EP1386084B1 - Hydraulic control assembly for controlling the direction and speed of a single-action hydraulic consumer and a directional control valve therefor - Google Patents

Hydraulic control assembly for controlling the direction and speed of a single-action hydraulic consumer and a directional control valve therefor Download PDF

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Publication number
EP1386084B1
EP1386084B1 EP02742885A EP02742885A EP1386084B1 EP 1386084 B1 EP1386084 B1 EP 1386084B1 EP 02742885 A EP02742885 A EP 02742885A EP 02742885 A EP02742885 A EP 02742885A EP 1386084 B1 EP1386084 B1 EP 1386084B1
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EP
European Patent Office
Prior art keywords
chamber
control
consumer
spool
pressure
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EP02742885A
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German (de)
French (fr)
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EP1386084A2 (en
Inventor
Peter BÜTTNER
Tatu Miikkulainen
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Bosch Rexroth AG
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Bosch Rexroth AG
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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
    • 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
    • F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
    • F15B2013/006—Modular components with multiple uses, e.g. kits for either normally-open or normally-closed valves, interchangeable or reprogrammable manifolds

Definitions

  • the invention is based on a hydraulic control arrangement which is provided for controlling a single-acting hydraulic consumer, in particular a single-acting hydraulic cylinder, in terms of direction and speed and having the features of the preamble of patent claim 1.
  • Such a hydraulic control arrangement is known for example from DE 196 31 803 and comprises a directional control valve which in a valve housing a piston bore with a central inlet chamber, the pressure medium from a pressure medium source can be supplied, two adjacent consumer chambers and a drain chamber, via the pressure medium to a tank is drained, has. Usually there are two drainage chambers.
  • the directional control valve also has a control piston which is displaceable by an arbitrary predetermined driving force from a central position of axially in a first and in an opposite second direction and the first Feinumblenuten for als Strukturn a connection between the inlet chamber and a first of the two consumer chambers at a Displacement from the center position in a first direction and provided with second fine control grooves for controlling the connection between the first consumer chamber and the discharge chamber in a shift from the central position in the second direction.
  • the control piston acted upon by the load pressure measuring piston cooperate in such a way that upon displacement of the control piston from the center position one of the driving force opposing and increasing with increasing load pressure compensating force is exerted on the control piston.
  • the known hydraulic control arrangement is used to control a double-acting hydraulic consumer, for example a differential cylinder and is a so-called load sensing control.
  • a variable or the bypass connected to a constant pump pressure compensator regulated so that adjusts a pump pressure in a pump line in which a pump pressure to a certain pressure difference, the so-called pump ⁇ p, above the highest load pressure all at the same time actuated hydraulic consumer is located.
  • the pressure medium flows via proportionally adjustable metering orifices formed by control grooves on the control piston to one or the other port of the hydraulic consumer.
  • the invention has the object of providing a hydraulic control arrangement niezuentwikkeln with the features of the preamble of claim 1 so that even with a single-acting hydraulic load, especially in a single-acting hydraulic cylinder at a given acting on the control piston driving force with simple means a strong increase the lowering speed of the hydraulic consumer is avoided with increasing load pressure.
  • the desired object is achieved according to the invention that in the hydraulic control arrangement with the features of the preamble of claim 1 of the volumetric flask is acted upon by a displacement of the control piston in the second direction of the prevailing pressure in the first consumer chamber. So it is the volumetric flask, which is applied in the use of the directional control valve for the operation of a double-acting hydraulic consumer with the pending in the second load chamber load pressure when lowering connected to the first load chamber and thus acted upon lowering with the load pressure. The compensation force generated thereby increases with increasing load pressure and shifts the control piston in the sense of a reduction of the flow cross-section from the first consumer chamber to the drain chamber.
  • control piston on one of the message of Lastdrukkes of the hydraulic consumer serving axial bore with a displacement of the control piston in the first direction via a first transverse bore to the first consumer chamber and a displacement of the control piston in the second direction via a second transverse bore is opened to the second consumer chamber.
  • the pressure from the axial bore is passed through a third transverse bore in a load reporting chamber.
  • the volumetric flask is guided in the control piston and exposed in the interior of the control piston to the pending in the axial bore pressure and the outside of a stop of the valve housing can be supported.
  • the invention is also embodied in a directional control valve according to claim 9.
  • a variable displacement pump 10 can supply a plurality of hydraulic consumers with pressure medium, usually mineral oil, via a directional control valve block 11.
  • the diagram explicitly shows only a single-acting hydraulic cylinder 12 and a directional valve disc 13, with which the pressure medium paths between the hydraulic cylinder, the variable displacement pump and a tank 14 are controllable.
  • the variable displacement pump is current demand-controlled and has a load-sensing controller 15, which is reported via a terminal LS of an input element 16 of the directional control valve block 11, the highest load pressure of all simultaneously controlled hydraulic consumers.
  • the variable displacement pump sucks pressure medium from the tank 14 and it is in a leading to a pump port P of the input element pressure line 17 from. It promotes in each case so much pressure medium that in the pressure line 17 to the pump ⁇ p, which is usually set to a value between ten and twenty bar, above the highest load pressure lying pump pressure is generated.
  • the directional control valve disc 13 comprises a proportionally adjustable directional control valve 20 and an upstream of a metering orifice 21 of the directional valve pressure compensator 22 which is connected at its input to the pump port P.
  • the hydraulic cylinder can be actuated for the extension of the piston rod independent of the load pressure.
  • a piston bore 31 passes through a valve housing 30, in which a control piston 32 is axially movable.
  • the length of the control piston 32 coincides with the length of the piston bore 31 from one end face 33 to the other end face 34 of the valve housing 30.
  • the piston bore 31 is surrounded by five axially spaced control chambers.
  • the fluidic connections under the three control chambers are controlled by the control piston 32.
  • the middle control chamber 35 of the five control chambers is the inlet chamber. This flows pressure medium via a channel 36 from the only in Figure 2 shown in circuit diagram pressure compensator 22 ago.
  • On both sides of the inlet chamber is in each case a consumer chamber 38 and 39, each of which is connected to a located at the end of a consumer channel 40 and 41, consumer connection threaded bore 42 and 43 of the valve disc.
  • the two consumer channels 40 and 41 are substantially parallel to each other and perpendicular to the piston bore 31.
  • Each consumer chamber 38 and 39 is followed by a drain chamber 44 and 45, which is open to one of two passing through the valve housing 30 tank channels 46.
  • the control piston 32 assumes a central position, from which it is in a first direction and a second thereto opposite due to two centering springs 47 which are housed in the end faces 33 and 34 of the valve housing 30 and the piston bore 31 outwardly closing lids 48 Direction can be adjusted continuously. At maximum stroke, he proposes each on an adjustable designed as a stroke limiter stop 49.
  • the control piston 32 has a piston neck 57, which is centered in the middle position to the inlet chamber 35.
  • the two piston collars 58 and 59 on both sides of the piston neck 57 are so long that their one end face is in the middle position of the control piston at a distance from the inlet chamber 35 and its other end face in the drain chamber 44 and 45 respectively.
  • the piston collar 58 has control grooves 60, which are axially open at the inlet chamber 35 facing end face, and control grooves 61 which are axially open at the end face facing the drain chamber 44.
  • the control grooves 60 and 61 are covered by the located between the control chambers 35 and 44 housing web, so that there is no open fluidic connection between the control chambers via the control grooves.
  • the piston collar 59 has no control grooves and separates the consumer chamber 39 in each position of the control piston from both the inlet chamber 35 and the drain chamber 45. Following the piston collar 59 is followed by a short further neck another piston collar, the spring chamber in the one lid 48th seals against the drain chamber 45.
  • the distance between the drain chamber 44 and the end face 33 of the valve housing 30 is greater than the distance between the drain chamber 45 and the end face 34.
  • three axially spaced chambers 63, 64 and 65 wherein the middle of these three chambers is referred to as Lastmeldesch 64.
  • the chamber 65 is present without any function.
  • a piston section 67 reaches from the end face 33 of the valve housing 30 into the region of the housing web between the chamber 63 and the drain chamber 44.
  • a flat annular groove 69 is screwed, via which in the middle position of the control piston 32, the load reporting chamber 64 is connected to the chamber 63.
  • the piston portion 67 has on a drain chamber 44 facing outer edge of a piston collar 71, which is located between the annular groove 69 and a piston neck in the region of the drain chamber 44, a notch 70, the effective width of the piston collar 71 is smaller than the width of the chamber 63rd makes and through which the chamber 63 and the drain chamber 44 with a small opening cross-section are open to each other when the control piston 32 is in its central position. Only after a certain way of the control piston from its central position out in the second direction, this fluidic connection between the drain chamber 44 and the chamber 63 and thus the chamber 64 is closed.
  • the fluidic connection between the chamber 64 via the chamber 63 to the drain chamber 44 is interrupted only by a certain stroke by the piston collar 71 in the region of the housing web between the two chambers 63rd and 64 arrived.
  • the annular groove 69 is only so wide that it comes out after a short initial stroke of the control piston 32 in the second direction from the region of the load signaling chamber 64 and is separated from this.
  • the fluidic connection between the annular groove 69 and the load reporting chamber 64 is maintained over the entire stroke of the control piston.
  • the pressure compensator 22 has a control piston 23 which is inserted in a manner not shown in a parallel to the piston bore 31 and introduced from the end face 34 in the valve housing 30 blind bore.
  • the output of the pressure compensator is connected via the channel 36 to the inlet chamber 35 of the piston bore 31.
  • the control piston 23 is in the sense of increasing the flow area of the pressure compensator of the pressure prevailing in the load detection chamber 64, which is equal to the load pressure of the hydraulic cylinder 12 with a displacement of the control piston in the first direction, and acted upon by a compression spring 78, the pressure equivalent in the area between 10 and 20 bar. In the sense of a reduction of the flow cross-section of the control piston is acted upon by the pressure in the inlet chamber 35 of the piston bore 31.
  • the axial bore 74 is widened in one step.
  • a bushing 79 or 80 is screwed, in which a measuring piston 81 and 82 is movably guided in the axis of the control piston.
  • the guide diameter of the measuring piston is about one-seventh of the diameter of the control piston, which determines the area at which a control pressure acts on the control piston.
  • each measuring piston 81, 82 has a head by which it is held captive in the screwed-in socket and the volumetric flask in the middle position of the control piston and its movement in the one direction at a distance to the respective stroke limiter holds.
  • the control grooves 60 and 61 on the piston collar 58 are covered, so that they have no fluidic Connection between the control chambers exists. If the control piston 32 moved far enough in the first direction by acting on the spring chamber in a lid 48 with a control pressure from its central position, the transverse bore 75 is first opened to the consumer chamber 38 and then via the control grooves 60 on the piston collar 58 a flow area after a brief initial stroke opened between the inlet chamber 35 and the load chamber 38, wherein the flow area increases with increasing stroke of the control piston.
  • the hydraulic cylinder 12 flows through the load channel 40 and the terminal 42 of the valve housing 30 to pressure medium.
  • the load pressure of the hydraulic cylinder 12 is via the transverse bore 75, via the axial bore 74 and the transverse bore 77 in the load signaling chamber 64 and thus on one side of the pressure compensator 22 and is also, if it is the highest load pressure, via a from Figure 1 apparent shuttle valve 83 reported to the pump controller 15.
  • the Zumeßblende 21 is realized from Figure 1, via which a pressure difference decreases, which is held constant by the pressure compensator 22 and which corresponds to the pressure equivalent of the compression spring 78.
  • the hydraulic fluid inflowing pressure medium quantity is thus determined only by the flow area of the metering orifice.
  • this flow cross section is also influenced by the load pressure of the hydraulic consumer for the hydraulic fluid flowing to the hydraulic consumer.
  • the load pressure acts on the two measuring pistons 81 and 82, of which, after a displacement of the control piston 32 in the first direction beyond an initial stroke, the measuring piston 81 is supported on the corresponding stroke limiter 49, while the measuring piston 82 rests with its head against the bushing 79. Therefore, the load pressure generated on the control piston 32 in the second direction and thus directed against the driving force generated by the control pressure force.
  • the area on which the control pressure acts is about forty times as large as the area at which the load pressure acts.
  • the force generated by the load pressure is greater, the higher the load pressure, so that at a certain Control pressure results in a load-dependent position of the control piston 32. The distance of this position from the center position and thus the Zumeßblende is smaller, the higher the load pressure.
  • a spring chamber in one of the two covers 48 is acted upon by a control pressure.
  • the pilot valves 84 and 85 control oil is supplied via a channel 86 in the valve disc 13, while control oil can flow through a channel 87.
  • the control piston 32 In order to drain pressure medium from the single-acting hydraulic cylinder 12 to the tank, the control piston 32 is adjusted by pressurization at its other end in the second direction and thereby opened via the control grooves 61 on the piston collar 58, a flow area between the consumer chamber 38 and the drain chamber 44. Given a certain control pressure, with which the control piston is acted upon, the lowering speed of the hydraulic consumer should increase less with increasing load pressure than would be due to the increase in pressure difference across the flow area at a constant flow area.
  • the transverse bore 76 is opened to the consumer chamber 39 after a short initial stroke, in which due to the connecting hole 91 of the load pressure of the hydraulic cylinder 12 is present.
  • the load pressure then acts also in the axial bore 74 and acts on the two measuring pistons 81 and 82, of which the measuring piston 82 is supported on the stroke limiter 49 and the measuring piston 81 with its head on the control piston 32.
  • the load pressure thus generates a control force opposing compensating force on the control piston. Only when the driving force exceeds the sum of compensation force and spring force, the control piston moves beyond the initial stroke. Only now, so after opening the transverse bore 76, the control grooves 61 open a flow area between the two control chambers 38 and 44.
  • control piston assumes a position in which between the driving force on the one hand and the sum of the compensation force and the force of a centering spring There is an equilibrium.
  • the control piston is moved less far from the center position than a valve without compensation force, in which the control piston at a given control pressure in each case assumes such a position in which the driving force is equal to the spring force. Accordingly, the flow area between the load chamber 38 and the drain chamber 44 via the control grooves 61 is smaller.
  • the provision of one or more measuring pistons is basically also possible in the case of a direct actuation by means of proportional solenoids.

