EP1360419B1 - Distributing valve for the load-independent control of a hydraulic consumer in terms of direction and speed - Google Patents

Distributing valve for the load-independent control of a hydraulic consumer in terms of direction and speed Download PDF

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Publication number
EP1360419B1
EP1360419B1 EP02702315A EP02702315A EP1360419B1 EP 1360419 B1 EP1360419 B1 EP 1360419B1 EP 02702315 A EP02702315 A EP 02702315A EP 02702315 A EP02702315 A EP 02702315A EP 1360419 B1 EP1360419 B1 EP 1360419B1
Authority
EP
European Patent Office
Prior art keywords
chamber
control
consumer
spool
piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02702315A
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German (de)
French (fr)
Other versions
EP1360419A1 (en
Inventor
Peter BÜTTNER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Rexroth AG
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Bosch Rexroth AG
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Publication date
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1360419A1 publication Critical patent/EP1360419A1/en
Application granted granted Critical
Publication of EP1360419B1 publication Critical patent/EP1360419B1/en
Anticipated expiration legal-status Critical
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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
    • 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
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
    • F15B2211/30—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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/76—Control of force or torque of the output member
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86694—Piston valve
    • Y10T137/8671—With annular passage [e.g., spool]
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87177—With bypass
    • Y10T137/87185—Controlled by supply or exhaust valve

Definitions

  • the invention is based on a directional control valve that is used for load-independent control of a hydraulic consumer in terms of direction and speed serves and which has the features from the preamble of claim 1.
  • Such a directional valve is from the data sheet RD 64282 / 10.99 from the applicant known.
  • the directional valve then has a piston bore in a valve housing one from a central position axially in opposite directions sliding control piston with which the pressure medium paths between an inlet chamber, the pressure medium can be supplied from a pressure medium source, two together connected drainage chambers via which pressure medium can be discharged to a tank is, and two consumer chambers are controllable.
  • the control piston points first fine control grooves for opening a connection between a consumer chamber and the inlet chamber and second fine control grooves for opening a connection between a consumer chamber and a drain chamber on.
  • the directional control valve which differ in their design of the control piston.
  • Control piston in its central position from all valve chambers against each other.
  • This Variant can also be described as a variant with a locked middle position.
  • a second variant is a throttled connection in the middle position or residual opening between the two consumer chambers and the drain chambers.
  • This variant can also be used as a variant with a relieved middle position describe.
  • control piston is the variant with a relieved center position compared to the control piston, which in the middle position the existing consumer chambers shuts off, the second fine control grooves extended so far that they protrude into the consumer chambers when the control piston is in the middle position.
  • the disadvantage here is that with valve actuation at the beginning of the opening the first fine control grooves the flow cross-section between the inlet chamber and the one consumer chamber in comparison to the flow cross section between the other consumer chamber and a drain chamber very much is small. A sensitive control and a clamped procedure of the hydraulic Consumer is not possible in this stroke range.
  • the invention has for its object a directional control valve that features the preamble of claim 1 has to develop so that a sensitive one even at the beginning of the opening of the first fine control grooves Control of the hydraulic consumer is possible and that the effort for the design of the fine control grooves is reduced.
  • the desired goal can be with a generic directional valve after the Achieve the invention in that, as in the characterizing part of the claim 1, the relief connection is independent of the second fine control grooves via a recess of the control piston and that when the control piston moves in the sense of a connection Consumer chamber with a drain chamber interrupted the relief connection is before the second fine control grooves open a flow cross section. Accordingly, in the variant with a relieved center position, the second fine control grooves nothing to do with the relief of a consumer chamber. Your Interpretation can therefore be based solely on the desired control of the hydraulic dimensions necessary for the consumer. At a given maximum flow rate, the second fine control grooves for the Valve variant with relieved middle position and for the valve variant with locked Middle position be the same.
  • the recess is in the central position of the control piston directly to both a consumer chamber and a drain chamber is open and is in the event of a displacement of the control piston from the Locked middle position to one of the chambers. So here is the throttled Relief in a short way through the recess alone.
  • the recess can be a recess, which in addition to the Known directional valve already provided recesses on the control piston becomes.
  • a recess which also known directional control valves already have, namely a recess, which serves to report a load pressure, slightly So changed that they bring relief to the consumer chamber can.
  • the relief can take place directly via the recess. This appears in the case of a directional control valve, as is described in DE 38 without a relieved middle position 41 507 C1 or from EP 0 786 598 is known and in which the load message via radial channels of the control piston takes place in the area of the housing webs between the consumer chambers and the drainage chambers are particularly useful. There are there to make the radial channels in the outer mouth area axially only so large that they are both in the middle position of the control piston to the consumer chambers as well as open to the drain chamber.
  • a continuously adjustable directional valve passes through a valve housing 20, that within a load-sensing control for one hydraulic consumer is used, a piston bore 21 through, in which a control piston 22 is axially movable.
  • the length of the spool 22 agrees with the length of the piston bore 21 from one end face 23 to other end face 24 of the valve housing 20.
