EP2513491B1 - Valve arrangement for actuating a load - Google Patents

Valve arrangement for actuating a load Download PDF

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Publication number
EP2513491B1
EP2513491B1 EP10784445.8A EP10784445A EP2513491B1 EP 2513491 B1 EP2513491 B1 EP 2513491B1 EP 10784445 A EP10784445 A EP 10784445A EP 2513491 B1 EP2513491 B1 EP 2513491B1
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EP
European Patent Office
Prior art keywords
valve
consumer
pressure
brake
valve arrangement
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EP10784445.8A
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German (de)
French (fr)
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EP2513491A1 (en
Inventor
Winfried Rueb
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Hydac Filtertechnik GmbH
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Hydac Filtertechnik GmbH
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Publication of EP2513491A1 publication Critical patent/EP2513491A1/en
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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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • 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
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control

Definitions

  • the invention relates to a hydraulic valve arrangement for controlling a consumer with an acting as inlet throttle, continuously adjustable directional control valve, via which a pump connection with consumer connections is connected, the consumer is connected via working lines to the directional control valve and a drain volume flow of a pressure medium from the consumer via a throttle device is adjustable in response to a load signal of the consumer, wherein the throttle device is adjustable by a derived from the load signal back pressure.
  • Valve arrangements are used in the mobile hydraulics of working machines, for example, for the control of single or double-acting consumers or of rotating mechanisms, such as hydraulic motors and power lifts.
  • a throttle device in each case leading to the respective consumer working lines a throttle device is knotted, via which the incoming or outgoing hydraulic oil flow rate can be throttled.
  • valve throttle For throttling the pressure medium inlet and the pressure medium outlet a valve throttle are arranged in the working lines, the valve members are mechanically coupled.
  • the ratio of the inlet and outlet openings of the valve throttles is determined by the mechanical coupling of the opening edges of the common valve spool, so that a certain setting of the respective valve throttle a certain pressure loss in the drain line corresponds.
  • This pressure loss is particularly undesirable when connecting single-acting consumers, as it does not represent a useful function.
  • the pressure loss leads to energy losses, to an increase in the pressure medium temperature and possibly to premature wear of the valve throttle.
  • Lowering brake valves prevent not only an uncontrolled slump but also a lack of filling on the inlet side and thus cavitation.
  • the lowering brake valve In a working phase or lifting phase of a working cylinder, the lowering brake valve is bypassed by a check valve.
  • the flow through the check valve causes high pressure losses.
  • a valve assembly of the type described above is made DE 10 2007 020 558 A1 known.
  • the known valve arrangement serves to supply pressure medium to a hydraulic consumer with a directional control valve, which has a pressure measuring medium volume flow predetermining inflow orifice and a directional part.
  • the directional valve is associated with an individual pressure compensator.
  • a lowering brake valve is provided, which is acted upon in the opening direction by a pilot pressure and the opening towards the consumer
  • Check valve is connected in parallel, wherein the pilot pressure is tapped in a channel between the pressure compensator and the directional part.
  • the channel is a bow channel between a pressure compensator outlet and in each case an intermediate chamber of a flow-side or return-side directional part of the directional control valve.
  • both in the flow and in the course of a lowering brake valve can be provided and both acted upon by the same pilot pressure.
  • the known valve arrangement is preferably a directional control valve element of a mobile control block.
  • the invention has for its object to provide a valve assembly for controlling a consumer whose drive signal of a brake valve is decoupled from cylinder pressures or pressures at another consumer, with a high reliability and an improved switching behavior should be guaranteed.
  • a hydraulic valve assembly having the features of claim 1 in its entirety.
  • the throttle device is controlled via a hydraulic circuit, which detects the size and direction of a pressure medium flow to the consumer.
  • a device which detects the size and the direction of the pressure medium flow in the valve arrangement to the consumer. This makes it possible that the dynamic pressure signal for the brake slide, a signal of this device is superimposed for measuring the size and direction of the pressure medium flow.
  • the pertinent device detects, for example, the switching position of the spool of the directional control valve. If the spool is switched back from a switching position corresponding to a working position of the consumer in a neutral position, the brake slide is in a switching position passed through this device, which corresponds to a closed position.
  • the device or the hydraulic circuit which detects the size and direction of the pressure medium flow to the consumer, acts by means of a pressure divider circuit in the process of the brake slide in a closed position such that a derived from the control pressure for the valve assembly, the reduced pressure controls the brake slide.
  • the dynamic pressure signal for the brake slide is superimposed on a displacement of the spool in a switching position corresponding to the open position in terms of a working position of the consumer, by a signal of said device, in the sense that a disproportionately rapid opening position of the Brake slider is taken.
  • the throttle device is set by a derived from a load signal or load-sensing signal back pressure, a constructive measure is taken to prevent Mitkoppelung of pressure increases in the consumer in the drive pressure or the drive signal for the brake valve.
  • the dynamic pressure derived from a load-sensing signal is taken from a metering orifice of the directional spool or control piston of a directional control valve.
  • a pressure compensator of such a directional control valve is able to generate the dynamic pressure correlated with the load signal.
  • the throttle device can be designed as a metering diaphragm, in particular as a variable diaphragm. To a particularly compact To achieve construction of the valve assembly, it may be appropriate to integrate a brake valve of a Senkbremsventils in an existing spool of the directional control valve.
  • a dynamic pressure signal basically represents a physical quantity which is available only outside short-term pressure fluctuations or pressure increases in a hydraulic system; unlike the pressures themselves. It is a filtered signal per se.
  • a standard directional control valve can be inexpensively extended to a directional control valve with load braking function.
  • short control channels are possible and logical switch positions of the spool can be used to control the brake slide.
  • throttle notches of the brake valve only allow a pressure fluid drain when the directional control valve spool is moved from a neutral position.
  • the throttle notches in the interior of the brake valve spool are in fluid-carrying connection with openings of the spool in its inner through hole. The brake slide or brake valve spool can thus be acted upon by dynamic pressure on its two end faces.
  • the valve arrangement according to the invention reduces the pressure loss during operation of a hydraulic consumer in both flow directions of a pressure medium to the consumer. If the consumer presents itself as a single-acting hydraulic cylinder, the pressure loss during lifting is reduced by the fact that no check valve must be overflowed. In addition, the pressure loss decreases when lowering the hydraulic cylinder, since only the pressure in an inlet chamber of the hydraulic cylinder must be considered and a spring force of a return spring for the brake valve can be reduced to about 1/5 of the value according to the prior art.
  • a valve assembly 1 for controlling a hydraulic load 2 is shown in a schematic circuit diagram.
  • the consumer 2 is designed as a double-acting hydraulic cylinder, to whose operation a pressure medium flow is provided by a constant current pump 19.
  • the constant-current pump 19 is driven by an internal combustion engine, not shown, of a working machine, such as a mini-excavator or wheel loader.
  • the hydraulic cylinder is used, for example, for raising and lowering a front working tool or an excavator arm or bucket or the like. It is understood that other fields of application of the valve arrangement 1 are possible, for example in an industrial truck or in known hydraulic hoists.
  • the consumer 2 is a continuously adjustable directional control valve 3, of which in the Fig.1 to 3 only exemplary embodiments are shown, driven.
  • the directional control valve 3 is shown in FIG Fig.1 as 4/3-way valve with two working lines 4.5 connected to the consumer 2 fluid leading. Taking the load-sensing line into consideration, it is a 5/3-way valve.
  • a brake valve 10 is knotted in the working line 5, which opens into a piston-side working space of the hydraulic cylinder.
  • the brake valve 10 is mounted directly on the hydraulic cylinder to represent a pipe rupture function can.
  • a check valve 21 secures the valve assembly 1 in case of any pipe break before loss of pressure medium.
  • the brake valve 10 thus represents one, the drain volume flow 6 of a pressure medium 7 in the consumer 2 very stable controlling throttle device 8.
  • FIG.2 is a schematic longitudinal section of a valve assembly 1 from a directional control valve 3 with an integrated therein according to the invention with a controlled dynamic pressure p 'controlled brake slide 11 shown in the brake valve 10.
  • the valve assembly 1 has a pump or pressure supply port P, a return port R, two load ports A, B and two control ports P ' A and P' B and a load signal or load sensing port LS.
  • the basic function of such a valve arrangement 1 is described in several prior applications by the applicant (for example in US Pat DE 10 2007 054 137.8 A1 ), so that will not be discussed in detail on this issue.
  • the valve assembly 1 has one in its housing in the direction of the Fig.2 seen horizontally displaceable spool 12, which is shown in its neutral position.
  • the spool 12 in turn serves as a housing for the therein also displaceable in the horizontal direction brake slide 11.
  • the spool 12 has in addition to metering 9 ( Figure 4 ) between the control terminals P ' A and P' B and the respective load ports A and B two openings 22 in an inner, longitudinal through hole 23. These openings 22 are in constant communication with throttle notches 24 of the inner brake slide 11.
  • the throttle notches 24 can only then release the drain or fluid carrying connection 13 to the return port R when the spool 12 is moved from the neutral position shown to a working position.
  • an opening 15,15 ' are each provided at the ends 16 of the spool 12, at which end faces 18 of the brake slide 11 with the back pressure p' can be connected.
  • the Figure 3 shows in a schematic circuit diagram of a valve assembly 1 according to the invention, the additional application of a hydraulic circuit 17, which superimposed the back pressure signal for the brake slide 11, a signal which maps the size and direction of a pressure medium flow for the consumer 2.
  • a hydraulic circuit 17 which superimposed the back pressure signal for the brake slide 11, a signal which maps the size and direction of a pressure medium flow for the consumer 2.
  • each of the two control lines 25,26 for the spool 1 such, also known as brake detector with pressure divider circuit to be designated hydraulic circuit 17 is knotted.
  • the hydraulic circuit 17 is the deflection of a non-biased by means of spring elements piston 27, the control pressure for the spool 12 to the brake slide 11 on.
  • Figure 4 shown in detail pressure divider circuit that a comparatively reduced pressure the brake slide 11 i drives.
  • the throttle device 8 or the brake valve 10 are closed disproportionately. This contributes to the dynamics of, for example, the in Figure 3 as a hydraulic motor 28 illustrated consumer 2 and results in a rapid deceleration of the hydraulic motor 28.
  • the circuit according to the Figure 3 further discloses a pressure compensator 29 upstream of the constant displacement pump 19, which can serve for Druckstoffmengenabschneidung to avoid overloading of the hydraulic motor 28.
  • the Figure 4 shows an embodiment of a hydraulic circuit 17 for detecting the size and direction of the pressure medium flow for each consumer, which may be performed twice, approximately at each end face of the spool 12 in the directional control valve housing.
  • the hydraulic circuit 17 is shown in a longitudinal section in a longitudinal center plane of the directional control valve 3, so that not all fluid-carrying connections according to the circuit diagram 3 are shown.
  • the Figure 5 There are linear dependencies in both operating states in the working position (a) and the braking position (b) of the spool 12.
  • In the working position (a) of the control spool 12 is a direct given proportional ratio of said pressures, while in the braking position or throttle position of the Brake valve 11 is a disproportionate connection of the pressures.
  • the Figure 6 further illustrates the change in the driving pressure for the brake slide 11 when braking (a) a load and when accelerating (b) a load or a consumer. 2