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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)
  • Mechanically-Actuated Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Non-Deflectable Wheels, Steering Of Trailers, Or Other Steering (AREA)
  • Servomotors (AREA)

Abstract

The aim of the invention is to improve a hydraulic control assembly comprising a directional control valve that can be proportionally adjusted, in such a way that even for a single-action hydraulic cylinder a significant increase in the lowering speed of the hydraulic consumer is prevented as the load pressure accumulates, in a simple manner. To achieve this, a measuring piston (82) can be subjected to a pressure prevailing in a first consumer chamber (38) during a displacement of a control piston (32) in the second direction. During the lowering operation, the load pressure prevailing in the first consumer chamber thus impinges on the measuring piston. The compensatory force thus created increases with the accumulating load pressure and displaces the control piston to reduce the flow rate cross-section between the first consumer chamber and the outlet chamber (44). A pressure differential, which increases by means of an accumulating load pressure can therefore be partially or wholly compensated, or even overcompensated by the reduction of the flow rate cross-section, thus limiting the lowering speed.

Description

Die Erfindung geht aus von einer hydraulischen Steueranordnung, die zur Steuerung eines einfachwirkenden hydraulischen Verbrauchers, insbesondere eines einfachwirkenden Hydrozylinders, hinsichtlich Richtung und Geschwindigkeit vorgesehen ist und die Merkmale aus dem Oberbegriff des Patentanspruchs 1 aufweist.The invention is based on a hydraulic control arrangement which is provided for controlling a single-acting hydraulic consumer, in particular a single-acting hydraulic cylinder, in terms of direction and speed and having the features of the preamble of patent claim 1.

Eine solche hydraulische Steueranordnung ist zum Beispiel aus der DE 196 31 803 bekannt und umfaßt ein Wegeventil, das in einem Ventilgehäuse eine Kolbenbohrung mit einer mittleren Zulaufkammer, der Druckmittel von einer Druckmittelquelle zuführbar ist, zwei dazu benachbarte Verbraucherkammern und eine Ablaufkammer, über die Druckmittel zu einem Tank abführbar ist, hat. Üblicherweise sind zwei Ablaufkammern vorhanden. Das Wegeventil besitzt außerdem einen Steuerkolben, der durch eine willkürlich vorgegebene Ansteuerkraft von einer Mittelstellung aus axial in eine erste und in eine dazu entgegengesetzte zweite Richtung verschiebbar ist und der mit ersten Feinsteuernuten zum Aufsteuern einer Verbindung zwischen der Zulaufkammer und einer ersten der beiden Verbraucherkammern bei einer Verschiebung aus der Mittelstellung in eine erste Richtung und mit zweiten Feinsteuernuten zum Aufsteuern der Verbindung zwischen der ersten Verbraucherkammer und der Ablaufkammer bei einer Verschiebung aus der Mittelstellung in die zweite Richtung versehen ist. Mit dem Steuerkolben wirken vom Lastdruck beaufschlagbare Meßkolben derart zusammen, daß bei einer Verschiebung des Steuerkolbens aus der Mittelstellung eine der Ansteuerkraft entgegengerichtete und mit zunehmendem Lastdruck zunehmende Kompensationskraft auf den Steuerkolben ausübbar ist.Such a hydraulic control arrangement is known for example from DE 196 31 803 and comprises a directional control valve which in a valve housing a piston bore with a central inlet chamber, the pressure medium from a pressure medium source can be supplied, two adjacent consumer chambers and a drain chamber, via the pressure medium to a tank is drained, has. Usually there are two drainage chambers. The directional control valve also has a control piston which is displaceable by an arbitrary predetermined driving force from a central position of axially in a first and in an opposite second direction and the first Feinsteuernuten for aufsteuern a connection between the inlet chamber and a first of the two consumer chambers at a Displacement from the center position in a first direction and provided with second fine control grooves for controlling the connection between the first consumer chamber and the discharge chamber in a shift from the central position in the second direction. With the control piston acted upon by the load pressure measuring piston cooperate in such a way that upon displacement of the control piston from the center position one of the driving force opposing and increasing with increasing load pressure compensating force is exerted on the control piston.