  • the piston bore 21 is surrounded by five axially spaced control chambers, the inflow of pressure medium to and the drain from a hydraulic consumer serve and their connections to each other controlled by the control piston 22 become.
  • the middle of the five control chambers is the inlet chamber 27.
  • An outlet chamber 32 follows each consumer chamber 28 or 29 or 33, which are not closer to one passing through the valve housing 20 tank channel shown is open.
  • the control piston 22 takes due to two not shown centering springs attached to the end faces 23 and 24 of the valve housing 20 and the piston bore 21 outward-closing lids are housed, one Middle position. In this middle position, two piston collars 34 and 35 lock of the control piston 22, between which there is an inlet chamber 27 Piston neck 36 with circumferential annular groove 37, the two consumer chambers 28 and 29 against the inlet chamber 27.
  • the two piston collars 34 and 35 are so long that they are in the middle position of the control piston, the consumer chambers 28 and 29 also along the housing webs 38 from the drain chambers able to separate.
  • Each piston collar 34 or 35 is followed by another Piston neck 39 or 40 with an annular groove 41 or 42, each in the area a drain chamber is located. Another is connected to the piston neck 40 Piston collar 43 on the spring chamber in the one cover against the drain chamber 33 seals.
  • the distance between the drain chamber 32 and the end face 23 is greater than the distance between the drain chamber 33 and the end face 24 of the valve housing 20.
  • Between the drain chamber 32 and the end face 23 are in the piston bore 21 has three axially spaced annular chambers 44, 45 and 46, the middle of these three chambers being referred to as the load reporting chamber 45 is because from there the load pressure to an assigned to the directional control valve however, not shown individual pressure compensator and, if the load pressure is the highest is reported to a pump controller.
  • The, from the load reporting chamber 45 viewed from, to the end face 23 of the valve housing 20 lying annular chamber 44 can be connected to the input of a pressure relief valve.
  • a pressure relief valve can be connected.
  • the control piston 22 extends to the piston neck 39 following piston section from the front side 23 of the valve housing 20 to in the area of the housing web 47 between the annular chamber 46 and the drain chamber 32.
  • a flat annular groove 49 is screwed into this piston section, via the three ring chambers 44, 45 in the central position of the control piston 22 and 46 are interconnected.
  • a piston collar 48 Between the ring groove 49 and the piston neck 39 there is a piston collar 48, the effective sealing length of which is less than is the width of the annular chamber 46.
  • the piston collar 48 has on the drain chamber 32 facing outer edge two diametrically opposite each other Milling 50 through which the annular chamber 46 and drain chamber 32 with Small opening cross-section are open to each other when the control piston 22 is in its central position.
  • the control piston 22 is out of its central position moved out, the load reporting chamber 45 depending on the direction of movement of the control piston from the annular chamber 44 or from the annular chamber 46 Cut.
  • the load reporting chamber 45 to drain chamber 32 closed by the load reporting chamber 45 from the annular chamber 46 or the annular chamber 46 from the drain chamber 32 is separated.
  • the Cross section becomes larger towards the front edges.
  • the fine control grooves are enough from the front edges only so far into the piston collars that their inner End in the central position of the control piston 22 still a distance from the consumer chambers 28 or 29 has. Are in the central position of the control piston 22 So the consumer chambers via the fine control grooves neither with the inlet chamber 27 still fluidly connected to the adjacent drain chamber 32 or 33.
  • An axial bore 57 passes through the control piston 22 and connects to the two Ends is closed.
  • the control piston 22 has in the region of the annular groove 49 a narrow radial bore 62 which extends from the outside to the axial bore 57 and which acts as a nozzle or throttle.
  • the axial bore 57 is also two Radial bores 58 and 59 crossed, of which the radial bore 58 through the Piston collar 34 and the radial bore 59 through the piston collar 35 of the control piston 22 passes through.
  • the radial bores 58 and 59 are in the axial Seen direction, are still within the extent of the fine control grooves 55 but offset by 90 degrees to these.
  • the connection is over the nozzle action of the radial bore 62 a throttled connection. about the connection can thus be hydraulic fluid in one from the consumer chambers small current flow to the drain chamber 32 and thus to a tank. This relieves the consumer chambers of pressure, so that for example Check or brake valves between the consumer chambers and one hydraulic consumers are arranged to work safely. A burden that is supported on a consumer chamber if there is no check valve, moves slowly.
  • the consumer chambers are relieved without including the fine tax slots 56, so that they can be designed exactly as with a directional control valve without throttled relief of the middle position. From the spool one Such a directional control valve differs from the control piston 22 of the exemplary embodiment of the invention according to FIG. 1 only through the additional blind bores 60 and 61.
  • control piston 22 moves out of the middle position, in the view according to FIG. 1 For example, moved to the right, the blind holes 60 are covered and the flow area between them and the consumer chamber 28 closed before this consumer chamber via the fine control grooves 56 is connected to the drain chamber 32 on the piston collar 34. Is locked also the connection between the annular groove 49 on the control piston 22 and the Drain chamber 32.
  • the radial bore 59 remains to the consumer chamber 29, which is now connected to the inlet chamber 27 via the fine control grooves 55 is open so that a load message is possible.
  • the blind holes 61 covers and the radial bores 58 remain open to the consumer chamber 28.
  • the radial bores 58 and 59 are sufficient except for the outside of the piston collars 34 and 35 and are in the middle position of the control piston 22 covered by the piston bore 21.
  • the throttled For the throttled everyone has discharge of the consumer chambers 28 and 29 in the middle position Piston collar 34 and 35 two opposite, axially extending, Narrow grooves 70 and 71 on the 22 in the central position of the control piston along the housing webs 38 an immediate throttled connection between the consumer chambers and the drainage chambers.
  • the grooves 70 and 71 only extend as far into the consumer chambers and the drain chambers into that fluid communication through them interrupted when the control piston 22 moves from the central position before fine control grooves 55 and 56 open to the consumer chambers.
  • the throttled also takes place Relief for the consumer chambers without the inclusion of fine tax slots 56.