Description

Die Erfindung betrifft eine hydraulische Ventilanordnung zur Ansteuerung eines Verbrauchers mit einem als Zulaufdrossel wirkenden, stetig verstellbaren Wegeventil, über das ein Pumpenanschluß mit Verbraucheranschlüssen verbindbar ist, wobei der Verbraucher über Arbeitsleitungen an das Wegeventil angeschlossen ist und ein Ablaufvolumenstrom eines Druckmittels von dem Verbraucher über eine Drosseleinrichtung in Abhängigkeit eines Lastsignals des Verbrauchers einstellbar ist, wobei die Drosseleinrichtung von einen vom dem Lastsignal abgeleiteten Staudruck einstellbar ist.The invention relates to a hydraulic valve arrangement for controlling a consumer with an acting as inlet throttle, continuously adjustable directional control valve, via which a pump connection with consumer connections is connected, the consumer is connected via working lines to the directional control valve and a drain volume flow of a pressure medium from the consumer via a throttle device is adjustable in response to a load signal of the consumer, wherein the throttle device is adjustable by a derived from the load signal back pressure.

Ventilanordnungen werden in der Mobilhydraulik von Arbeitsmaschinen beispielsweise zur Ansteuerung von einfach oder doppelt wirkenden Verbrauchern oder von Drehwerken, wie beispielsweise von Hydromotoren und Krafthebern, verwendet. Dabei ist in zu dem jeweiligen Verbraucher führenden Arbeitsleitungen jeweils eine Drosseleinrichtung eingeknüpft, über die der zu- oder ablaufende Hydraulikölvolumenstrom drosselbar ist.Valve arrangements are used in the mobile hydraulics of working machines, for example, for the control of single or double-acting consumers or of rotating mechanisms, such as hydraulic motors and power lifts. In this case, in each case leading to the respective consumer working lines a throttle device is knotted, via which the incoming or outgoing hydraulic oil flow rate can be throttled.