Die bekannte hydraulische Steueranordnung dient zur Steuerung eines doppeltwirkenden hydraulischen Verbrauchers, zum Beispiel eines Differentialzylinders und ist eine sogenannte Load-Sensing -Steuerung. Hier wird eine Verstellpumpe oder die im Bypass zu einer Konstantpumpe geschaltete Druckwaage derart geregelt, daß sich in einer Pumpenleitung, in die die Pumpe fördert, ein Pumpendruck einstellt, der um eine bestimmte Druckdifferenz, das sogenannte Pumpen-Δp, über dem höchsten Lastdruck aller gleichzeitig betätigten hydraulischen Verbraucher liegt. Das Druckmittel fließt über proportional verstellbare und durch Steuernuten am Steuerkolben gebildete Zumeßblenden dem einen oder dem anderen Anschluß des hydraulischen Verbrauchers zu. Damit nicht nur die dem lastdruckhöchsten, sondern auch die den anderen gleichzeitig angesteuerten hydraulischen Verbrauchern zufließende Druckmittelmenge lastdruckunabhängig nur von dem Durchflußquerschnitt der Zumeßblende abhängt, ist den beiden Zumeßblenden eines hydraulischen Verbrauchers eine sogenannte Individualdruckwaage vorgeschaltet, deren Regelkolben in Schließrichtung von dem Druck vor den Zumeßblenden und in Öffnungsrichtung vom Lastdruck des jeweiligen hydraulischen Verbrauchers und von einer Regelfeder beaufschlagt ist. Die Druckwaage hält eine dem Druckäquivalent der Regelfeder entsprechende Druckdifferenz über die gerade aktive Zumeßblende aufrecht.The known hydraulic control arrangement is used to control a double-acting hydraulic consumer, for example a differential cylinder and is a so-called load sensing control. Here is a variable or the bypass connected to a constant pump pressure compensator regulated so that adjusts a pump pressure in a pump line in which a pump pressure to a certain pressure difference, the so-called pump Δp, above the highest load pressure all at the same time actuated hydraulic consumer is located. The pressure medium flows via proportionally adjustable metering orifices formed by control grooves on the control piston to one or the other port of the hydraulic consumer. So that not only the load pressure highest, but also the other simultaneously controlled hydraulic consumers inflowing pressure medium load pressure independent depends only on the flow area of Zumeßblende, the two Zumeßblenden a hydraulic consumer upstream of a so-called individual pressure compensator whose control piston in the closing direction of the pressure in front of the Zumeßblenden and is acted upon in the opening direction by the load pressure of the respective hydraulic consumer and by a control spring. The pressure compensator maintains a pressure difference corresponding to the pressure equivalent of the control spring across the currently active metering orifice.

Durch die mit dem Steuerkolben zusammenwirkenden Meßkolben wird nun erreicht, daß der Durchflußquerschnitt einer Zumeßblende bei einer vorgegebenen auf den Steuerkolben wirkenden Ansteuerkraft um so kleiner ist, je höher der Lastdruck ist. Da die Druckwaage eine konstante Druckdifferenz über die Zumeßblende aufrechterhält, wird die dem hydraulischen Verbraucher zufließende Druckmittelmenge und damit die Geschwindigkeit, mit der sich der hydraulische Verbraucher bewegt, mit zunehmendem Lastdruck kleiner. Letztendlich vermögen in Abhängigkeit von der Ansteuerkraft verschieden hohe Lastdrücke die Zumeßblende ganz zu schließen, so daß der Lastdruck nicht weiter ansteigen kann. Die auf diese Weise mögliche Momenten- oder Kraftsteuerung des hydraulischen Verbrauchers ist bisher der wesentliche Grund für das Vorsehen der Meßkolben.By cooperating with the control piston measuring piston is now achieved that the flow area of a metering orifice at a given acting on the control piston driving force is the smaller, the higher the load pressure. Since the pressure compensator maintains a constant pressure difference across the metering orifice, the amount of pressure fluid flowing to the hydraulic consumer, and thus the speed with which the hydraulic consumer moves, decreases with increasing load pressure. Finally, depending on the driving force, different high load pressures can completely close the metering orifice, so that the load pressure can not increase any further. The possible in this way torque or force control of the hydraulic consumer has been the main reason for the provision of the measuring flask.

Der Erfindung liegt die Aufgabe zugrunde, eine hydraulische Steueranordnung mit den Merkmalen aus dem Oberbegriff des Patentanspruchs 1 so weiterzuentwikkeln, daß auch bei einem einfachwirkenden hydraulischen Verbraucher, insbesondere bei einem einfachwirkenden Hydrozylinder, bei einer vorgegebenen auf den Steuerkolben wirkenden Ansteuerkraft mit einfachen Mitteln ein starker Anstieg der Senkgeschwindigkeit des hydraulischen Verbrauchers mit zunehmendem Lastdruck vermieden wird.The invention has the object of providing a hydraulic control arrangement weiterzuentwikkeln with the features of the preamble of claim 1 so that even with a single-acting hydraulic load, especially in a single-acting hydraulic cylinder at a given acting on the control piston driving force with simple means a strong increase the lowering speed of the hydraulic consumer is avoided with increasing load pressure.

Das angestrebte Ziel wird erfindungsgemäß dadurch erreicht, daß bei der hydraulischen Steueranordnung mit den Merkmalen aus dem Oberbegriff des Patentanspruchs 1 der Meßkolben bei einer Verschiebung des Steuerkolbens in die zweite Richtung von dem in der ersten Verbraucherkammer herrschenden Druck beaufschlagbar ist. Es wird also der Meßkolben, der bei der Verwendung des Wegeventils für die Betätigung eines doppeltwirkenden hydraulischen Verbrauchers mit dem in der zweiten Verbraucherkammer anstehenden Lastdruck beaufschlagt wird, beim Senken mit der ersten Verbraucherkammer verbunden und damit beim Senken mit dem Lastdruck beaufschlagt. Die dadurch erzeugte Kompensationskraft steigt mit zunehmendem Lastdruck an und verschiebt den Steuerkolben im Sinne einer Verkleinerung des Durchflußquerschnitts von der ersten Verbraucherkammer zur Ablaufkammer. Auf diese Weise kann eine durch einen zunehmenden Lastdruck zunehmende Druckdifferenz über den Durchflußquerschnitt durch dessen Verkleinerung teilweise oder ganz oder sogar überkompensiert und damit die Senkgeschwindigkeit begrenzt werden. Dies geschieht auf wesentlich einfachere Weise als zum Beispiel mit einer Druckwaage in einem von der Ablaufkammer wegführenden Ablaufkanal.The desired object is achieved according to the invention that in the hydraulic control arrangement with the features of the preamble of claim 1 of the volumetric flask is acted upon by a displacement of the control piston in the second direction of the prevailing pressure in the first consumer chamber. So it is the volumetric flask, which is applied in the use of the directional control valve for the operation of a double-acting hydraulic consumer with the pending in the second load chamber load pressure when lowering connected to the first load chamber and thus acted upon lowering with the load pressure. The compensation force generated thereby increases with increasing load pressure and shifts the control piston in the sense of a reduction of the flow cross-section from the first consumer chamber to the drain chamber. In this way, a by an increasing load pressure increasing pressure difference across the flow area by its reduction partially or completely or even overcompensated and thus the lowering speed can be limited. This is done in a much simpler manner than for example with a pressure compensator in a leading away from the drain chamber drainage channel.

Vorteilhafte Ausgestaltungen einer erfindungsgemäßen hydraulischen Steueranordnung kann man den Unteransprüchen entnehmen.Advantageous embodiments of a hydraulic control arrangement according to the invention can be found in the dependent claims.

Grundsätzlich ist es denkbar, zwischen der ersten Verbraucherkammer und der zweiten Verbraucherkammer, von der aus der Meßkolben vorteilhafterweise gemäß Patentanspruch 2 mit Lastdruck beaufschlagt wird, eine fluidische Verbindung außerhalb des Ventilgehäuses zu schaffen. Besonders bevorzugt wird jedoch die einfache Lösung gemäß Patentanspruch 3, wonach die fluidische Verbindung zwischen der ersten Verbraucherkammer und der zweiten Verbraucherkammer ganz innerhalb des Ventilgehäuses besteht. Der Aufwand für die Verbindung ist bei den Ausbildungen gemäß den Patentansprüchen 4 und 5 besonders gering.In principle, it is conceivable to create a fluidic connection outside the valve housing between the first consumer chamber and the second consumer chamber, from which the volumetric flask is advantageously subjected to load pressure according to claim 2. However, particularly preferred is the simple solution according to claim 3, according to which the fluidic connection between the first consumer chamber and the second consumer chamber is entirely within the valve housing. The cost of the compound is particularly low in the embodiments according to claims 4 and 5.