Abstract

A directional control valve for a hydraulic load has, in a piston bore of a valve housing, a control piston which can be displaced axially in opposite directions from a central position and which has first fine control grooves for opening a connection between a load chamber and a feed chamber. There are second fine control grooves for opening a connection between a load chamber and a discharge chamber of the piston bore under control. In its central position, there is a restricted relief connection from a load chamber to the discharge chamber via the control piston. The restricted relief connection is obtained via a recess in the control piston, independently of the second fine control grooves.

Description

Die Erfindung geht aus von einem Wegeventil, das zur lastunabhängigen Steuerung eines hydraulischen Verbrauchers hinsichtlich Richtung und Geschwindigkeit dient und das die Merkmale aus dem Oberbegriff des Patentanspruchs 1 aufweist.The invention is based on a directional control valve that is used for load-independent control of a hydraulic consumer in terms of direction and speed serves and which has the features from the preamble of claim 1.

Ein solches Wegeventil ist aus dem Datenblatt RD 64282/10.99 der Anmelderin bekannt. Danach besitzt das Wegeventil in einer Kolbenbohrung eines Ventilgehäuses einen von einer Mittelstellung aus axial in entgegengesetzte Richtungen verschiebbaren Steuerkolben, mit dem die Druckmittelwege zwischen einer Zulaufkammer, der Druckmittel von einer Druckmittelquelle zuführbar ist, zwei miteinander verbundenen Ablaufkammern, über die Druckmittel zu einem Tank abführbar ist, und zwei Verbraucherkammern steuerbar sind. Der Steuerkolben weist erste Feinsteuernuten zum Aufsteuern einer Verbindung zwischen einer Verbraucherkammer und der Zulaufkammer und zweite Feinsteuernuten zum Aufsteuern einer Verbindung zwischen einer Verbraucherkammer und einer Ablaufkammer auf. Für das Wegeventil gibt es unterschiedliche Varianten, die sich in der Ausbilden des Steuerkolbens voneinander unterscheiden. Bei einer Variante sperrt der Steuerkolben in seiner Mittelstellung alle Ventilkammern gegeneinander ab. Diese Variante kann man auch als Variante mit gesperrter Mittelstellung bezeichnen. Bei einer zweiten Variante besteht in der Mittelstellung eine gedrosselte Verbindung oder Restöffnung zwischen den beiden Verbraucherkammern und den Ablaufkammern. Diese Variante kann man auch als Variante mit entlasteter Mittelstellung bezeichnen.Such a directional valve is from the data sheet RD 64282 / 10.99 from the applicant known. The directional valve then has a piston bore in a valve housing one from a central position axially in opposite directions sliding control piston with which the pressure medium paths between an inlet chamber, the pressure medium can be supplied from a pressure medium source, two together connected drainage chambers via which pressure medium can be discharged to a tank is, and two consumer chambers are controllable. The control piston points first fine control grooves for opening a connection between a consumer chamber and the inlet chamber and second fine control grooves for opening a connection between a consumer chamber and a drain chamber on. There are different variants for the directional control valve, which differ in their design of the control piston. In one variant, the Control piston in its central position from all valve chambers against each other. This Variant can also be described as a variant with a locked middle position. at a second variant is a throttled connection in the middle position or residual opening between the two consumer chambers and the drain chambers. This variant can also be used as a variant with a relieved middle position describe.

In der Praxis sind bei dem Steuerkolben der Variante mit entlasteter Mittelstellung im Vergleich zu dem Steuerkolben, der in der Mittelstellung die vorhandenen Verbraucherkammern absperrt, die zweiten Feinsteuernuten soweit verlängert, daß sie schon in der Mittelstellung des Steuerkolbens in die Verbraucherkammern hineinragen. Nachteilig ist dabei, daß bei einer Ventilbetätigung zu Beginn der Öffnung der ersten Feinsteuernuten der Durchflußquerschnitt zwischen der Zulaufkammer und der einen Verbraucherkammer im Vergleich zu dem Durchflußquerschnitt zwischen der anderen Verbraucherkammer und einer Ablaufkammer sehr klein ist. Eine feinfühlige Steuerung und ein eingespanntes Verfahren des hydraulischen Verbrauchers ist in diesem Hubbereich nicht möglich. Sind zwischen dem Wegeventil und dem hydraulischen Verbraucher noch Sperrventile oder Bremsventile geschaltet, so ist ein hoher Aufwand für die Abstimmung dieser Ventile zu den Durchflußquerschnitten am Wegeventil zu leisten. Nachteilig ist auch, daß gegenüber einem Steuerkolben mit gesperrter Mittelstellung eine völlig neue Auslegung der zweiten Feinsteuernuten notwendig ist.In practice, the control piston is the variant with a relieved center position compared to the control piston, which in the middle position the existing consumer chambers shuts off, the second fine control grooves extended so far that they protrude into the consumer chambers when the control piston is in the middle position. The disadvantage here is that with valve actuation at the beginning of the opening the first fine control grooves the flow cross-section between the inlet chamber and the one consumer chamber in comparison to the flow cross section between the other consumer chamber and a drain chamber very much is small. A sensitive control and a clamped procedure of the hydraulic Consumer is not possible in this stroke range. Are between that Directional control valve and the hydraulic consumer still check valves or brake valves switched, so there is a high effort for the coordination of these valves to make the flow cross-sections at the directional valve. Another disadvantage is that a control piston with locked middle position a completely new design the second fine control grooves is necessary.

Der Erfindung liegt die Aufgabe zugrunde, ein Wegeventil, das die Merkmale aus dem Oberbegriff des Patentanspruchs 1 aufweist, so weiterzuentwickeln, daß auch schon zu Beginn der Öffnung der ersten Feinsteuernuten eine feinfühlige Steuerung des hydraulischen Verbrauchers möglich, ist und daß der Aufwand für die Auslegung der Feinsteuernuten verringert ist.The invention has for its object a directional control valve that features the preamble of claim 1 has to develop so that a sensitive one even at the beginning of the opening of the first fine control grooves Control of the hydraulic consumer is possible and that the effort for the design of the fine control grooves is reduced.

Das angestrebte Ziel läßt sich bei einem gattungsgemäßen Wegeventil nach der Erfindung dadurch erreichen, daß, wie dies im kennzeichnenden Teil des Patentanspruchs 1 angegeben ist, die Entlastungsverbindung unabhängig von den zweiten Feinsteuernuten über eine Ausnehmung des Steuerkolbens besteht und daß bei einer Verschiebung des Steuerkolbens im Sinne einer Verbindung einer Verbraucherkammer mit einer Ablaufkammer die Entlastungsverbindung unterbrochen wird, bevor die zweiten Feinsteuernuten einen Durchflußquerschnitt öffnen. Demnach haben bei der Variante mit entlasteter Mittelstellung die zweiten Feinsteuernuten nichts mehr mit der Entlastung einer Verbraucherkammer zu tun. Ihre Auslegung kann sich deshalb allein nach den für die gewünschte Steuerung des hydraulischen Verbrauchers notwendigen Dimensionen richten. Bei einer vorgegebenen maximalen Durchflußmenge können die zweiten Feinsteuernuten für die Ventifväriante mit entlasteter Mittelstellung und für die Ventilvariante mit gesperrter Mittelstellung gleich sein.The desired goal can be with a generic directional valve after the Achieve the invention in that, as in the characterizing part of the claim 1, the relief connection is independent of the second fine control grooves via a recess of the control piston and that when the control piston moves in the sense of a connection Consumer chamber with a drain chamber interrupted the relief connection is before the second fine control grooves open a flow cross section. Accordingly, in the variant with a relieved center position, the second fine control grooves nothing to do with the relief of a consumer chamber. Your Interpretation can therefore be based solely on the desired control of the hydraulic dimensions necessary for the consumer. At a given maximum flow rate, the second fine control grooves for the Valve variant with relieved middle position and for the valve variant with locked Middle position be the same.

Vorteilhafte Ausgestaltungen eines erfindungsgemäßen Wegeventils kann man den Unteransprüchen entnehmen.Advantageous embodiments of a directional control valve according to the invention can be used take from the subclaims.