Zur Drosselung des Druckmittelzulaufs und des Druckmittelablaufs sind in den Arbeitsleitungen je eine Ventildrossel angeordnet, deren Ventilglieder mechanisch gekoppelt sind. Das Verhältnis der Zulauf- und Ablauföffnung der Ventildrosseln ist durch die mechanische Koppelung der Öffnungskanten des gemeinsamen Ventilschiebers vorgegeben, so dass einer bestimmten Einstellung der jeweiligen Ventildrossel ein bestimmter Druckverlust in der Ablaufleitung entspricht. Dieser Druckverlust ist insbesondere beim Anschluß von einfach wirkenden Verbrauchern unerwünscht, da er keine sinnvolle Funktion darstellt. Der Druckverlust führt zu Energieverlusten, zu einem Anstieg der Druckmitteltemperatur und gegebenenfalls zu einem vorzeitigen Verschleiß der Ventildrossel.For throttling the pressure medium inlet and the pressure medium outlet a valve throttle are arranged in the working lines, the valve members are mechanically coupled. The ratio of the inlet and outlet openings of the valve throttles is determined by the mechanical coupling of the opening edges of the common valve spool, so that a certain setting of the respective valve throttle a certain pressure loss in the drain line corresponds. This pressure loss is particularly undesirable when connecting single-acting consumers, as it does not represent a useful function. The pressure loss leads to energy losses, to an increase in the pressure medium temperature and possibly to premature wear of the valve throttle.

Es ist des weiteren bekannt, für hydraulische Verbraucher mit ziehender Lastrichtung diese jeweils mit einem Senkbremsventil in der zugeordneten Arbeitsleitung zu versehen oder in zumindest der, den Kolbenraum mit Druckmittel versorgenden Arbeitsleitung das Senkbremsventil einzusetzen. Werden solche Senkbremsventile direkt an einen Arbeitszylinder angebaut, so läßt sich damit wirkungsvoll eine Berstsicherung der betreffenden Arbeitsleitung vornehmen. Bei einem Leck der Arbeitsleitung kann dabei ein Rückschlag-Sitzventil die Arbeitsleitung abdichten. Der Arbeitszylinder bleibt dann stehen. Solche Senkbremsventile werden von einem Druckmitteldruck in der korrespondierenden Arbeitsleitung geöffnet und von einem Stellglied, wie etwa einer Druckfeder, wieder geschlossen.It is also known for hydraulic consumers with pulling load direction to provide each of these with a lowering brake valve in the associated working line or to use in at least the, the piston chamber with pressure fluid supplying working line the lowering brake valve. If such Senkbremsventile grown directly on a working cylinder, so can effectively make a rupture of the relevant working line. In the event of a leak in the working line, a non-return seat valve can seal the working line. The working cylinder then stops. Such lowering brake valves are opened by a fluid pressure in the corresponding working line and closed by an actuator, such as a compression spring.

Senkbremsventile verhindern neben einem unkontrollierten Absacken einen Füllungsmangel auf der Zulaufseite und somit Kavitation. In einer Arbeitsphase oder Hebephase eines Arbeitszylinders wird das Senkbremsventil durch ein Rückschlagventil umgangen. Die Durchströmung des Rückschlagventils bedingt allerdings hohe Druckverluste. Zudem ergeben sich Instabilitäten im Betrieb. Um solche Erscheinungen auszuschließen, ist das Druckmittel oft mit sehr hohen Drücken, z.B. 70 bar, vorzuspannen. Dies bedingt beispielsweise bei einem Hydrozylinder, der zum Heben von Lasten eingesetzt ist, dass selbst bei einem Senkvorgang die Last gedrückt werden muß, obwohl diese ohne Vorspannung des Druckmittels von allein sinken würde.Lowering brake valves prevent not only an uncontrolled slump but also a lack of filling on the inlet side and thus cavitation. In a working phase or lifting phase of a working cylinder, the lowering brake valve is bypassed by a check valve. The flow through the check valve, however, causes high pressure losses. In addition, there are instabilities in the operation. To exclude such phenomena, the pressure medium is often with very high pressures, eg 70 bar, bias. This requires, for example, in a hydraulic cylinder, which is used for lifting loads, that even with a lowering process, the load must be pressed, although this would fall by itself without bias of the pressure medium.

Eine Möglichkeit, solche Systeme zu stabilisieren, ist die Anwendung von Rohrbruchsicherungsventilen, die mit einem proportionalen Steuerventilverhalten ausgelegt sind und beispielsweise mit einem Ansteuerdruck eines Wegeventils angesteuert werden. Deren Öffnungssignal ist nicht mit der jeweiligen Last oder einem Lastdruck gekoppelt, so dass keinerlei Instabilitäten auftreten können. Jedoch ist von Nachteil, dass es einer zusätzlichen Ansteuerleitung zu einem unter Umständen entferntdiegenden Arbeitszylinder bedarf. Die Kosten für ein dahingehendes Steuersystem sind daher insbesondere für kleine Arbeitsmaschinen nicht akzeptabel. Einfache Arbeitsmaschinen, wie Minibagger od. dgl., haben mechanisch betätigte Wegeventile, bei denen kein Ansteuerdruck für Rohrbruchsicherungsventile abgreifbar ist. Deshalb ist das klassische Senkbremsventil die Standardlösung beim Bremsen von Lasten in Zusammenarbeit mit mechanisch betätigten Steuerschiebern.One way to stabilize such systems, the use of pipe rupture valve, which are designed with a proportional control valve behavior and are driven, for example, with a drive pressure of a directional control valve. Their opening signal is not coupled to the respective load or a load pressure, so that no instabilities can occur. However, it is disadvantageous that an additional drive line is required for a cylinder which may be removed in some circumstances. The cost of a pertinent tax system is therefore not acceptable, especially for small machines. Simple working machines, such as mini excavators od. Like., Have mechanically operated directional control valves, in which no control pressure for pipe rupture valves can be tapped. This is why the classic counterbalance valve is the standard solution for braking loads in cooperation with mechanically operated spool valves.

In Abhängigkeit von dem jeweiligen Einsatzzweck einer betreffenden Ventilanordnung ist es wünschenswert, insbesondere bei kleinen Arbeitsmaschinen aus Kostengründen die Senkbremsfunktion in das Wegeventil zu integrieren. Die DE 10 2005 013 823 A1 beschreibt eine derartige Ventilanordnung. Allerdings ist die Funktionalität und Sicherheit dieser Ventilanordnung abhängig von elektronischen Sensoren sowie einer elektronischen Steuer- und Regeleinrichtung.Depending on the particular application of a particular valve arrangement, it is desirable to integrate the Senkbremsfunktion in the directional control valve, especially for small machines for cost reasons. The DE 10 2005 013 823 A1 describes such a valve arrangement. However, the functionality and safety of this valve assembly is dependent on electronic sensors and an electronic control and regulating device.