Gemäß Patentanspruch 6 weist der Steuerkolben eine der Meldung des Lastdrukkes des hydraulischen Verbrauchers dienende Axialbohrung auf, die bei einer Verschiebung des Steuerkolbens in die erste Richtung über eine erste Querbohrung zu der ersten Verbraucherkammer und bei einer Verschiebung des Steuerkolbens in die zweite Richtung über eine zweite Querbohrung zu der zweiten Verbraucherkammer geöffnet wird. Bei einer Verschiebung des Steuerkolbens in die erste Richtung wird der Druck aus der Axialbohrung über eine dritte Querbohrung in eine Lastmeldekammer gegeben. Der Meßkolben ist in dem Steuerkolben geführt und im Innern des Steuerkolbens dem in der Axialbohrung anstehenden Druck ausgesetzt und außen an einem Anschlag des Ventilgehäuses abstützbar. Diese an sich zum Beispiel aus der DE 196 31 803 bekannte Gestaltung kann somit aufgrund der fluidischen Verbindung der zweiten Verbraucherkammer mit der ersten Verbraucherkammer ohne weiteres beibehalten werden, um den Meßkolben bei einer Verschiebung des Steuerkolbens in die zweite Richtung mit dem in der ersten Verbraucherkammer anstehenden Druck zu beaufschlagen.According to claim 6, the control piston on one of the message of Lastdrukkes of the hydraulic consumer serving axial bore, with a displacement of the control piston in the first direction via a first transverse bore to the first consumer chamber and a displacement of the control piston in the second direction via a second transverse bore is opened to the second consumer chamber. Upon displacement of the control piston in the first direction, the pressure from the axial bore is passed through a third transverse bore in a load reporting chamber. The volumetric flask is guided in the control piston and exposed in the interior of the control piston to the pending in the axial bore pressure and the outside of a stop of the valve housing can be supported. This configuration, known per se, for example, from DE 196 31 803, can thus be readily retained due to the fluidic connection of the second consumer chamber to the first consumer chamber in order to deliver the volumetric flask to the first consumer chamber when the control piston is displaced in the second direction To pressurize.

Beim Absenken des hydraulischen Verbrauchers wird für diesen kein Druckmittel von der Hydropumpe benötigt. Damit diese nicht durch den Lastdruck des hydraulischen Verbrauchers aufgeregelt wird, ist gemäß Patentanspruch 7 bei einer Verschiebung des Steuerkolbens in die zweite Richtung die Axialbohrung von der Lastmeldekammer getrennt. Vorteilhafterweise erreicht man dies durch die Ausgestaltung gemäß Patentanspruch 8.When lowering the hydraulic load no pressure medium from the hydraulic pump is required for this. So that this is not regulated by the load pressure of the hydraulic consumer, according to claim 7 in a displacement of the control piston in the second direction, the axial bore of the Load indicator chamber separated. Advantageously, this is achieved by the embodiment according to claim 8.

Die Erfindung ist auch in einem Wegeventil gemäß Patentanspruch 9 verkörpert.The invention is also embodied in a directional control valve according to claim 9.

Ein Ausführungsbeispiel einer erfindungsgemäßen hydraulischen Steueranordnung mit einem erfindungsgemäßen Wegeventil ist in den Zeichnungen dargestellt. Anhand der Figuren dieser Zeichnungen wird die Erfindung nun näher erläutert.An embodiment of a hydraulic control arrangement according to the invention with a directional control valve according to the invention is shown in the drawings. With reference to the figures of these drawings, the invention will now be explained in more detail.

Es zeigen

Figur 1
die hydraulische Steueranordnung einschließlich des Wegeventils als Schaltbild,
Figur 2
einen Längsschnitt durch das Wegeventil mit dem Steuerkolben in der Mittelstellung und
Figur 3
einen Längsschnitt durch das Wegeventil mit dem Steuerkolben nach einer Verschiebung im Sinne eines Ablaufs von Druckmittel aus dem hydraulischen Verbraucher.
Show it
FIG. 1
the hydraulic control arrangement including the directional control valve as a circuit diagram,
FIG. 2
a longitudinal section through the directional control valve with the control piston in the middle position and
FIG. 3
a longitudinal section through the directional control valve with the control piston after a shift in the sense of a flow of pressure medium from the hydraulic consumer.

Nach Figur 1 können von einer Verstellpumpe 10 über einen Wegeventilblock 11 mehrere hydraulische Verbraucher mit Druckmittel, üblicherweise Mineralöl, versorgt werden. Im Schaltbild explizit dargestellt ist lediglich ein einfachwirkender Hydrozylinder 12 und eine Wegeventilscheibe 13, mit der die Druckmittelwege zwischen dem Hydrozylinder, der Verstellpumpe und einem Tank 14 steuerbar sind. Die Verstellpumpe ist strombedarfsgesteuert und weist einen Load-Sensing-Regler 15 auf, dem über einen Anschluß LS eines Eingangselements 16 der Wegeventilblocks 11 der höchste Lastdruck aller gleichzeitig angesteuerter hydraulischer Verbraucher gemeldet wird. Die Verstellpumpe saugt Druckmittel aus dem Tank 14 an und gibt es in eine zu einem Pumpenanschluß P des Eingangselements führende Druckleitung 17 ab. Sie fördert dabei jeweils soviel Druckmittel, daß in der Druckleitung 17 ein um das Pumpen-Δp, das üblicherweise auf einen Wert zwischen zehn und zwanzig bar eingestellt ist, über dem höchsten Lastdruck liegender Pumpendruck erzeugt wird.According to FIG. 1, a variable displacement pump 10 can supply a plurality of hydraulic consumers with pressure medium, usually mineral oil, via a directional control valve block 11. The diagram explicitly shows only a single-acting hydraulic cylinder 12 and a directional valve disc 13, with which the pressure medium paths between the hydraulic cylinder, the variable displacement pump and a tank 14 are controllable. The variable displacement pump is current demand-controlled and has a load-sensing controller 15, which is reported via a terminal LS of an input element 16 of the directional control valve block 11, the highest load pressure of all simultaneously controlled hydraulic consumers. The variable displacement pump sucks pressure medium from the tank 14 and it is in a leading to a pump port P of the input element pressure line 17 from. It promotes in each case so much pressure medium that in the pressure line 17 to the pump Δp, which is usually set to a value between ten and twenty bar, above the highest load pressure lying pump pressure is generated.

Die Wegeventilscheibe 13 umfaßt ein proportional verstellbares Wegeventil 20 und eine einer Zumeßblende 21 des Wegeventils vorgeschaltete Druckwaage 22, die mit ihrem Eingang mit dem Pumpenanschluß P verbunden ist. Mit dem Wegeventil und der Druckwaage kann der Hydrozylinder für das Ausfahren der Kolbenstange lastdruckunabhängig betätigt werden. Für die Wegefunktionen und die Funktion der Zumeßblende geht durch ein Ventilgehäuse 30 eine Kolbenbohrung 31 hindurch, in der ein Steuerkolben 32 axial bewegbar ist. Die Länge des Steuerkolbens 32 stimmt mit der Länge der Kolbenbohrung 31 von der einen Stirnseite 33 bis zur anderen Stirnseite 34 des Ventilgehäuses 30 überein. Die Kolbenbohrung 31 ist von fünf axial voneinander beabstandeten Steuerkammern umgeben. Drei davon dienen dem Zufluß von Druckmittel zu und dem Abfluß von Druckmittel aus dem Hydrozylinder 12. Die fluidischen Verbindungen unter den drei Steuerkammern werden von dem Steuerkolben 32 gesteuert. Es sind jedoch fünf Steuerkammern vorhanden, weil ein auch für die Steuerung von doppeltwirkenden hydraulischen Verbrauchern gegossenes Ventilgehäuse verwendet wird. Die mittlere Steuerkammer 35 der fünf Steuerkammern ist die Zulaufkammer. Dieser strömt Druckmittel über einen Kanal 36 von der auch in Figur 2 nur schaltbildmäßig dargestellten Druckwaage 22 her zu. Beidseits der Zulaufkammer befindet sich jeweils eine Verbraucherkammer 38 bzw. 39, von denen jede mit einer am Ende eines Verbraucherkanals 40 bzw. 41 befindlichen Verbraucheranschlußgewindebohrung 42 bzw. 43 der Ventilscheibe verbunden ist. Die beiden Verbraucherkanäle 40 und 41 verlaufen im wesentlichen parallel zueinander und senkrecht zur Kolbenbohrung 31. Auf jede Verbraucherkammer 38 bzw. 39 folgt noch eine Ablaufkammer 44 bzw. 45, die zu einem von zwei durch das Ventilgehäuse 30 hindurchgehenden Tankkanälen 46 offen ist.The directional control valve disc 13 comprises a proportionally adjustable directional control valve 20 and an upstream of a metering orifice 21 of the directional valve pressure compensator 22 which is connected at its input to the pump port P. With the directional control valve and the pressure compensator, the hydraulic cylinder can be actuated for the extension of the piston rod independent of the load pressure. For the path functions and the function of the metering aperture, a piston bore 31 passes through a valve housing 30, in which a control piston 32 is axially movable. The length of the control piston 32 coincides with the length of the piston bore 31 from one end face 33 to the other end face 34 of the valve housing 30. The piston bore 31 is surrounded by five axially spaced control chambers. Three of these serve for the inflow of pressure medium to and the outflow of pressure medium from the hydraulic cylinder 12. The fluidic connections under the three control chambers are controlled by the control piston 32. However, there are five control chambers because a valve housing also cast for the control of double acting hydraulic consumers is used. The middle control chamber 35 of the five control chambers is the inlet chamber. This flows pressure medium via a channel 36 from the only in Figure 2 shown in circuit diagram pressure compensator 22 ago. On both sides of the inlet chamber is in each case a consumer chamber 38 and 39, each of which is connected to a located at the end of a consumer channel 40 and 41, consumer connection threaded bore 42 and 43 of the valve disc. The two consumer channels 40 and 41 are substantially parallel to each other and perpendicular to the piston bore 31. Each consumer chamber 38 and 39 is followed by a drain chamber 44 and 45, which is open to one of two passing through the valve housing 30 tank channels 46.