Gemäß Patentanspruch 2 ist die Ausnehmung in der Mittelstellung des Steuerkolbens unmittelbar sowohl zu einer Verbraucherkammer als auch zu einer Ablaufkammer hin offen ist und wird bei einer Verschiebung des Steuerkolbens aus der Mittelstellung zu einer der Kammern hin abgesperrt. Hier erfolgt also die gedrosselte Entlastung auf kurzem Weg allein über die Ausnehmung.According to claim 2, the recess is in the central position of the control piston directly to both a consumer chamber and a drain chamber is open and is in the event of a displacement of the control piston from the Locked middle position to one of the chambers. So here is the throttled Relief in a short way through the recess alone.

Die Ausnehmung kann eine Ausnehmung sein, die zusätzlich zu den auch beim bekannten Wegeventil schon vorhandenen Ausnehmungen am Steuerkolben vorgesehen wird. In besonders bevorzugter Weise wird jedoch gemäß Patentanspruch 3 eine Ausnehmung, die auch bekannte Wegeventile schon haben, nämlich eine Ausnehmung, die der Meldung eines Lastdrucks dient, in geringfügiger Weise so verändert, däß sie die Entlastung der Verbraucherkammer herbeizuführen vermag.The recess can be a recess, which in addition to the Known directional valve already provided recesses on the control piston becomes. In a particularly preferred manner, however, according to claim 3 a recess, which also known directional control valves already have, namely a recess, which serves to report a load pressure, slightly So changed that they bring relief to the consumer chamber can.

Dabei kann die Entlastung unmittelbar über die Ausnehmung geschehen. Dies erscheint bei einem Wegeventil, wie es ohne entlastete Mittelstellung aus der DE 38 41 507 C1 oder aus der EP 0 786 598 bekannt ist und bei dem die Lastmeldung über Radialkanäle des Steuerkolbens erfolgt, die sich im Bereich der Gehäusestege zwischen den Verbraucherkammern und den Ablaufkammern befinden, besonders zweckmäßig. Es sind dort die Radialkanäle im äußeren Mündungsbereich axial nur so groß zu machen, daß sie in der Mittelstellung des Steuerkolbens sowohl zur Verbraucherkämmer als auch zur Ablaufkammer öffen sind.The relief can take place directly via the recess. This appears in the case of a directional control valve, as is described in DE 38 without a relieved middle position 41 507 C1 or from EP 0 786 598 is known and in which the load message via radial channels of the control piston takes place in the area of the housing webs between the consumer chambers and the drainage chambers are particularly useful. There are there to make the radial channels in the outer mouth area axially only so large that they are both in the middle position of the control piston to the consumer chambers as well as open to the drain chamber.

Bei einer Lastmeldung, wie sie bei dem Wegeventil nach dem Datenblatt oder bei einem aus der EP 0 638 730 A1 bekannten Wegeventil gemacht wird, erhält man gemäß den Patentansprüchen 3, 4 und 5 unter Einbeziehung des Fluidpfades für die Lastmeldung und durch eine Anpassung des den Druck in der Verbraucherkammer abgreifenden Radialkanals ebenfalls auf einfache Weise eine Entlastung einer Verbraucherkammer.In the case of a load message, as in the directional control valve according to the data sheet or in a directional control valve known from EP 0 638 730 A1 is obtained according to claims 3, 4 and 5 including the fluid path for the load message and by adjusting the pressure in the consumer chamber tapping radial channel also a relief in a simple manner a consumer chamber.

Zwei Ausführungsbeispiele eines erfindungsgemäßen Wegeventils sind in den Zeichnungen dargestellt. Anhand der Figuren dieser Zeichnungen wird die Erfindung nun näher erläutert.Two embodiments of a directional control valve according to the invention are in the Drawings shown. The invention is illustrated by the figures in these drawings now explained in more detail.

Es zeigen

Figur 1
das erste Ausführungsbeispiel, bei dem die Verbraucherkammern über den Fluidpfad zur Lastmeldung entlastet werden, und
Figur 2
das zweite Ausführungsbeispiel, bei dem die Verbraucherkammern über zusätzliche Ausnehmungen des Steuerkolbens entlastet werden.
Show it
Figure 1
the first embodiment, in which the consumer chambers are relieved via the fluid path for load reporting, and
Figure 2
the second embodiment in which the consumer chambers are relieved via additional recesses in the control piston.

Nach den Figuren geht durch ein Ventilgehäuse 20 eines stetig verstellbaren Wegeventils, das innerhalb einer lastfühlenden (load-sensing) Steuerung für einen hydraulischen Verbraucher verwendet wird, eine Kolbenbohrung 21 hindurch, in der ein Steuerkolben 22 axial bewegbar ist. Die Länge des Steuerkolbens 22 stimmt mit der Länge der Kolbenbohrung 21 von der einen Stirnseite 23 bis zur anderen Stirnseite 24 des Ventilgehäuses 20 überein. Die Kolbenbohrung 21 ist von fünf axial voneinander beabstandeten Steuerkammern umgeben, die dem Zufluß von Druckmittel zu und dem Abfluß von einem hydraulischen Verbraucher dienen und deren Verbindungen untereinander von dem Steuerkolben 22 gesteuert werden. Die mittlere der fünf Steuerkammern ist die Zulaufkammer 27. Beidseits dieser Zulaufkammer befindet sich jeweils eine Verbraucherkammer 28 bzw. 29. Auf jede Verbraucherkammer 28 bzw. 29 folgt noch eine Ablaufkammer 32 bzw. 33, die zu einem durch das Ventilgehäuse 20 hindurchgehenden nicht näher dargestellten Tankkanal offen ist. According to the figures, a continuously adjustable directional valve passes through a valve housing 20, that within a load-sensing control for one hydraulic consumer is used, a piston bore 21 through, in which a control piston 22 is axially movable. The length of the spool 22 agrees with the length of the piston bore 21 from one end face 23 to other end face 24 of the valve housing 20. The piston bore 21 is surrounded by five axially spaced control chambers, the inflow of pressure medium to and the drain from a hydraulic consumer serve and their connections to each other controlled by the control piston 22 become. The middle of the five control chambers is the inlet chamber 27. On both sides there is a consumer chamber 28 or this feed chamber 29. An outlet chamber 32 follows each consumer chamber 28 or 29 or 33, which are not closer to one passing through the valve housing 20 tank channel shown is open.