Eine Ventilanordnung der eingangs beschriebenen Art ist aus DE 10 2007 020 558 A1 bekannt geworden. Die bekannte Ventilanordnung dient zur Druckmittelversorgung eines hydraulischen Verbrauchers mit einem Wegeventil, das eine den Druckmittelvolumenstrom vorgebende Zulaufmessblende und ein Richtungsteil aufweist. Dem Wegeventil ist eine Individual-Druckwaage zugeordnet. In einem Rücklauf vom Verbraucher ist ein Senkbremsventil vorgesehen, das in Öffnungsrichtung von einem Pilotdruck beaufschlagt ist und dem ein in Richtung zum Verbraucher öffnendes Rückschlagventil parallel geschaltet ist, wobei der Pilotdruck in einem Kanal zwischen der Druckwaage und dem Richtungsteil abgegriffen ist. Der Kanal ist ein Bogenkanal zwischen einem Druckwaagenausgang und jeweils einer Zwischenkammer eines vorlauf- bzw. rücklaufseitigen Richtungsteils des Wegeventils. Hierbei kann sowohl im Vorlauf als auch im Ablauf ein Senkbremsventil vorgesehen und beide vom gleichen Pilotdruck beaufschlagt sein. Die bekannte Ventilanordnung ist vorzugsweise ein Wegeventilelement eines Mobilsteuerblocks.A valve assembly of the type described above is made DE 10 2007 020 558 A1 known. The known valve arrangement serves to supply pressure medium to a hydraulic consumer with a directional control valve, which has a pressure measuring medium volume flow predetermining inflow orifice and a directional part. The directional valve is associated with an individual pressure compensator. In a return from the consumer, a lowering brake valve is provided, which is acted upon in the opening direction by a pilot pressure and the opening towards the consumer Check valve is connected in parallel, wherein the pilot pressure is tapped in a channel between the pressure compensator and the directional part. The channel is a bow channel between a pressure compensator outlet and in each case an intermediate chamber of a flow-side or return-side directional part of the directional control valve. Here, both in the flow and in the course of a lowering brake valve can be provided and both acted upon by the same pilot pressure. The known valve arrangement is preferably a directional control valve element of a mobile control block.

Der Erfindung liegt die Aufgabe zugrunde, eine Ventilanordnung zur Ansteuerung eines Verbrauchers anzugeben, deren Ansteuersignal eines Bremsventils von Zylinderdrücken oder Drücken an einem sonstigen Verbraucher entkoppelt ist, wobei eine hohe Betriebssicherheit und ein verbessertes Schaltverhalten gewährleistet sein sollen.The invention has for its object to provide a valve assembly for controlling a consumer whose drive signal of a brake valve is decoupled from cylinder pressures or pressures at another consumer, with a high reliability and an improved switching behavior should be guaranteed.

Eine dahingehende Aufgabe löst eine hydraulische Ventilanordnung mit den Merkmalen des Patentanspruches 1 in seiner Gesamtheit. Gemäß dem kennzeichnenden Teil von Patentanspruch 1 ist die Drosseleinrichtung über eine hydraulische Schaltung, welche Größe und Richtung eines Druckmittelstroms zu dem Verbraucher detektiert, angesteuert.This object is achieved by a hydraulic valve assembly having the features of claim 1 in its entirety. According to the characterizing part of claim 1, the throttle device is controlled via a hydraulic circuit, which detects the size and direction of a pressure medium flow to the consumer.

Erfindungsgemäß ist eine Einrichtung vorgesehen, die die Größe und die Richtung des Druckmittelstromes in der Ventilanordnung zu dem Verbraucher detektiert. Dadurch ist es ermöglicht, dass dem Staudrucksignal für den Bremsschieber ein Signal dieser Einrichtung zur Messung der Größe und Richtung des Druckmittelstromes überlagert wird.According to the invention, a device is provided which detects the size and the direction of the pressure medium flow in the valve arrangement to the consumer. This makes it possible that the dynamic pressure signal for the brake slide, a signal of this device is superimposed for measuring the size and direction of the pressure medium flow.

Die dahingehende Einrichtung erkennt beispielsweise die Schaltstellung des Steuerschiebers des Wegeventils..Wird der Steuerschieber aus einer Schaltstellung, die einer Arbeitsstellung des Verbrauchers entspricht, zurückgeschaltet in eine Neutralposition, so wird der Bremsschieber in eine Schaltstellung durch diese Einrichtung gebracht, die einer geschlossenen Position entspricht. Die Einrichtung oder die hydraulische Schaltung, welche Größe und Richtung des Druckmittelstromes zu dem Verbraucher erkennt, wirkt mit Hilfe einer Druckteilerschaltung beim Verfahren des Bremsschiebers in eine geschlossene Position derart, dass ein von dem Ansteuerdruck für die Ventilanordnung abgeleiteter, reduzierter Druck den Bremsschieber ansteuert.The pertinent device detects, for example, the switching position of the spool of the directional control valve. If the spool is switched back from a switching position corresponding to a working position of the consumer in a neutral position, the brake slide is in a switching position passed through this device, which corresponds to a closed position. The device or the hydraulic circuit, which detects the size and direction of the pressure medium flow to the consumer, acts by means of a pressure divider circuit in the process of the brake slide in a closed position such that a derived from the control pressure for the valve assembly, the reduced pressure controls the brake slide.

In umgekehrter Weise wird das Staudrucksignal für den Bremsschieber bei einem Verbringen des Steuerschiebers in eine Schaltstellung, die der geöffneten Position im Sinne einer Arbeitsstellung des Verbrauchers entspricht, von einem Signal der genannten Einrichtung überlagert, in dem Sinne, dass eine überproportional rasche Öffnen-Position des Bremsschiebers eingenommen wird.In the reverse manner, the dynamic pressure signal for the brake slide is superimposed on a displacement of the spool in a switching position corresponding to the open position in terms of a working position of the consumer, by a signal of said device, in the sense that a disproportionately rapid opening position of the Brake slider is taken.