Der Steuerkolben 32 nimmt aufgrund von zwei Zentrierfedern 47, die in an den Stirnseiten 33 und 34 des Ventilgehäuses 30 befestigten und die Kolbenbohrung 31 nach außen verschließenden Deckeln 48 untergebracht sind, eine Mittelstellung ein, aus der er in eine erste Richtung und eine dazu entgegengesetzte zweite Richtung stetig verstellt werden kann. Bei maximalem Hub schlägt er jeweils an einem verstellbaren als Hubbegrenzer ausgeführten Anschlag 49 an. Der Steuerkolben 32 besitzt einen Kolbenhals 57, der in der Mittelstellung zur Zulaufkammer 35 zentriert ist. Die beiden Kolbenbunde 58 und 59 beidseits des Kolbenhalses 57 sind so lang, daß sich in der Mittelstellung des Steuerkolbens ihre eine Stirnseite in einem Abstand von der Zulaufkammer 35 und ihre andere Stirnseite in der Ablaufkammer 44 bzw. 45 befindet. Der Kolbenbund 58 hat Steuernuten 60, die an der der Zulaufkammer 35 zugekehrten Stirnseite axial offen sind, und Steuernuten 61, die an der der Ablaufkammer 44 zugekehrten Stirnseite axial offen sind. In der Mittelstellung des Steuerkolbens 32 sind die Steuernuten 60 und 61 von dem zwischen den Steuerkammern 35 und 44 befindlichen Gehäusesteg überdeckt, so daß über die Steuernuten keine offene fluidische Verbindung zwischen einzelnen Steuerkammern besteht. Der Kolbenbund 59 besitzt keine Steuernuten und trennt die Verbraucherkammer 39 in jeder Stellung des Steuerkolbens sowohl von der Zulaufkammer 35 als auch von der Ablaufkammer 45. Auf den Kolbenbund 59 folgt nach einem kurzen weiteren Hals ein weiterer Kolbenbund, der den Federraum in dem einen Deckel 48 gegen die Ablaufkammer 45 abdichtet.The control piston 32 assumes a central position, from which it is in a first direction and a second thereto opposite due to two centering springs 47 which are housed in the end faces 33 and 34 of the valve housing 30 and the piston bore 31 outwardly closing lids 48 Direction can be adjusted continuously. At maximum stroke, he proposes each on an adjustable designed as a stroke limiter stop 49. The control piston 32 has a piston neck 57, which is centered in the middle position to the inlet chamber 35. The two piston collars 58 and 59 on both sides of the piston neck 57 are so long that their one end face is in the middle position of the control piston at a distance from the inlet chamber 35 and its other end face in the drain chamber 44 and 45 respectively. The piston collar 58 has control grooves 60, which are axially open at the inlet chamber 35 facing end face, and control grooves 61 which are axially open at the end face facing the drain chamber 44. In the middle position of the control piston 32, the control grooves 60 and 61 are covered by the located between the control chambers 35 and 44 housing web, so that there is no open fluidic connection between the control chambers via the control grooves. The piston collar 59 has no control grooves and separates the consumer chamber 39 in each position of the control piston from both the inlet chamber 35 and the drain chamber 45. Following the piston collar 59 is followed by a short further neck another piston collar, the spring chamber in the one lid 48th seals against the drain chamber 45.

Der Abstand zwischen der Ablaufkammer 44 und der Stirnseite 33 des Ventilgehäuses 30 ist größer als der Abstand zwischen der Ablaufkammer 45 und der Stirnseite 34. Zwischen der Ablaufkammer 44 und der Stirnseite 33 befinden sich in der Kolbenbohrung 31 drei axial voneinander beabstandete Kammern 63, 64 und 65, wobei die mittlere dieser drei Kammern als Lastmeldekammer 64 bezeichnet sei. Die Kammer 65 ist vorliegend ohne jede Funktion. In der in der Figur 2 gezeigten Mittelstellung des Steuerkolbens 32 reicht ein Kolbenabschnitt 67 von der Stirnseite 33 des Ventilgehäuses 30 aus bis in den Bereich des Gehäusesteges zwischen der Kammer 63 und der Ablaufkammer 44. In diesen Kolbenabschnitt ist eine flache Ringnut 69 eingedreht, über die in der gezeigten Mittelstellung des Steuerkolbens 32 die Lastmeldekammer 64 mit der Kammer 63 verbunden ist. Außerdem besitzt der Kolbenabschnitt 67 an einer der Ablaufkammer 44 zugekehrten Außenkante eines Kolbenbundes 71, der sich zwischen der Ringnut 69 und einem Kolbenhals im Bereich der Ablaufkammer 44 befindet, eine Einkerbung 70, die die wirksame Breite des Kolbenbundes 71 kleiner als die Breite der Kammer 63 macht und durch die die Kammer 63 und die Ablaufkammer 44 mit einem kleinen Öffnungsquerschnitt zueinander offen sind, wenn sich der Steuerkolben 32 in seiner Mittelstellung befindet. Erst nach einem bestimmten Weg des Steuerkolbens aus seiner Mittelstellung heraus in die zweite Richtung wird diese fluidische Verbindung zwischen der Ablaufkammer 44 und der Kammer 63 und damit der Kammer 64 verschlossen. Auch bei einer Verstellung des Steuerkolbens 32 aus der Mittelstellung in die erste Richtung wird erst nach einem bestimmten Hub die fluidische Verbindung zwischen der Kammer 64 über die Kammer 63 zur Ablaufkammer 44 unterbrochen, indem der Kolbenbund 71 in den Bereich des Gehäusesteges zwischen den beiden Kammern 63 und 64 gelangt. Die Ringnut 69 ist nur so breit, daß sie nach einem kurzen Anfangshub des Steuerkolbens 32 in die zweite Richtung aus dem Bereich der Lastmeldekammer 64 herauskommt und von dieser getrennt ist. Bei einer Bewegung des Steuerkolbens aus der Mittelstellung in die erste Richtung bleibt die fluidische Verbindung zwischen der Ringnut 69 und der Lastmeldekammer 64 über den gesamten Hub des Steuerkolbens erhalten.The distance between the drain chamber 44 and the end face 33 of the valve housing 30 is greater than the distance between the drain chamber 45 and the end face 34. Between the drain chamber 44 and the end face 33 are located in the piston bore 31, three axially spaced chambers 63, 64 and 65, wherein the middle of these three chambers is referred to as Lastmeldekammer 64. The chamber 65 is present without any function. In the middle position of the control piston 32 shown in FIG. 2, a piston section 67 reaches from the end face 33 of the valve housing 30 into the region of the housing web between the chamber 63 and the drain chamber 44. In this piston portion, a flat annular groove 69 is screwed, via which in the middle position of the control piston 32, the load reporting chamber 64 is connected to the chamber 63. In addition, the piston portion 67 has on a drain chamber 44 facing outer edge of a piston collar 71, which is located between the annular groove 69 and a piston neck in the region of the drain chamber 44, a notch 70, the effective width of the piston collar 71 is smaller than the width of the chamber 63rd makes and through which the chamber 63 and the drain chamber 44 with a small opening cross-section are open to each other when the control piston 32 is in its central position. Only after a certain way of the control piston from its central position out in the second direction, this fluidic connection between the drain chamber 44 and the chamber 63 and thus the chamber 64 is closed. Even with an adjustment of the control piston 32 from the central position in the first direction, the fluidic connection between the chamber 64 via the chamber 63 to the drain chamber 44 is interrupted only by a certain stroke by the piston collar 71 in the region of the housing web between the two chambers 63rd and 64 arrived. The annular groove 69 is only so wide that it comes out after a short initial stroke of the control piston 32 in the second direction from the region of the load signaling chamber 64 and is separated from this. Upon movement of the control piston from the central position in the first direction, the fluidic connection between the annular groove 69 and the load reporting chamber 64 is maintained over the entire stroke of the control piston.