Der Steuerkolben 22 nimmt aufgrund von zwei nicht gezeigten Zentrierfedern, die in an den Stirnseiten 23 und 24 des Ventilgehäuses 20 befestigten und die Kolbenbohrung 21 nach außen verschließenden Deckeln untergebracht sind, eine Mittelstellung ein. In dieser Mittelstellung sperren zwei Kolbenbunde 34 und 35 des Steuerkolbens 22, zwischen denen sich im Bereich der Zulaufkammer 27 ein Kolbenhals 36 mit umlaufender Ringnut 37 befindet, die beiden Verbraucherkammern 28 und 29 gegen die Zulaufkammer 27 ab. Die beiden Kolbenbunde 34 und 35 sind so lang, daß sie an sich in der Mittelstellung des Steuerkolbens die Verbraucherkammern 28 und 29 auch entlang der Gehäusestege 38 von den Ablaufkammern zu trennen vermögen. Auf jeden Kolbenbund 34 bzw. 35 folgt ein weiterer Kolbenhals 39 bzw. 40 mit einer Ringnut 41 bzw. 42, der sich jeweils im Bereich einer Ablaufkammer befindet. An den Kolbenhals 40 schließt sich ein weiterer Kolbenbund 43 an, der den Federraum in dem einen Deckel gegen die Ablaufkammer 33 abdichtet.The control piston 22 takes due to two not shown centering springs attached to the end faces 23 and 24 of the valve housing 20 and the piston bore 21 outward-closing lids are housed, one Middle position. In this middle position, two piston collars 34 and 35 lock of the control piston 22, between which there is an inlet chamber 27 Piston neck 36 with circumferential annular groove 37, the two consumer chambers 28 and 29 against the inlet chamber 27. The two piston collars 34 and 35 are so long that they are in the middle position of the control piston, the consumer chambers 28 and 29 also along the housing webs 38 from the drain chambers able to separate. Each piston collar 34 or 35 is followed by another Piston neck 39 or 40 with an annular groove 41 or 42, each in the area a drain chamber is located. Another is connected to the piston neck 40 Piston collar 43 on the spring chamber in the one cover against the drain chamber 33 seals.

Der Abstand zwischen der Ablaufkammer 32 und der Stirnseite 23 ist größer als der Abstand zwischen der Ablaufkammer 33 und der Stirnseite 24 des Ventilgehäuses 20. Zwischen der Ablaufkammer 32 und der Stirnseite 23 befinden sich in der Kolbenbohrung 21 drei axial voneinander beabstandete Ringkammern 44, 45 und 46, wobei die mittlere dieser drei Kammern als Lastmeldekammer 45 bezeichnet sei, weil von dort aus der Lastdruck an eine dem Wegeventil zugeordnete, jedoch nicht gezeigte Individualdruckwaage und, falls der Lastdruck der höchste ist, an einen Pumpenregler gemeldet wird. Die, von der Lastmeldekammer 45 aus betrachtet, zur Stirnseite 23 des Ventilgehäuses 20 hin liegende Ringkammer 44 kann an den Eingang eines Druckbegrenzungsventils angeschlossen sein. Auch an die zwischen der Lastmeldekammer 45 und der Ablaufkammer 32 liegende Ringkammer 46 kann ein Druckbegrenzungsventil angeschlossen werden. In der gezeigten Mittelstellung des Steuerkolbens 22 reicht ein dem Kolbenhals 39 folgender Kolbenabschnitt von der Stirnseite 23 des Ventilgehäuses 20 aus bis in den Bereich des Gehäusesteges 47 zwischen der Ringkammer 46 und der Ablaufkammer 32. In diesen Kolbenabschnitt ist eine flache Ringnut 49 eingedreht, über die in der Mittelstellung des Steuerkolbens 22 alle drei Ringkammern 44, 45 und 46 miteinander verbunden sind. Zwischen der Ringnut 49 und dem Kolbenhals 39 ist ein Kolbenbund 48 vorhanden, dessen wirksame Dichtlänge kleiner als die Breite der Ringkammer 46 ist. Der Kolbenbund 48 besitzt an seiner der Ablaufkammer 32 zugekehrten Außenkante zwei einander diametral gegenüberliegende Einfräsungen 50, durch die die Ringkammer 46 und Ablaufkammer 32 mit kleinem Öffnungsquerschnitt zueinander offen sind, wenn sich der Steuerkolben 22 in seiner Mittelstellung befindet. Wird der Steuerkolben 22 aus seiner Mittelstellung herausbewegt, so wird die Lastmeldekammer 45 je nach Bewegungsrichtung des Steuerkolbens von der Ringkammer 44 oder von der Ringkammer 46 getrennt. Außerdem wird unabhängig von der Bewegungsrichtung die in der Mittelstellung des Steuerkolbens 22 über die Ringkammer 46 bestehende Verbindung der Lastmeldekammer 45 zu Ablaufkammer 32 geschlossen, indem die Lastmeldekammer 45 von der Ringkammer 46 oder die Ringkammer 46 von der Ablaufkammer 32 getrennt wird.The distance between the drain chamber 32 and the end face 23 is greater than the distance between the drain chamber 33 and the end face 24 of the valve housing 20. Between the drain chamber 32 and the end face 23 are in the piston bore 21 has three axially spaced annular chambers 44, 45 and 46, the middle of these three chambers being referred to as the load reporting chamber 45 is because from there the load pressure to an assigned to the directional control valve however, not shown individual pressure compensator and, if the load pressure is the highest is reported to a pump controller. The, from the load reporting chamber 45 viewed from, to the end face 23 of the valve housing 20 lying annular chamber 44 can be connected to the input of a pressure relief valve. Also to the one between the load reporting chamber 45 and the drain chamber 32 Annular chamber 46, a pressure relief valve can be connected. In the shown central position of the control piston 22 extends to the piston neck 39 following piston section from the front side 23 of the valve housing 20 to in the area of the housing web 47 between the annular chamber 46 and the drain chamber 32. A flat annular groove 49 is screwed into this piston section, via the three ring chambers 44, 45 in the central position of the control piston 22 and 46 are interconnected. Between the ring groove 49 and the piston neck 39 there is a piston collar 48, the effective sealing length of which is less than is the width of the annular chamber 46. The piston collar 48 has on the drain chamber 32 facing outer edge two diametrically opposite each other Milling 50 through which the annular chamber 46 and drain chamber 32 with Small opening cross-section are open to each other when the control piston 22 is in its central position. The control piston 22 is out of its central position moved out, the load reporting chamber 45 depending on the direction of movement of the control piston from the annular chamber 44 or from the annular chamber 46 Cut. In addition, regardless of the direction of movement in the middle position of the control piston 22 via the annular chamber 46 existing connection the load reporting chamber 45 to drain chamber 32 closed by the load reporting chamber 45 from the annular chamber 46 or the annular chamber 46 from the drain chamber 32 is separated.