Weiter ist es vorteilhaft, dass in jeder der beiden Steuerleitungen für den Steuerschieber eine derartige, auch als Bremsdetektor mit Druckteilerschaltung zu bezeichnende hydraulische Schaltung eingeknüpft ist. Weitere vorteilhafte Ausgestaltungen der erfindungsgemäßen Ventilanordnung sind Gegenstände der weiteren abhängigen Patentansprüche.Furthermore, it is advantageous that in each of the two control lines for the control slide such, also as a brake detector with pressure divider circuit to be designated hydraulic circuit is knotted. Further advantageous embodiments of the valve arrangement according to the invention are objects of the other dependent claims.

Dadurch, dass die Drosseleinrichtung von einem von einem Lastsignal oder Load-Sensing-Signal abgeleiteten Staudruck eingestellt wird, ist eine konstruktive Maßnahme getroffen, eine Mitkoppelung von Druckanstiegen in dem Verbraucher in dem Ansteuerdruck oder dem Ansteuersignal für das Bremsventil zu verhindern. Bevorzugt wird der von einem Load-Sensing-Signal abgeleitete Staudruck von einer Zumeßblende des Wegeschiebers oder Steuerkolbens eines Wegeventils abgenommen. Eine Druckwaage eines solchen Wegeventils ist in der Lage, den Staudruck korreliert mit dem Lastsignal zu erzeugen. Die Drosseleinrichtung kann als Zumeßblende, insbesondere als variable Blende, ausgebildet sein. Um einen besonders kompakten Aufbau der Ventilanordnung zu erreichen, kann es zweckmäßig sein, einen Bremsschieber eines Senkbremsventils in einen vorhandenen Steuerschieber des Wegeventils zu integrieren.Characterized in that the throttle device is set by a derived from a load signal or load-sensing signal back pressure, a constructive measure is taken to prevent Mitkoppelung of pressure increases in the consumer in the drive pressure or the drive signal for the brake valve. Preferably, the dynamic pressure derived from a load-sensing signal is taken from a metering orifice of the directional spool or control piston of a directional control valve. A pressure compensator of such a directional control valve is able to generate the dynamic pressure correlated with the load signal. The throttle device can be designed as a metering diaphragm, in particular as a variable diaphragm. To a particularly compact To achieve construction of the valve assembly, it may be appropriate to integrate a brake valve of a Senkbremsventils in an existing spool of the directional control valve.

Ein Staudrucksignal stellt grundsätzlich eine physikalische Größe dar, die nur außerhalb kurzzeitiger Druckschwankungen oder Druckanstiegen in einem hydraulischen System zur Verfügung steht; anders als dies bei den Drücken selbst der Fall ist. Es handelt sich per se um ein gefiltertes Signal. Somit kann ein Standard-Wegeventil kostengünstig zu einem Wegeventil mit Lastbremsfunktion erweitert werden. Dadurch sind kurze Steuerkanäle möglich und logische Schaltstellungen des Steuerschiebers können zur Ansteuerung des Bremsschiebers genutzt werden. So kann dadurch auf einfache Weise vorgegeben werden, dass Drosselkerben des Bremsventils nur dann einen Druckmittelabfluß ermöglichen, wenn der Wegeventil-Steuerschieber aus einer neutralen Position verfahren ist. Die Drosselkerben im Inneren des Bremsventilschiebers stehen mit Durchbrüchen des Steuerschiebers in seiner inneren Durchgangsbohrung in fluidführender Verbindung. Der Bremsschieber oder Bremsventilschieber ist damit mit Staudruck auf seinen beiden Stirnseiten beaufschlagbar.A dynamic pressure signal basically represents a physical quantity which is available only outside short-term pressure fluctuations or pressure increases in a hydraulic system; unlike the pressures themselves. It is a filtered signal per se. Thus, a standard directional control valve can be inexpensively extended to a directional control valve with load braking function. As a result, short control channels are possible and logical switch positions of the spool can be used to control the brake slide. Thus, it can be specified in a simple manner that throttle notches of the brake valve only allow a pressure fluid drain when the directional control valve spool is moved from a neutral position. The throttle notches in the interior of the brake valve spool are in fluid-carrying connection with openings of the spool in its inner through hole. The brake slide or brake valve spool can thus be acted upon by dynamic pressure on its two end faces.

Die erfindungsgemäße Ventilanordnung verringert den Druckverlust beim Betrieb eines hydraulischen Verbrauchers in beide Strömungsrichtungen eines Druckmittels zu dem Verbraucher. Stellt sich der Verbraucher als einfach wirkender Hydraulikzylinder dar, so reduziert sich der Druckverlust beim Heben dadurch, dass kein Rückschlagventil überströmt werden muß. Zudem reduziert sich der Druckverlust beim Senken des Hydraulikzylinders, da lediglich der Druck in einer Zulaufkammer des Hydraulikzylinders berücksichtigt werden muß und eine Federkraft einer Rückstellfeder für den Bremsschieber etwa auf 1/5 des Wertes gemäß dem bisherigen Stand der Technik reduziert werden kann.The valve arrangement according to the invention reduces the pressure loss during operation of a hydraulic consumer in both flow directions of a pressure medium to the consumer. If the consumer presents itself as a single-acting hydraulic cylinder, the pressure loss during lifting is reduced by the fact that no check valve must be overflowed. In addition, the pressure loss decreases when lowering the hydraulic cylinder, since only the pressure in an inlet chamber of the hydraulic cylinder must be considered and a spring force of a return spring for the brake valve can be reduced to about 1/5 of the value according to the prior art.

Im Folgenden wird die erfindungsgemäße hydraulische Ventilanordnung anhand verschiedener Ausführungsbeispiele näher erläutert.In the following, the hydraulic valve arrangement according to the invention will be explained in more detail with reference to various embodiments.