Durch den gesamten Steuerkolben 32 hindurch verläuft eine Axialbohrung 74, die von zwei Querbohrungen 75 und 76 gekreuzt wird, von denen sich die Querbohrung 75 im Kolbenbund 58 und die Querbohrung 76 im Kolbenbund 59 des Steuerkolbens 32 jeweils an einer solchen Stelle befindet, daß sie in der Mittelstellung des Steuerkolbens von der Wand der Kolbenbohrung 31 überdeckt ist. Bei einer Bewegung des Steuerkolbens 32 aus der Mittelstellung heraus in die erste Richtung wird die Querbohrung 75 zur Verbraucherkammer 38 hin und bei einer Bewegung des Steuerkolbens in die zweite Richtung die Querbohrung 76 zur Verbraucherkammer 39 hin offen. Über eine weitere Querbohrung 77, die im Bereich der Ringnut 69 bis zur Axialbohrung 74 in den Steuerkolben 32 eingebracht ist, ist die Axialbohrung zur Ringnut 69 offen.Through the entire control piston 32 passes through an axial bore 74 which is crossed by two transverse bores 75 and 76, of which the transverse bore 75 in the piston collar 58 and the transverse bore 76 in the piston collar 59 of the control piston 32 is in each case in such a position that they the center position of the control piston is covered by the wall of the piston bore 31. Upon movement of the control piston 32 from the central position out in the first direction, the transverse bore 75 to the consumer chamber 38 and during a movement the control piston in the second direction, the transverse bore 76 to the consumer chamber 39 out. About a further transverse bore 77, which is introduced in the region of the annular groove 69 to the axial bore 74 in the control piston 32, the axial bore to the annular groove 69 is open.

Die Druckwaage 22 besitzt einen Regelkolben 23, der in nicht näher dargestellter Weise in eine zur Kolbenbohrung 31 parallel verlaufende und von der Stirnseite 34 in das Ventilgehäuse 30 eingebrachte Sackbohrung eingesetzt ist. Der Ausgang der Druckwaage ist über den Kanal 36 mit der Zulaufkammer 35 der Kolbenbohrung 31 verbunden. Der Regelkolben 23 wird im Sinne einer Vergrößerung des Durchflußquerschnitts der Druckwaage von dem in der Lastmeldekammer 64 herrschenden Druck, der bei einer Verschiebung des Steuerkolbens in die erste Richtung gleich dem Lastdruck des Hydrozylinders 12 ist, und von einer Druckfeder 78 beaufschlagt, deren Druckäquivalent im Bereich zwischen 10 und 20 bar liegt. Im Sinne einer Verkleinerung des Durchflußquerschnitts wird der Regelkolben vom Druck in der Zulaufkammer 35 der Kolbenbohrung 31 beaufschlagt.The pressure compensator 22 has a control piston 23 which is inserted in a manner not shown in a parallel to the piston bore 31 and introduced from the end face 34 in the valve housing 30 blind bore. The output of the pressure compensator is connected via the channel 36 to the inlet chamber 35 of the piston bore 31. The control piston 23 is in the sense of increasing the flow area of the pressure compensator of the pressure prevailing in the load detection chamber 64, which is equal to the load pressure of the hydraulic cylinder 12 with a displacement of the control piston in the first direction, and acted upon by a compression spring 78, the pressure equivalent in the area between 10 and 20 bar. In the sense of a reduction of the flow cross-section of the control piston is acted upon by the pressure in the inlet chamber 35 of the piston bore 31.

Zu beiden Enden des Steuerkolbens 32 hin ist die Axialbohrung 74 in einer Stufe erweitert. In die jeweilige Erweiterung ist eine Buchse 79 bzw. 80 eingeschraubt, in der ein Meßkolben 81 bzw. 82 in der Achse des Steuerkolbens beweglich geführt ist. Der Führungsdurchmesser der Meßkolben beträgt etwa ein Siebtel des Durchmessers des Steuerkolbens, der die Fläche bestimmt, an der ein Steuerdruck auf den Steuerkolben wirkt. Mit ihrem äußeren Ende können sich die Meßkolben an den Hubbegrenzem 49 abstützen. An seinem Ende im Innern des Steuerkolbens 32 hat jeder Meßkolben 81, 82 einen Kopf, durch den er unverlierbar in der eingeschraubten Buchse gehalten ist und der den Meßkolben in der Mittelstellung des Steuerkolbens und bei dessen Bewegung in die eine Richtung im Abstand zu dem jeweiligen Hubbegrenzer hält.Towards both ends of the control piston 32, the axial bore 74 is widened in one step. Into the respective extension a bushing 79 or 80 is screwed, in which a measuring piston 81 and 82 is movably guided in the axis of the control piston. The guide diameter of the measuring piston is about one-seventh of the diameter of the control piston, which determines the area at which a control pressure acts on the control piston. With its outer end, the volumetric flask can be supported on the Hubbegrenzem 49. At its end in the interior of the control piston 32, each measuring piston 81, 82 has a head by which it is held captive in the screwed-in socket and the volumetric flask in the middle position of the control piston and its movement in the one direction at a distance to the respective stroke limiter holds.

Wie schon erwähnt, sind in der Mittelstellung des Steuerkolbens 32 die Steuernuten 60 und 61 an dem Kolbenbund 58 überdeckt, so daß über sie keine fluidische Verbindung zwischen den Steuerkammern besteht. Wird der Steuerkolben 32 durch Beaufschlagung des Federraums in einem Deckel 48 mit einem Steuerdruck aus seiner Mittelstellung weit genug in die erste Richtung verschoben, so wird zunächst nach kurzem Anfangshub die Querbohrung 75 zur Verbraucherkammer 38 geöffnet und dann über die Steuernuten 60 am Kolbenbund 58 ein Durchflußquerschnitt zwischen der Zulaufkammer 35 und der Verbraucherkammer 38 aufgemacht, wobei sich der Durchflußquerschnitt mit zunehmendem Hub des Steuerkolbens vergrößert. Dem Hydrozylinder 12 fließt über den Verbraucherkanal 40 und den Anschluß 42 des Ventilgehäuses 30 Druckmittel zu. Der Lastdruck des Hydrozylinders 12 steht über die Querbohrung 75, über die Axialbohrung 74 und über die Querbohrung 77 in der Lastmeldekammer 64 und damit an der einen Seite der Druckwaage 22 an und wird außerdem, sofern er der höchste Lastdruck ist, über ein aus Figur 1 ersichtliches Wechselventil 83 an den Pumpenregler 15 gemeldet. Durch den Durchflußquerschnitt an den Steuernuten 60 des Kolbenbunds 58 ist die Zumeßblende 21 aus Figur 1 realisiert, über die eine Druckdifferenz abfällt, die durch die Druckwaage 22 konstant gehalten wird und die dem Druckäquivalent der Druckfeder 78 entspricht. Die dem hydraulischen Verbraucher zufließende Druckmittelmenge wird somit nur noch vom Durchflußquerschnitt der Zumeßblende bestimmt.As already mentioned, in the middle position of the control piston 32, the control grooves 60 and 61 on the piston collar 58 are covered, so that they have no fluidic Connection between the control chambers exists. If the control piston 32 moved far enough in the first direction by acting on the spring chamber in a lid 48 with a control pressure from its central position, the transverse bore 75 is first opened to the consumer chamber 38 and then via the control grooves 60 on the piston collar 58 a flow area after a brief initial stroke opened between the inlet chamber 35 and the load chamber 38, wherein the flow area increases with increasing stroke of the control piston. The hydraulic cylinder 12 flows through the load channel 40 and the terminal 42 of the valve housing 30 to pressure medium. The load pressure of the hydraulic cylinder 12 is via the transverse bore 75, via the axial bore 74 and the transverse bore 77 in the load signaling chamber 64 and thus on one side of the pressure compensator 22 and is also, if it is the highest load pressure, via a from Figure 1 apparent shuttle valve 83 reported to the pump controller 15. By the flow area at the control grooves 60 of the piston collar 58, the Zumeßblende 21 is realized from Figure 1, via which a pressure difference decreases, which is held constant by the pressure compensator 22 and which corresponds to the pressure equivalent of the compression spring 78. The hydraulic fluid inflowing pressure medium quantity is thus determined only by the flow area of the metering orifice.