An beiden Stirnseiten eines jeden der beiden Kolbenbunde 34 und 35 befinden sich einander diametral gegenüberliegend zwei Feinsteuernuten 55 bzw. 56, deren Querschnitt zu den Stirnkanten hin größer wird. Die Feinsteuernuten reichen von den Stirnkanten aus nur soweit in die Kolbenbunde hinein, daß ihr inneres Ende in der Mittelstellung des Steuerkolbens 22 noch einen Abstand von den Verbraucherkammern 28 bzw. 29 hat. In der Mittelstellung des Steuerkolbens 22 sind also die Verbraucherkammern über die Feinsteuernuten weder mit der Zulaufkammer 27 noch mit der benachbarten Ablaufkammer 32 bzw. 33 fluidisch verbunden.Located on both ends of each of the two piston collars 34 and 35 diametrically opposite each other two fine control grooves 55 and 56, the Cross section becomes larger towards the front edges. The fine control grooves are enough from the front edges only so far into the piston collars that their inner End in the central position of the control piston 22 still a distance from the consumer chambers 28 or 29 has. Are in the central position of the control piston 22 So the consumer chambers via the fine control grooves neither with the inlet chamber 27 still fluidly connected to the adjacent drain chamber 32 or 33.

Durch den Steuerkolben 22 geht eine Axialbohrung 57 hindurch, die an den beiden Enden verschlossen ist. Im Bereich der Ringnut 49 weist der Steuerkolben 22 eine enge Radialbohrung 62 auf, die von außen bis in die Axialbohrung 57 reicht und die als Düse oder Drossel wirkt. Die Axialbohrung 57 wird außerdem von zwei Radialbohrungen 58 und 59 gekreuzt, von denen die Radialbohrung 58 durch den Kolbenbund 34 und die Radialbohrung 59 durch den Kolbenbund 35 des Steuerkolbens 22 hindurchgeht. Die Radialbohrungen 58 und 59 befinden sich, in axialer Richtung gesehen, noch innerhalb der Erstreckung der Feinsteuernuten 55, sind jedoch gegenüber diesen um 90 Grad versetzt. Sie haben einen solchen Durchmesser und von der der Zulaufkammer 27 zugewandten Stirnkante des jeweiligen Kolbenbundes 34 bzw. 35 einen solchen Abstand, daß sie an sich in der Mittelstellung des Steuerkolbens 22 in einem geringen Abstand zu einer Verbraucherkammer 28, 29 von der Wand der Kolbenbohrung 21 überdeckt wären. Bei dem Ausführungsbeispiel nach Figur 2 ist dies der Fall.An axial bore 57 passes through the control piston 22 and connects to the two Ends is closed. The control piston 22 has in the region of the annular groove 49 a narrow radial bore 62 which extends from the outside to the axial bore 57 and which acts as a nozzle or throttle. The axial bore 57 is also two Radial bores 58 and 59 crossed, of which the radial bore 58 through the Piston collar 34 and the radial bore 59 through the piston collar 35 of the control piston 22 passes through. The radial bores 58 and 59 are in the axial Seen direction, are still within the extent of the fine control grooves 55 but offset by 90 degrees to these. They have such a diameter and from the end edge of the respective one facing the inlet chamber 27 Piston collar 34 and 35 such a distance that they are in the middle position of the control piston 22 at a short distance from a consumer chamber 28, 29 would be covered by the wall of the piston bore 21. In which This is the case for the exemplary embodiment according to FIG. 2.

Bei dem Ausführungsbeispiel nach Figur 1 allerdings ist exzentrisch an den beiden gegenüberliegenden Mündungen jeder Radialbohrung 58 und 59 und die Radialbohrungen überdeckend eine Sackbohrung 60 bzw. 61 geringer Tiefe eingebracht, deren Durchmesser größer als der Durchmesser der Radialbohrungen ist. In der Mittelstellung des Steuerkolbens 22 besteht zwischen den Sackbohrungen 60 und der Verbraucherkammer 28 und zwischen den Sackbohrungen 61 und der Verbraucherkammer 29 ein Durchflußquerschnitt.In the embodiment of Figure 1, however, is eccentric on the two opposite mouths of each radial bore 58 and 59 and the radial bores overlying a blind hole 60 or 61 of shallow depth, whose diameter is larger than the diameter of the radial bores. In the The central position of the control piston 22 exists between the blind bores 60 and the consumer chamber 28 and between the blind bores 61 and the consumer chamber 29 a flow cross section.

Somit sind bei dem Ausführungsbeispiel nach Figur 1 in der Mittelstellung des Steuerkolbens 22 die Verbraucherkammer 28 über die Sackbohrungen 60 und die Radialbohrung 58 und die Verbraucherkammer 29 über die Sackbohrungen 61 und die Radialbohrung 59 sowie ebenso wie die Verbraucherkammer 28 weiter über die Axialbohrung 57, die Radialbohrung 62, über die Ringnut 49 des Steuerkolbens 22, über die Ringkammer 46 der Kolbenbohrung 21 und über die Einfräsungen 50 fluidisch mit der Ablaufkammer 32 verbunden. Die Verbindung ist wegen der Düsenwirkung der Radialbohrung 62 eine gedrosselte Verbindung. Über die Verbindung kann somit aus den Verbraucherkammern Druckflüssigkeit in einem kleinen Strom zu der Ablaufkammer 32 und damit zu einem Tank abfließen. Dadurch werden die Verbraucherkammern von Druck entlastet, so daß zum Beispiel Sperr- oder Bremsventile, die zwischen den Verbraucherkammern und einem hydraulischen Verbraucher angeordnet sind, sicher funktionieren. Eine Last, die sich bei nicht vorhandenem Sperrventil auf einer Verbraucherkammer abstützt, bewegt sich nur langsam.Thus, in the embodiment of Figure 1 in the middle position of the Control piston 22, the consumer chamber 28 via the blind bores 60 and Radial bore 58 and the consumer chamber 29 via the blind bores 61 and the radial bore 59 as well as the consumer chamber 28 via the axial bore 57, the radial bore 62, via the annular groove 49 of the control piston 22, over the annular chamber 46 of the piston bore 21 and over the cutouts 50 fluidly connected to the drain chamber 32. The connection is over the nozzle action of the radial bore 62 a throttled connection. about the connection can thus be hydraulic fluid in one from the consumer chambers small current flow to the drain chamber 32 and thus to a tank. This relieves the consumer chambers of pressure, so that for example Check or brake valves between the consumer chambers and one hydraulic consumers are arranged to work safely. A burden that is supported on a consumer chamber if there is no check valve, moves slowly.