Dabei zeigt die

Fig.1
eine schematische Darstellung eines Ausführungsbeispiels einer Ventilanordnung zur Ansteuerung eines Verbrauchers mit von einem Staudruck eines LS-Wegeventils angesteuertem B remssch ieber;
Fig.2
einen schematischen Längsschnitt durch eine erfindungsgemäße Ventilanordnung mit einem in einem Steuerschieber eines Wegeventils integrierten Bremsschieber;
Fig.3
einen schematischen Schaltplan einer erfindungsgemäßen Ventilanordnung und einer hydraulischen Schaltung, welche Größe und Richtung eines Druckmittelstromes zu einem Verbraucher detektiert;
Fig.4
einen teilweisen schematischen Längsschnitt durch eine Ventilanordnung mit einer hydraulischen Schaltung, welche Größe und Richtung eines Druckmittelstromes zu einem Verbraucher detektiert;
Fig.5
ein Beispiel eines Ansteuerdruckverlaufs an einem Bremsschieber einer erfindungsgemäßen Ventilanordnung, aufgezeichnet über den Ansteuerdruck an einem Steuerschieber eines Wegeventils; und
Fig.6
ein Beispiel betreffend die Auflösegenauigkeit der hydraulischen Schaltung zur Erkennung der Größe und Richtung des Druckmittelstromes zu/von dem Verbraucher mit einer Drukkumkehr bei dem Ansteuerdruck an einem Steuerschieber.
It shows the
Fig.1
a schematic representation of an embodiment of a valve assembly for controlling a consumer with controlled by a dynamic pressure of a LS-way valve B remssch ieber;
Fig.2
a schematic longitudinal section through a valve assembly according to the invention with an integrated in a spool of a directional control valve brake valve;
Figure 3
a schematic circuit diagram of a valve arrangement according to the invention and a hydraulic circuit, which detects the size and direction of a pressure medium flow to a consumer;
Figure 4
a partial schematic longitudinal section through a valve assembly with a hydraulic circuit, which detects the size and direction of a pressure medium flow to a consumer;
Figure 5
an example of a Ansteuerdruckverlaufs on a brake valve of a valve assembly according to the invention, recorded on the control pressure to a spool of a directional control valve; and
Figure 6
an example concerning the resolution accuracy of the hydraulic circuit for detecting the size and direction of the Pressure medium flow to / from the consumer with a Drukkumkehr at the control pressure to a spool.

In der Fig.1 ist in einem schematischen Schaltplan ein Ausführungsbeispiel einer Ventilanordnung 1 zur Ansteuerung eines hydraulischen Verbrauchers 2 gezeigt. Der Verbraucher 2 ist als doppelt wirkender Hydraulikzylinder ausgebildet, zu dessen Betrieb ein Druckmittelstrom von einer Konstantstrompumpe 19 bereitgestellt ist. Die Konstantstrompumpe 19 wird von einer nicht gezeigten Verbrennungskraftmaschine einer Arbeitsmaschine, wie etwa einem Minibagger oder Radlader, angetrieben. Der Hydraulikzylinder dient beispielsweise dem Heben und Senken eines Frontarbeitswerkzeuges oder eines Baggerarmes oder Baggerlöffels od. dgl.. Es versteht sich, dass andere Anwendungsbereiche der Ventilanordnung 1 möglich sind, so etwa in einem Flurförderfahrzeug oder in bekannten hydraulischen Hubwerken.In the Fig.1 is an example of a valve assembly 1 for controlling a hydraulic load 2 is shown in a schematic circuit diagram. The consumer 2 is designed as a double-acting hydraulic cylinder, to whose operation a pressure medium flow is provided by a constant current pump 19. The constant-current pump 19 is driven by an internal combustion engine, not shown, of a working machine, such as a mini-excavator or wheel loader. The hydraulic cylinder is used, for example, for raising and lowering a front working tool or an excavator arm or bucket or the like. It is understood that other fields of application of the valve arrangement 1 are possible, for example in an industrial truck or in known hydraulic hoists.

Der Verbraucher 2 wird über ein stetig verstellbares Wegeventil 3, von dem in den Fig.1 bis 3 lediglich exemplarische Ausführungsbeispiele gezeigt sind, angesteuert. Das Wegeventil 3 ist gemäß der Darstellung in Fig.1 als 4/3-Wegeventil mit zwei Arbeitsleitungen 4,5 mit dem Verbraucher 2 fluidführend verbunden. Wenn man die Load-Sensing-Leitung in die Betrachtung mit einbezieht, handelt es sich um ein 5/3-Wegeventil. In der Arbeitsleitung 5, die in einen kolbenseitigen Arbeitsraum des Hydraulikzylinders mündet, ist ein Bremsventil 10 eingeknüpft. Das Bremsventil 10 ist direkt an den Hydraulikzylinder angebaut, um eine Rohrbruchsicherungsfunktion darstellen zu können. Ein Rückschlagventil 21 sichert die Ventilanordnung 1 bei einem etwaigen Rohrbruch vor Druckmittelverlust. Ein Senkbremsventil 20 ist, anders als beim Stand der Technik aufgezeigt, nicht direkt von einem Druckmitteldruck in der jeweils korrespondierenden Arbeitsleitung 4 (Stangenseite) geöffnet. Vielmehr ist, um die bekannten Instabilitäten solcher Steuerungen nach dem Stand der Technik zu vermeiden, ein Load-Sensing-Ventil 35 in eine zwischen der Konstantstrompumpe 19 und dem Wegeventil 3 angeordneten Druckmittelleitung eingeknüpft. Ein Staudruck p' dieses Load-Sensing-Wegeventils 35 steuert die Funktion und mithin die Schaltstellung eines Bremsschiebers 11 des Bremsventils 10 an.The consumer 2 is a continuously adjustable directional control valve 3, of which in the Fig.1 to 3 only exemplary embodiments are shown, driven. The directional control valve 3 is shown in FIG Fig.1 as 4/3-way valve with two working lines 4.5 connected to the consumer 2 fluid leading. Taking the load-sensing line into consideration, it is a 5/3-way valve. In the working line 5, which opens into a piston-side working space of the hydraulic cylinder, a brake valve 10 is knotted. The brake valve 10 is mounted directly on the hydraulic cylinder to represent a pipe rupture function can. A check valve 21 secures the valve assembly 1 in case of any pipe break before loss of pressure medium. A lowering brake valve 20, unlike the prior art shown, not directly from a pressure medium pressure in the respective corresponding working line 4 (rod side) open. Rather, in order to avoid the known instabilities of such controls according to the prior art, a load-sensing valve 35 is incorporated into a arranged between the constant current pump 19 and the directional control valve 3 pressure medium line. A back pressure p 'of this load-sensing directional valve 35 controls the function and thus the switching position of a brake slide 11 of the brake valve 10.

Auf diese Weise ist eine Instabilität in der Ansteuerung des Bremsventils 10 und damit ein unkontrolliertes Absinken beispielsweise einer Last verhindert. Bei einem Hebevorgang des Hydraulikzylinders oder Verbrauchers 2 hingegen ist das Rückschlagventil 21 zu durchstömen, was mit entsprechenden Druckverlusten einhergeht. Es versteht sich, dass andere VentilAuslegungen mit anderer Steuerlogik gleichfalls eingesetzt werden können, um die erfindungsgemäße Funktion der offenbarten Ventilanordnung 1 darstellen zu können. Das Bremsventil 10 stellt somit eine, den Ablaufvolumenstrom 6 eines Druckmittels 7 in dem Verbraucher 2 sehr stabil steuernde Drosseleinrichtung 8 dar.In this way, instability in the control of the brake valve 10 and thus an uncontrolled drop, for example, a load is prevented. In a lifting operation of the hydraulic cylinder or consumer 2, however, the check valve 21 is to flow through, which is associated with corresponding pressure losses. It will be appreciated that other valve designs with different control logic may also be used to represent the inventive function of the disclosed valve assembly 1. The brake valve 10 thus represents one, the drain volume flow 6 of a pressure medium 7 in the consumer 2 very stable controlling throttle device 8.

