, 30, 31) is inserted between the ducts (11, 41; 42, 43; 44, 45) running transversely to the longitudinal duct (37, 38, 39).
- Device according to one or more of claims 1 to 5, characterised in that the sealing element (12, 30, 31) is movable between a cylinder chamber side valve seat (32, 28, 29) and a spring chamber side stop (33, 35, 36).
- Device according to one or more of claims 1 to 6, characterised in that the stop (33, 35, 36) is formed by an end face of a closing element (34, 46, 47) inserted in the compensator (10, 14, 15), which closing element serves at the same time as guide means for the spring (18).
- Device according to one or more of claims 1 to 7, characterised in that the duct (16, 20, 21) leading to the spring chamber (17, 22, 23) runs through the closing element (34, 46, 47).
- Device according to one or more of claims 1 to 7, characterised in that the duct leading to the spring chamber (17, 22, 23) runs inside the wall of the compensator (10, 14, 15).
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19510408 | 1995-03-24 | ||
DE19510408 | 1995-03-24 | ||
DE19520451A DE19520451C1 (en) | 1995-03-24 | 1995-06-03 | Hydraulic system |
DE19520451 | 1995-06-03 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0733743A1 EP0733743A1 (en) | 1996-09-25 |
EP0733743B1 true EP0733743B1 (en) | 1999-06-30 |
Family
ID=26013593
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP96102897A Expired - Lifetime EP0733743B1 (en) | 1995-03-24 | 1996-02-27 | Flow distribution device, independent of the load pressure, for control valves in mobile working machines |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0733743B1 (en) |
AT (1) | ATE181755T1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR3057309B1 (en) * | 2016-10-10 | 2018-11-16 | Robert Bosch Gmbh | HYDRAULIC CONTROL CIRCUIT |
CN109869362B (en) * | 2019-01-31 | 2021-01-26 | 中国铁建重工集团股份有限公司 | Hydraulic system for simulating rock drilling load and simulation test method of rock drilling load |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1990009528A1 (en) * | 1989-02-20 | 1990-08-23 | Hitachi Construction Machinery Co., Ltd. | Hydraulic circuit for working machines |
KR940008823B1 (en) * | 1990-07-05 | 1994-09-26 | 히다찌 겐끼 가부시기가이샤 | Hydraulic drive system and valve device |
US5067389A (en) * | 1990-08-30 | 1991-11-26 | Caterpillar Inc. | Load check and pressure compensating valve |
JP2579202Y2 (en) * | 1992-04-10 | 1998-08-20 | 株式会社小松製作所 | Operating valve with pressure compensation valve |
-
1996
- 1996-02-27 AT AT96102897T patent/ATE181755T1/en not_active IP Right Cessation
- 1996-02-27 EP EP96102897A patent/EP0733743B1/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
EP0733743A1 (en) | 1996-09-25 |
ATE181755T1 (en) | 1999-07-15 |
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