Allerdings wird dieser Durchflußquerschnitt für das dem hydraulischen Verbraucher zufließende Druckmittel auch vom Lastdruck des hydraulischen Verbrauchers beeinflußt. Der Lastdruck beaufschlagt nämlich die beiden Meßkolben 81 und 82, von denen sich nach einer Verschiebung des Steuerkolbens 32 in die erste Richtung über einen Anfangshub hinaus der Meßkolben 81 am entsprechenden Hubbegrenzer 49 abstützt, während der Meßkolben 82 mit seinem Kopf an der Buchse 79 anliegt. Der Lastdruck erzeugt deshalb am Steuerkolben 32 eine in die zweite Richtung und damit gegen die durch den Steuerdruck erzeugte Ansteuerkraft gerichtete Kraft. Die Fläche, an der der Steuerdruck wirkt ist dabei etwa vierzig mal so groß wie die Fläche, an der der Lastdruck angreift. Die vom Lastdruck erzeugte Kraft ist um so größer, je höher der Lastdruck ist, so daß sich bei einem bestimmten Steuerdruck eine vom Lastdruck abhängige Stellung des Steuerkolbens 32 ergibt. Der Abstand dieser Stellung von der Mittelstellung und damit die Zumeßblende ist um so kleiner, je höher der Lastdruck ist.However, this flow cross section is also influenced by the load pressure of the hydraulic consumer for the hydraulic fluid flowing to the hydraulic consumer. The load pressure acts on the two measuring pistons 81 and 82, of which, after a displacement of the control piston 32 in the first direction beyond an initial stroke, the measuring piston 81 is supported on the corresponding stroke limiter 49, while the measuring piston 82 rests with its head against the bushing 79. Therefore, the load pressure generated on the control piston 32 in the second direction and thus directed against the driving force generated by the control pressure force. The area on which the control pressure acts is about forty times as large as the area at which the load pressure acts. The force generated by the load pressure is greater, the higher the load pressure, so that at a certain Control pressure results in a load-dependent position of the control piston 32. The distance of this position from the center position and thus the Zumeßblende is smaller, the higher the load pressure.

Zur Verschiebung des Steuerkolbens 32 aus seiner Mittelstellung wird ein Federraum in einem der beiden Deckel 48 mit einem Steuerdruck beaufschlagt. Dazu dienen zwei elektromagnetisch betätigbare Pilotventile 84 und 85, die in nicht näher dargestellter Weise an der Ventilscheibe 13 sitzen und die als proportional verstellbare Druckreduzierventile ausgebildet sind. Auf einen maximalen Steuerdruck von z.B. 30 bar begrenzt, wird den beiden Pilotventilen 84 und 85 Steueröl über einen Kanal 86 in der Ventilscheibe 13 zugeführt, während Steueröl über einen Kanal 87 abfließen kann.For displacement of the control piston 32 from its central position, a spring chamber in one of the two covers 48 is acted upon by a control pressure. Serve two electromagnetically actuated pilot valves 84 and 85, sitting in a manner not shown on the valve disc 13 and which are designed as proportionally adjustable pressure reducing valves. To a maximum control pressure of e.g. Limits 30 bar, the pilot valves 84 and 85 control oil is supplied via a channel 86 in the valve disc 13, while control oil can flow through a channel 87.

Um Druckmittel aus dem einfachwirkenden Hydrozylinder 12 zum Tank abfließen zu lassen, wird der Steuerkolben 32 durch Druckbeaufschlagung an seiner anderen Stirnseite in die zweite Richtung verstellt und dadurch über die Steuernuten 61 am Kolbenbund 58 ein Durchflußquerschnitt zwischen der Verbraucherkammer 38 und der Ablaufkammer 44 geöffnet. Bei Vorgabe eines bestimmten Steuerdrucks, mit dem der Steuerkolben beaufschlagt wird, soll die Senkgeschwindigkeit des hydraulischen Verbrauchers mit zunehmendem Lastdruck weniger ansteigen als es bei konstantem Durchflußquerschnitt durch die Zunahme der Druckdifferenz über den Durchflußquerschnitt bedingt wäre. Zu diesem Zweck sind die beiden Verbraucherkanäle 40 und 41 und damit die beiden Verbraucherkammern 38 und 39 über eine Bohrung 90 fluidisch miteinander verbunden, die parallel zu der Ventilbohrung 31 verläuft und die durch eine Stufenbohrung 91 des Ventilgehäuses 30 in dieses eingebracht werden kann, die der Aufnahme eines zwischen dem Verbraucherkanal 40 und einem Tankkanal 46 angeordneten Sekundärdruckbegrenzungs- und Nachsaugventils 92 dient bzw., da der hydraulische Verbraucher einfachwirkend ist, durch einen Stopfen 93 verschlossen ist. Da nur Steueröl durch die Verbindungsbohrung 90 fließt, kann deren Durchmesser klein sein. An sich kann der Fluidpfad zur Anbindung der Verbraucherkammer 39 an den Druckmittelweg zwischen der Verbraucherkammer 38 und dem hydraulischen Verbraucher auch außerhalb des Ventilgehäuses 30 liegen und über den Anschluß 43 führen. Die Verbindung innerhalb des Ventilgehäuses erscheint jedoch wesentlich einfacher. Der Anschluß 43 ist dann durch einen Stopfen 94 verschlossen.In order to drain pressure medium from the single-acting hydraulic cylinder 12 to the tank, the control piston 32 is adjusted by pressurization at its other end in the second direction and thereby opened via the control grooves 61 on the piston collar 58, a flow area between the consumer chamber 38 and the drain chamber 44. Given a certain control pressure, with which the control piston is acted upon, the lowering speed of the hydraulic consumer should increase less with increasing load pressure than would be due to the increase in pressure difference across the flow area at a constant flow area. For this purpose, the two consumer channels 40 and 41 and thus the two consumer chambers 38 and 39 fluidly connected to each other via a bore 90 which is parallel to the valve bore 31 and which can be introduced through a stepped bore 91 of the valve housing 30 in this, the Receiving a arranged between the consumer channel 40 and a tank channel 46 Sekundärdruckbegrenzungs- and Nachsaugventils 92 serves or, since the hydraulic consumer is single-acting, is closed by a plug 93. Since only control oil flows through the communication hole 90, the diameter thereof may be small. In itself, the fluid path for connecting the consumer chamber 39 to the pressure medium path between the consumer chamber 38 and the hydraulic consumer and outside of the valve housing 30 and lead over the terminal 43. However, the connection within the valve housing appears much easier. The port 43 is then closed by a plug 94.

Bei einer Verstellung des Steuerkolbens 32 in die zweite Richtung wird nach einem kurzen Anfangshub die Querbohrung 76 zu der Verbraucherkammer 39 geöffnet, in der wegen der Verbindungsbohrung 91 der Lastdruck des Hydrozylinders 12 ansteht. Der Lastdruck wirkt sodann auch in der Axialbohrung 74 und beaufschlagt die beiden Meßkolben 81 und 82, von denen sich der Meßkolben 82 am Hubbegrenzer 49 und der Meßkolben 81 mit seinem Kopf am Steuerkolben 32 abstützt. Der Lastdruck erzeugt somit eine der Ansteuerkraft entgegengerichtete Kompensationskraft am Steuerkolben. Erst wenn die Ansteuerkraft die Summe aus Kompensationskraft und Federkraft übersteigt, bewegt sich der Steuerkolben über den Anfangshub hinaus. Jetzt erst, also nach Öffnung der Querbohrung 76, öffnen die Steuernuten 61 einen Durchflußquerschnitt zwischen den beiden Steuerkammern 38 und 44. Letztendlich nimmt der Steuerkolben eine Stellung ein, in der zwischen der Ansteuerkraft einerseits und der Summe aus der Kompensationskraft und der Kraft der einen Zentrierfeder 47 ein Gleichgewicht herrscht. Der Steuerkolben ist weniger weit aus der Mittelstellung verschoben als bei einem Ventil ohne Kompensationskraft, in der der Steuerkolben bei einem vorgegebenen Steuerdruck jeweils eine solche Stellung einnimmt, in der die Ansteuerkraft gleich der Federkraft ist. Entsprechend ist der Durchflußquerschnitt zwischen der Verbraucherkammer 38 und der Ablaufkammer 44 über die Steuernuten 61 kleiner. Durch entsprechende Formgebung der Steuernuten kann erreicht werden, daß bei vorgegebenem Steuerdruck und zunehmendem Lastdruck die Zunahme der Druckdifferenz über den Durchflußquerschnitt durch eine Verringerung des Durchflußquerschnitts weitgehend ausgeglichen wird.With an adjustment of the control piston 32 in the second direction, the transverse bore 76 is opened to the consumer chamber 39 after a short initial stroke, in which due to the connecting hole 91 of the load pressure of the hydraulic cylinder 12 is present. The load pressure then acts also in the axial bore 74 and acts on the two measuring pistons 81 and 82, of which the measuring piston 82 is supported on the stroke limiter 49 and the measuring piston 81 with its head on the control piston 32. The load pressure thus generates a control force opposing compensating force on the control piston. Only when the driving force exceeds the sum of compensation force and spring force, the control piston moves beyond the initial stroke. Only now, so after opening the transverse bore 76, the control grooves 61 open a flow area between the two control chambers 38 and 44. Finally, the control piston assumes a position in which between the driving force on the one hand and the sum of the compensation force and the force of a centering spring There is an equilibrium. The control piston is moved less far from the center position than a valve without compensation force, in which the control piston at a given control pressure in each case assumes such a position in which the driving force is equal to the spring force. Accordingly, the flow area between the load chamber 38 and the drain chamber 44 via the control grooves 61 is smaller. By appropriate shaping of the control grooves can be achieved that at a given control pressure and increasing load pressure, the increase in the pressure difference across the flow area is largely compensated by a reduction in the flow area.