In der Fig.2 ist in einem schematischen Längsschnitt eine Ventilanordnung 1 aus einem Wegeventil 3 mit einem darin integrierten erfindungsgemäß mit einem geregelten Staudruck p' angesteuerten Bremsschieber 11 in dem Bremsventil 10 gezeigt. Die Ventilanordnung 1 weist einen Pumpen- oder Druckversorgungsanschluß P auf, einen Rücklaufanschluß R, zwei Verbraucheranschlüsse A,B sowie zwei Steueranschlüsse P'A und P'B und einen Lastsignal- oder Load-Sensing-Anschluß LS auf. Die Grundfunktion einer derartigen Ventilanordnung 1 ist in mehreren Voranmeldungen der Anmelderin (beispielsweise in der DE 10 2007 054 137.8 A1 ) offenbart, so dass im Detail hierauf nicht mehr näher eingegangen wird.In the Fig.2 is a schematic longitudinal section of a valve assembly 1 from a directional control valve 3 with an integrated therein according to the invention with a controlled dynamic pressure p 'controlled brake slide 11 shown in the brake valve 10. The valve assembly 1 has a pump or pressure supply port P, a return port R, two load ports A, B and two control ports P ' A and P' B and a load signal or load sensing port LS. The basic function of such a valve arrangement 1 is described in several prior applications by the applicant (for example in US Pat DE 10 2007 054 137.8 A1 ), so that will not be discussed in detail on this issue.

Die Ventilanordnung 1 weist einen in ihrem Gehäuse in Blickrichtung auf die Fig.2 gesehen horizontal verschiebbaren Steuerschieber 12 auf, der in seiner Neutralposition gezeigt ist. Der Steuerschieber 12 dient wiederum als Gehäuse für den darin ebenfalls in horizontaler Richtung verschiebbaren Bremsschieber 11. Der Steuerschieber 12 hat neben Zumeßblenden 9 (Fig.4) zwischen den Steueranschlüssen P'A und P'B und den jeweiligen Verbraucheranschlüssen A und B zwei Durchbrüche 22 in einer inneren, längsverlaufenden Durchgangsbohrung 23. Diese Durchbrüche 22 stehen in ständiger Verbindung mit Drosselkerben 24 des innen liegenden Bremsschiebers 11. Die Drosselkerben 24 können nur dann den Abfluß oder eine fluidführende Verbindung 13 zu dem Rücklaufanschluß R freigeben, wenn der Steuerschieber 12 aus der gezeigten neutralen Position in eine Arbeitsstellung bewegt wird. Zu diesem Zweck sind je ein Durchbruch 15,15' an den Enden 16 des Steuerschiebers 12 vorgesehen, an denen Stirnseiten 18 des Bremsschiebers 11 mit dem Staudruck p' verbunden werden können.The valve assembly 1 has one in its housing in the direction of the Fig.2 seen horizontally displaceable spool 12, which is shown in its neutral position. The spool 12 in turn serves as a housing for the therein also displaceable in the horizontal direction brake slide 11. The spool 12 has in addition to metering 9 ( Figure 4 ) between the control terminals P ' A and P' B and the respective load ports A and B two openings 22 in an inner, longitudinal through hole 23. These openings 22 are in constant communication with throttle notches 24 of the inner brake slide 11. The throttle notches 24 can only then release the drain or fluid carrying connection 13 to the return port R when the spool 12 is moved from the neutral position shown to a working position. For this purpose, an opening 15,15 'are each provided at the ends 16 of the spool 12, at which end faces 18 of the brake slide 11 with the back pressure p' can be connected.

Die Fig.3 zeigt in einem schematischen Schaltplan einer erfindungsgemäßen Ventilanordnung 1 die zusätzliche Anwendung einer hydraulischen Schaltung 17, welche dem Staudrucksignal für den Bremsschieber 11 ein Signal, welches die Größe und Richtung eines Druckmittelstromes für den Verbraucher 2 abbildet, überlagert. Wie die Fig.3 weiter zeigt, ist in jeder der beiden Steuerleitungen 25,26 für den Steuerschieber 1 eine derartige, auch als Bremsdetektor mit Druckteilerschaltung zu bezeichnende hydraulische Schaltung 17 eingeknüpft. Die hydraulische Schaltung 17 gibt beim Auslenken eines nicht mittels Federelementen vorgespannten Kolbens 27 den Ansteuerdruck für den Steuerschieber 12 an den Bremsschieber 11 weiter. Bei einer Verfahrbewegung des Steuerschiebers 12 in Richtung Neutralposition bewirkt die in Fig.4 im Einzelnen dargestellte Druckteilerschaltung, dass ein vergleichsweise reduzierter Druck den Bremsschieber 11 i ansteuert. Die Drosseleinrichtung 8 oder das Bremsventil 10 werden überproportional geschlossen. Dies trägt zur Dynamik beispielsweise des in Fig.3 als Hydromotor 28 dargestellten Verbrauchers 2 bei und ergibt eine rasche Verzögerung des Hydromotors 28. Die Schaltung nach der Fig.3 offenbart des weiteren eine Druckwaage 29 stromauf der Konstantpumpe 19, die zur Druckmittelmengenabschneidung dienen kann, um Überlastungen des Hydromotors 28 zu vermeiden.The Figure 3 shows in a schematic circuit diagram of a valve assembly 1 according to the invention, the additional application of a hydraulic circuit 17, which superimposed the back pressure signal for the brake slide 11, a signal which maps the size and direction of a pressure medium flow for the consumer 2. As the Figure 3 further shows, in each of the two control lines 25,26 for the spool 1 such, also known as brake detector with pressure divider circuit to be designated hydraulic circuit 17 is knotted. The hydraulic circuit 17 is the deflection of a non-biased by means of spring elements piston 27, the control pressure for the spool 12 to the brake slide 11 on. During a movement of the spool 12 in the direction of neutral position causes the in Figure 4 shown in detail pressure divider circuit that a comparatively reduced pressure the brake slide 11 i drives. The throttle device 8 or the brake valve 10 are closed disproportionately. This contributes to the dynamics of, for example, the in Figure 3 as a hydraulic motor 28 illustrated consumer 2 and results in a rapid deceleration of the hydraulic motor 28. The circuit according to the Figure 3 further discloses a pressure compensator 29 upstream of the constant displacement pump 19, which can serve for Druckmittelmengenabschneidung to avoid overloading of the hydraulic motor 28.