Die Entlastung der Verbraucherkammern erfolgt ohne Einbeziehung der Feinsteuernuten 56, so daß diese genauso ausgelegt sein können wie bei einem Wegeventil ohne gedrosselte Entlastung der Mittelstellung. Von dem Steuerkolben eines solchen Wegeventils unterscheidet sich der Steuerkolben 22 des Ausführungsbeispiels der Erfindung nach Figur 1 nur durch die zusätzlichen Sackböhrungen 60 und 61.The consumer chambers are relieved without including the fine tax slots 56, so that they can be designed exactly as with a directional control valve without throttled relief of the middle position. From the spool one Such a directional control valve differs from the control piston 22 of the exemplary embodiment of the invention according to FIG. 1 only through the additional blind bores 60 and 61.

Wird der Steuerkolben 22 aus der Mittelstellung, in der Anschauung nach Figur 1 zum Beispiel nach rechts, herausbewegt, so werden die Sackbohrungen 60 überdeckt und der Durchflußquerschnitt zwischen ihnen und der Verbraucherkammer 28 geschlossen, noch ehe diese Verbraucherkammer über die Feinsteuernuten 56 am Kolbenbund 34 mit der Ablaufkammer 32 verbunden wird. Verschlossen wird ebenfalls die Verbindung zwischen der Ringnut 49 am Steuerkolben 22 und der Ablaufkammer 32. Die Radialbohrung 59 dagegen bleibt zu der Verbraucherkammer 29, die nun über die Feinsteuernuten 55 mit der Zulaufkammer 27 verbunden ist, offen, so daß eine Lastmeldung möglich ist. Bei einer Verschiebung des Steuerkolbens 22 aus der Mittelstellung heraus nach links werden die Sackbohrungen 61 überdeckt und die Radialbohrungen 58 bleiben zur Verbraucherkammer 28 offen.If the control piston 22 moves out of the middle position, in the view according to FIG. 1 For example, moved to the right, the blind holes 60 are covered and the flow area between them and the consumer chamber 28 closed before this consumer chamber via the fine control grooves 56 is connected to the drain chamber 32 on the piston collar 34. Is locked also the connection between the annular groove 49 on the control piston 22 and the Drain chamber 32. The radial bore 59, however, remains to the consumer chamber 29, which is now connected to the inlet chamber 27 via the fine control grooves 55 is open so that a load message is possible. When the control piston moves 22 from the middle position to the left are the blind holes 61 covers and the radial bores 58 remain open to the consumer chamber 28.

Bei dem Ausführungsbeispiel nach Figur 2 reichen die Radialbohrungen 58 und 59 bis auf die Außenseite der Kolbenbunde 34 und 35 und sind in der Mittelstellung des Steuerkolbens 22 von der Kolbenbohrung 21 überdeckt. Für die gedrosselte Entlastung der Verbraucherkammern 28 und 29 in der Mittelstellung weist jeder Kolbenbund 34 und 35 zwei einander gegenüberliegende, axial verlaufende, schmale Nuten 70 bzw. 71 auf, über die in der Mittelstellung des Steuerkolbens 22 entlang der Gehäusestege 38 eine unmittelbare gedrosselte Verbindung zwischen den Verbraucherkammern und den Ablaufkammem besteht. In der Mittelstellung des Steuerkolbens reichen die Nuten 70 und 71 nur soweit in die Verbraucherkammern und die Ablaufkammern hinein, daß die fluidische Verbindung über sie bei einer Verschiebung des Steuerkolbens 22 aus der Mittelstellung unterbrochen wird, noch ehe sich Feinsteuernuten 55 und 56 zu den Verbraucherkammern öffnen. Auch bei dem Ausführungsbeispiel nach Figur 2 erfolgt also die gedrosselte Entlastung der Verbraucherkammern ohne Einbeziehung der Feinsteuernuten 56.In the exemplary embodiment according to FIG. 2, the radial bores 58 and 59 are sufficient except for the outside of the piston collars 34 and 35 and are in the middle position of the control piston 22 covered by the piston bore 21. For the throttled Everyone has discharge of the consumer chambers 28 and 29 in the middle position Piston collar 34 and 35 two opposite, axially extending, Narrow grooves 70 and 71 on the 22 in the central position of the control piston along the housing webs 38 an immediate throttled connection between the consumer chambers and the drainage chambers. In the middle position of the control piston, the grooves 70 and 71 only extend as far into the consumer chambers and the drain chambers into that fluid communication through them interrupted when the control piston 22 moves from the central position before fine control grooves 55 and 56 open to the consumer chambers. In the exemplary embodiment according to FIG. 2, the throttled also takes place Relief for the consumer chambers without the inclusion of fine tax slots 56.

Claims (5)