Anstelle einer hydraulischen Betätigung des Steuerkolbens ist das Vorsehen eines oder mehrerer Meßkolben grundsätzlich auch bei einer direkten Betätigung durch Proportionalmagnete möglich.Instead of a hydraulic actuation of the control piston, the provision of one or more measuring pistons is basically also possible in the case of a direct actuation by means of proportional solenoids.

Claims (9)

  1. A hydraulic control arrangement for control of the direction and speed of a single-acting hydraulic consumer, in particular a single-acting hydraulic cylinder (12),
    with a directional control valve (20) having a valve housing (30) and a spool bore (31) therein with a middle inlet chamber (35) to which pressure fluid can be conducted from a pressure fluid source (10), with two consumer chambers (38, 39) adjacent to the middle inlet chamber (35), and with an outlet chamber (44) via which pressure fluid can be exhausted to a tank (14),
    a control spool (32) which is situated in the spool bore (31) and which can be displaced axially, by means of an arbitrarily preselected driving force, out of a middle position in a first direction and in an opposed second direction and has first control grooves (60) for controlling the opening of a connection between the inlet chamber (35) and a first consumer chamber (38) during a displacement out of the middle position in a first direction and second control grooves (61) for controlling the opening of the connection between the first consumer chamber (38) and the outlet chamber (44) during a displacement from the middle position in the second direction, and
    a metering piston (82) interacting in such a way with the control spool (32) that when pressure is applied to the metering piston (82) and the control spool (32) is displaced in the second direction, a compensating force acting in the opposite direction to the control force can be exerted on the control spool (32), characterized by the fact that the metering piston (82) can be acted upon by the pressure prevailing in the first consumer chamber (38) when the control spool (32) is displaced in the second direction.
  2. A hydraulic control arrangement according to claim 1, characterized by the fact that a pressure space adjoining the metering surface of the metering piston (82) can be fluidically connected to the second consumer chamber (39) and that the latter is continuously connected fluidically with the first consumer chamber (38).
  3. A hydraulic control arrangement according to claim 2, characterized by the fact that the fluidic connection between the first consumer chamber (38) and the second consumer chamber (39) is located entirely within the valve housing (30).
  4. A hydraulic control arrangement according to claim 3, characterized by the fact that, within the valve housing (30), two consumer ducts (40, 41) emanating from the two consumer chambers (38, 39) and running essentially perpendicularly to the spool bore (31) and parallel to each other extend up to two connection regions (42, 43) of the valve housing (30) and that the consumer ducts (40, 41) are connected to each other by means of a connecting duct (90) running essentially parallel to the spool bore (31).
  5. A hydraulic control arrangement according to claim 3 or 4, characterized in that the valve housing (30) has a cavity (91) for a secondary pressure limiting valve (92) and that the connecting duct (90) is accessible to a drilling tool through the cavity (91).
  6. A hydraulic control arrangement according to any of the preceding claims, characterized by the fact that, running within the control spool (32) is an axial bore (74) serving to sense the load pressure of the hydraulic consumer (12), said axial bore (74) being opened via a first cross-bore (75) to the first consumer chamber (38) when the control spool (32) is displaced in the first direction and being opened via a second cross bore (76) to the second consumer chamber (39) when the control spool (32) is displaced in the second direction, that when the control spool (32) is displaced in the first direction the pressure from the axial bore (74) may be transmitted via a third cross-bore (77) into a load sensing chamber (64) and that the metering piston (82) is guided in the control spool (32) and is exposed inside the control spool (32) to the pressure prevailing in the axial bore (74) and can be supported at its outer end on an abutment (49) of the valve housing (30).
  7. A hydraulic control spool according to claim 6, characterized by the fact that, when the control spool (32) is displaced in the second direction, the axial bore (74) can be blocked off from the load sensing chamber (64).
  8. A hydraulic control arrangement according to claim 7, characterized by the fact that the control spool (32) has in the region of the first consumer chamber (38) a first spool collar (58) with first control grooves (60) and second control grooves (61), followed, in the region of the outlet chamber (44), by a first annular groove, followed by a further spool collar (71), which is in turn followed by a further annular groove (69) into which the third cross-bore (77) opens, that, separated from the outlet chamber (44) by a housing web, there extends around the spool bore (31) an annular space (63), the width of which is larger than the effective width of the further spool collar (71) and which is followed, after a further housing web, by the load sensing chamber (64), that the further spool collar (71) and the annular space (63) are situated in such a manner relative to each other that the further annular groove (69) is open to the outlet chamber (44) via a the annular space (63) when the control spool (32) is in the middle position and is separated from the outlet chamber (44) by the further spool collar (71) when the control spool (32) has moved a short distance away from the middle position, and that the width of the further annular groove (69) is only as great as necessary to ensure that the further annular groove (69) is blocked off from the load sensing chamber (64) by the further housing web when the control spool (32) is displaced in the second direction.
  9. A directional control valve (20) having a valve housing (30) and a spool bore (31) therein with a middle inlet chamber (35) to which pressure fluid can be conducted from a pressure fluid source (10), with two consumer chambers (38, 39) adjacent to the middle inlet chamber (35), and with an outlet chamber (44) via which pressure fluid can be exhausted to a tank (14), a control spool (32) which is situated in the spool bore (31) and which can be displaced axially, by means of an arbitrarily preselected driving force, out of a middle position in a first direction and in an opposed second direction and has first control grooves (60) for controlling the opening of a connection between the inlet chamber (35) and a first consumer chamber (38) during a displacement out of the middle position in a first direction and second control grooves (61) for controlling the opening of the connection between the first consumer chamber (38) and the outlet chamber (44) during a displacement from the middle position in the second direction, and
    a metering piston (82) interacting in such a way with the control spool (32) that when pressure is applied to the metering piston (82) and the control spool (32) is displaced in the second direction, a compensating force acting in the opposite direction to the control force can be exerted on the control spool (32), characterized by the fact that the metering piston (82) can be acted upon by the pressure prevailing in the first consumer chamber (38) when the control spool (32) is displaced in the second direction,
    that a pressure chamber (74) adjoining a metering surface of the metering piston (82) can be connected with the second consumer chamber (39) and the latter is continuously connected fluidically with the first consumer chamber (38), and that the fluidic connection between the first consumer chamber (38) and the second consumer chamber (39) is located entirely within the valve housing (30).
EP02742885A 2001-05-05 2002-04-11 Hydraulic control assembly for controlling the direction and speed of a single-action hydraulic consumer and a directional control valve therefor Expired - Lifetime EP1386084B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10121924 2001-05-05
DE10121924A DE10121924A1 (en) 2001-05-05 2001-05-05 Hydraulic control arrangement for controlling a single-acting hydraulic consumer with regard to direction and speed and directional valve therefor
PCT/EP2002/004022 WO2002090778A2 (en) 2001-05-05 2002-04-11 Hydraulic control assembly comprising a directional control valve for controlling the direction and speed of a single-action hydraulic consumer

Publications (2)

Publication Number Publication Date
EP1386084A2 EP1386084A2 (en) 2004-02-04
EP1386084B1 true EP1386084B1 (en) 2006-01-11

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EP02742885A Expired - Lifetime EP1386084B1 (en) 2001-05-05 2002-04-11 Hydraulic control assembly for controlling the direction and speed of a single-action hydraulic consumer and a directional control valve therefor

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EP (1) EP1386084B1 (en)
AT (1) ATE315728T1 (en)
DE (2) DE10121924A1 (en)
DK (1) DK1386084T3 (en)
WO (1) WO2002090778A2 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2311686A1 (en) * 2009-10-15 2011-04-20 Hyva International B.V. Tip valve
FI20115108L (en) * 2011-02-03 2012-08-04 Parker Hannifin Mfg Finland Oy Directional valve with pressure control
DE102011120302A1 (en) * 2011-12-03 2013-06-06 Robert Bosch Gmbh Hydraulic directional control valve for the hoist of an agricultural vehicle
DE102013017093A1 (en) 2013-10-15 2015-04-16 Hydac Filtertechnik Gmbh control device
CN105570220B (en) 2014-10-17 2017-08-11 徐工集团工程机械股份有限公司 Banked direction control valves and hydraulic flow shared system

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DE19631803B4 (en) 1996-08-07 2007-08-02 Bosch Rexroth Aktiengesellschaft Hydraulic control device

Also Published As

Publication number Publication date
DK1386084T3 (en) 2006-05-22
DE10121924A1 (en) 2002-11-07
DE50205586D1 (en) 2006-04-06
WO2002090778A3 (en) 2003-02-20
EP1386084A2 (en) 2004-02-04
ATE315728T1 (en) 2006-02-15
WO2002090778A2 (en) 2002-11-14

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