Die Fig.4 zeigt eine Ausführungsform einer hydraulischen Schaltung 17 zur Erkennung der Größe und Richtung des Druckmittelstromes für den jeweiligen Verbraucher, die zweifach, etwa an jeder Stirnseite des Steuerschiebers 12 in dem Wegeventilgehäuse ausgeführt sein kann. Die hydraulische Schaltung 17 ist in einem Längsschnitt in einer Längsmittelebene des Wegeventils 3 gezeigt, so dass nicht alle fluidführenden Verbindungen gemäß dem Schaltplan 3 aufgezeigt sind.The Figure 4 shows an embodiment of a hydraulic circuit 17 for detecting the size and direction of the pressure medium flow for each consumer, which may be performed twice, approximately at each end face of the spool 12 in the directional control valve housing. The hydraulic circuit 17 is shown in a longitudinal section in a longitudinal center plane of the directional control valve 3, so that not all fluid-carrying connections according to the circuit diagram 3 are shown.

Die gezeigten Schaltelemente sind dabei im Wesentlichen:

  • Blende DD1 für den Steuerschieber 12,
  • Blende DD2 zwischen dem Steuerschieber 12 (Druck X') und der Schnappfläche ASch,
  • Verstelldrossel 31 des Bremsdetektorkolbens für die hydraulische Schaltung 17,
  • Bremsdetektorfläche 32 (Federraum des Steuerschiebers 12),
  • Schnappfläche ASch oder 33 an der hydraulischen Schaltung 17, und
  • Geberdruckfläche 34.
The switching elements shown are essentially:
  • Diaphragm D D1 for the control slide 12,
  • Aperture D D2 between the spool 12 (pressure X ') and the snapping surface A Sch ,
  • Variable throttle 31 of the brake detector piston for the hydraulic circuit 17,
  • Brake detector surface 32 (spring space of the spool 12),
  • Snap area A Sch or 33 on the hydraulic circuit 17, and
  • Encoder pressure surface 34.

Die Fig.5 verdeutlicht den Steuerdruck für den Bremsschieber 11, aufgetragen über den Ansteuerdruck des Steuerschiebers 12. Es bestehen lineare Abhängigkeiten bei beiden Betriebszuständen in Arbeitsstellung (a) und Bremsstellung (b) des Steuerschiebers 12. In der Arbeitsstellung (a) des Steuerschiebers 12 ist ein direkt-proportionales Verhältnis der genannten Drücke gegeben, während in der Bremsstellung oder Drosselstellung des Bremsschiebers 11 ein unterproportionaler Zusammenhang der Drücke besteht.The Figure 5 There are linear dependencies in both operating states in the working position (a) and the braking position (b) of the spool 12. In the working position (a) of the control spool 12 is a direct given proportional ratio of said pressures, while in the braking position or throttle position of the Brake valve 11 is a disproportionate connection of the pressures.

Die Fig.6 verdeutlicht des weiteren die Änderung des Ansteuerdruckes für den Bremsschieber 11 beim Bremsen (a) einer Last und beim Beschleunigen (b) einer Last oder eines Verbrauchers 2.The Figure 6 further illustrates the change in the driving pressure for the brake slide 11 when braking (a) a load and when accelerating (b) a load or a consumer. 2

Claims (9)

  1. A valve arrangement for actuating a consumer (2), having an infinitely variable directional control valve (3) acting as the inlet throttle and by means of which a pump port (P) can be connected to consumer ports (A,B), the consumer (2) being connected to the directional control valve (3) by means of working lines (4,5) and a discharge volumetric flow (6) of a pressure medium (7) from the consumer (2) being adjustable by means of a throttle device (8) as a function of a load signal (LS) of the consumer (2), the throttle device (8) being adjustable by a dynamic pressure (p') derived from the load signal (LS), characterised in that the throttle device (8) is actuated by a hydraulic circuit (17) that detects the size and direction of a flow of pressure medium (7) to the consumer (2).
  2. A valve arrangement according to Claim 1, characterised in that the throttle device (8) is part of a brake valve (10) or a brake slide (11) of a brake valve (12) and that, when a control spool (12) of the directional control valve (3) is in a working position, the circuit (17) superimposes the dynamic pressure on a face side (18) of the brake slide (11) with an actuating pressure of the control spool (12).
  3. The valve arrangement according to Claim 2, characterised in that when the control spool (12) moves from a working position into a neutral position the circuit (17) passes the actuating pressure of the control spool (12) in an under-proportional manner to the brake slide (11) and vice versa.
  4. The valve arrangement according to either of Claims 2 or 3, characterised in that a hydraulic circuit (17) is integrated into each of the two control lines (25, 26) for the control spool (1).
  5. The valve arrangement according to any of the preceding claims, characterised in that the dynamic pressure (p') serves as the determinate for the volumetric flow via a metering orifice (9) of the directional control valve (3).
  6. The valve arrangement according to any of the preceding claims, characterised in that the dynamic pressure (p') is tapped from a pressure compensator (29) of the directional control valve (3).
  7. The valve arrangement according to any of Claims 2 to 6, characterised in that the brake slide (11) is built into the control spool (12) of the directional control valve (3) and can be axially displaced relative to the latter.
  8. The valve arrangement according to any of Claims 2 to 7, characterised in that the brake slide (11) releases a fluid-conveying connection (13) from the consumer (2) to a pressure medium tank (14) when the control spool (12) is in a switching position that corresponds to a working position for the consumer (2).
  9. The valve arrangement according to any of Claims 2 to 8, characterised in that the brake slide (11) can be supplied via breakthroughs (15, 15') with the dynamic pressure (p') at the ends of the control spool (12) on its two face sides.
EP10784445.8A 2009-12-15 2010-11-09 Valve arrangement for actuating a load Not-in-force EP2513491B1 (en)

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DE102009058371A DE102009058371A1 (en) 2009-12-15 2009-12-15 Valve arrangement for controlling a consumer
PCT/EP2010/006814 WO2011072778A1 (en) 2009-12-15 2010-11-09 Valve arrangement for actuating a load

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DE102022124970A1 (en) * 2022-09-28 2024-03-28 Deere & Company Arrangement for controlling a hydraulic three-point power lift

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Publication number Publication date
EP2513491A1 (en) 2012-10-24
WO2011072778A1 (en) 2011-06-23
DE102009058371A1 (en) 2011-06-16
WO2011072778A8 (en) 2011-09-09
JP2013513770A (en) 2013-04-22
US20120205563A1 (en) 2012-08-16

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