  1. A directional control valve for the control, in particular the load-independent control, of a hydraulic consumer in terms of direction and speed, comprising a control spool (22) which can be displaced axially in opposite directions from a central position in a spool bore (21) of a valve housing (20) with which the pressure medium paths can be controlled between a feed chamber (27), to which pressure medium can be fed from a pressure medium source, a discharge chamber (32, 33), via which pressure medium can be led away to a tank, and two consumer chambers (28, 29), which has first fine control grooves (55) for opening under control a connection between a consumer chamber (28, 29) and the feed chamber (27), and second fine control grooves (56) for opening under control a connection between a consumer chamber (28, 29) and the discharge chamber (32, 33), and via which, in the central position, there is a restricted relief connection from a consumer chamber (28, 29) to the discharge chamber (32, 33),
    characterized by the fact that the relief connection exists via a recess (60, 61, 70, 71) in the control spool (22), independently of the second fine control grooves (56), and that, in the event of displacement of the control spool (22) with the effect of connecting the consumer chamber (28, 29) to the discharge chamber (32, 33), the relief connection is interrupted before the second fine control grooves (56) open a flow cross section.
  2. A directional control valve according to claim 1, characterized by the fact that, in the central position of the control spool (22), the recess (70, 71) is directly open both to a consumer chamber (28, 29) and to a discharge chamber (32, 33) and, in the event of displacement of the control spool (22) from the central position, is shut off with respect to one of the chambers (28, 29, 32, 33).
  3. A directional control valve according to claim 1 or 2, characterized by the fact that, in the event of displacement of the control spool (22) with the effect of connecting a consumer chamber (28, 29) to the feed chamber (27), the recess (60, 61) remains open to the consumer chamber (28, 29), and that the recess (60, 61) lies in a fluid path serving to feed back a load pressure.
  4. A directional control valve according to claim 3, characterized by the fact that the fluid path has a radial bore (58, 59) to tap off the load pressure prevailing in a consumer chamber (28, 29), and that the recess (60, 61) is formed by an enlargement of only the opening region of the radial bore (58, 59).
  5. A directional control valve according to claim 3 or 4, characterized by the fact that, in the region of a consumer chamber (28), the control spool (22) has a first spool collar (34) with first fine control grooves (55) and second fine control grooves (56), a first annular groove (41) adjoining the first spool collar (34) in the region of a discharge chamber (32), a further spool collar (48) adjacent to said annular groove (41) and a further annular groove (49) adjacent thereto, that the recess (60) belongs to a first radial duct (58) of the first spool collar (34), that the control spool (22) has an axial bore (57) which is met by the first radial duct (58) and, at an axial distance from the first radial duct (58), is met by a second radial duct (62), which on the outside opens into the further annular groove (49), that, isolated from the discharge chamber (32) by a housing land (47), around the spool bore (21) there runs an annular chamber (46) whose width is greater than the effective width of the further spool collar (48), and that the further spool collar (48) and the annular chamber (46) are located in relation to each other in such a way that, in the central position of the control spool (22), the further annular groove (49) is open to the discharge chamber (32) via the annular chamber (46) but, following a short travel of the control spool (22) from the central position, is isolated from the discharge chamber (32) by the further spool collar (48).
EP02702315A 2001-02-17 2002-01-25 Distributing valve for the load-independent control of a hydraulic consumer in terms of direction and speed Expired - Lifetime EP1360419B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10107532A DE10107532A1 (en) 2001-02-17 2001-02-17 Directional control valve for load-independent control of a hydraulic consumer with regard to direction and speed
DE10107532 2001-02-17
PCT/EP2002/000792 WO2002066842A1 (en) 2001-02-17 2002-01-25 Distributing valve for the load-independent control of a hydraulic consumer in terms of direction and speed

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EP1360419A1 EP1360419A1 (en) 2003-11-12
EP1360419B1 true EP1360419B1 (en) 2004-11-03

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US (1) US6994116B2 (en)
EP (1) EP1360419B1 (en)
AT (1) ATE281602T1 (en)
DE (2) DE10107532A1 (en)
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WO (1) WO2002066842A1 (en)

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DE102005060069B4 (en) * 2004-12-17 2015-05-28 Hyundai Motor Company Manual valve of an automatic transmission
DE102005050169A1 (en) 2005-06-21 2006-12-28 Bosch Rexroth Ag LS control arrangement and LS directional control valve
DE102006040234A1 (en) * 2006-08-28 2008-03-06 Robert Bosch Gmbh LS control arrangement
DE102008008092A1 (en) * 2007-11-28 2009-06-04 Robert Bosch Gmbh valve assembly
US9689285B2 (en) * 2008-07-17 2017-06-27 Mitsubishi Electric Corporation Solenoid valve for variable valve timing control devices, and variable valve timing control system
DE102010053805A1 (en) 2010-12-08 2012-06-14 Robert Bosch Gmbh Directional control valve for controlling hydraulic load, has channel portion which is formed from axial hole to outer surface of control piston, by radial hole that is formed with constant diameter of axial hole to piston outer surface
DE102011084932A1 (en) * 2011-10-21 2013-04-25 Zf Friedrichshafen Ag Valve device with a valve housing having a plurality of switching tongues
DE112017008032T5 (en) * 2017-09-13 2020-07-02 Shimadzu Corporation CONTROL VALVE

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US3212522A (en) 1963-10-11 1965-10-19 Commercial Shearing Series type valves with float position
DE2514624C3 (en) 1975-04-03 1986-10-23 Danfoss A/S, Nordborg Control device for at least one hydraulically operated double-acting consumer
US4355660A (en) 1980-04-15 1982-10-26 General Signal Corporation Pneumatically controlled, four position hydraulic valve
DE3841507C1 (en) * 1988-01-22 1989-06-29 Danfoss A/S, Nordborg, Dk
DE3802672C2 (en) * 1988-01-29 1993-12-16 Danfoss As Hydraulic control valve with pressure sensing device
SE501289C2 (en) * 1993-06-24 1995-01-09 Voac Hydraulics Boraas Ab Controls for a hydraulic motor
DE4413216C2 (en) * 1994-04-15 2003-02-06 Bosch Gmbh Robert Hydraulic directional valve
IT1281708B1 (en) 1996-01-24 1998-02-26 Brevini Hydraulics Spa DEVICE FOR ACTIVATING A HYDRAULIC USE WITH AN ACTUATING SPEED INDEPENDENT OF THE RESISTANT LOAD BEARING ON IT
DE19800720C2 (en) * 1998-01-12 2001-10-31 Sauer Danfoss Nordborg As Nord Control valve for a hydraulic motor
DE19948232A1 (en) * 1999-07-10 2001-01-11 Mannesmann Rexroth Ag Directional valve disc, especially for a mobile working device
DE19957952A1 (en) * 1999-12-02 2001-06-07 Mannesmann Rexroth Ag Hydraulic directional control valve for load-independent control of a hydraulic consumer, especially of a mobile machine

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DE50201462D1 (en) 2004-12-09
WO2002066842A1 (en) 2002-08-29
DE10107532A1 (en) 2002-08-29
US20040069359A1 (en) 2004-04-15
US6994116B2 (en) 2006-02-07
ATE281602T1 (en) 2004-11-15
EP1360419A1 (en) 2003-11-12
DK1360419T3 (en) 2005-03-14

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