EP0224936B1 - Proportional directional valve with single pressure balance - Google Patents

Proportional directional valve with single pressure balance Download PDF

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Publication number
EP0224936B1
EP0224936B1 EP86116954A EP86116954A EP0224936B1 EP 0224936 B1 EP0224936 B1 EP 0224936B1 EP 86116954 A EP86116954 A EP 86116954A EP 86116954 A EP86116954 A EP 86116954A EP 0224936 B1 EP0224936 B1 EP 0224936B1
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EP
European Patent Office
Prior art keywords
valve
proportional directional
directional control
valve spool
load
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
EP86116954A
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German (de)
French (fr)
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EP0224936A2 (en
EP0224936A3 (en
Inventor
Karl-Thomas Dipl.-Ing. Rhody
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RHODY, KARL-THOMAS DIPL.-ING.
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Individual
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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
    • 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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool 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
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
    • F15B2013/006—Modular components with multiple uses, e.g. kits for either normally-open or normally-closed valves, interchangeable or reprogrammable manifolds

Definitions

  • the invention relates to a proportional directional control valve, the valve housing of which has a pressure connection, a tank connection and two consumer connections, with a valve piston controlling the connection of these connections in two working positions and an individual pressure compensator controlling the pressure connection depending on the load pressure.
  • a valve of this type is known, for example, from DE-A-3302 000.
  • Proportional directional control valves of the specified type as well as in general are used to control single-acting consumers such as cylinders with one load direction or motors with one direction of rotation and double-acting consumers such as cylinders with two load directions and motors with two directions of rotation.
  • Proportional behavior occurs when a load-independent constant oil flow is delivered to a consumer at every selectable position of the valve piston. Every consumer demands certain functional properties according to the circuit diagram, so that his work task is fulfilled.
  • the work task characterized by the "floating position" of the valve piston, in which a double-acting consumer can be moved in both directions by external forces without any significant resistance.
  • proportional directional control valves can only perform one single task at a time, i.e.
  • the valve pistons of these proportional directional control valves are specially designed and manufactured for your work task.
  • a proportional directional control valve for single-acting consumers with working connection A can therefore not be used as a proportional directional control valve for single-acting consumers with working connection B or for double-acting consumers.
  • valve block If several known proportional directional control valves are combined in a valve block in order to actuate several consumers of different types by a pump in any number, sequence and / or speed at the same time, the valve block must be disassembled and the corresponding proportional directional control valves replaced when the consumers change. This represents a considerable changeover effort.
  • the object of the present invention is to reduce the manufacturing and storage costs of the known proportional directional control valves and the changeover effort required when the consumers change in the case of proportional directional control valves interconnected in a block construction.
  • the effort for locking the valve piston in the predetermined end position can also be considerably reduced by providing a rotatable locking system or, when using a manual operating lever for the valve piston, a spring-loaded locking ball in the lever, which can be brought into engagement with adjustable locking bolts.
  • a proportional directional control valve with a valve housing 1, a valve piston 2, a single pressure compensator 3 and pilot operated pressure relief valves 4A and 4B for consumer connections A and B is shown.
  • the valve piston 2 has a first control line system 5 with an inner axial bore 5.1, a partial ring channel 5.2, a radial bore 5.3 and an axially widened partial ring channel 5.4. on.
  • the first control line system 5 is connected via a throttle 6 to an axial load feedback bore 7 which can be connected to the consumer connections A and B via radial bores 7.1 and 7.2, respectively.
  • the partial ring channel 5.2 of the control power system 5 is connected to axially milled slots 8A and 8B, which run in opposite directions in relation to the partial ring channel 5.2 and which are arranged offset by 90 ° to one another in the circumferential directions of the valve piston 2.
  • the valve piston 2 also has control notches 9 for controlling the oil flow. Furthermore, the valve piston has a second control line system 10 with a first ring channel 10.1, first axial slots 10.A, which are arranged offset by 180 ° to one another in the circumferential direction of the valve piston 2, second axial slots 10.B, which likewise in the circumferential direction of the valve piston 2 180 ° offset, the first axial slots 1 Q .A and the second axial slots 10.B in relation to the ring channel 10.1 run in opposite directions and are arranged offset by 90 ° to each other in the circumferential direction of the valve piston 2, and with a second ring channel 10.2, which is arranged at an axial distance from the first ring channel 10.1.
  • the second control line system 10 can be connected to a relief line 11.
  • the individual pressure compensator 3 has a control piston 12 with a piston chamber 12.1 and a control edge 12.2 and a spring 13 with a spring chamber 13.1.
  • the piston chamber 12.1 is connected to the spring chamber 13.1 via a throttle 14.
  • a pressure line P with a corresponding setting of the proportional directional control valve via the control edge 12.2, the piston chamber 12.1 and the control notches 9, supplies oil flow with the corresponding consumer pressure p A or PB to the consumer connection A or B.
  • the spring chamber 13.1 is connected to a load feedback line 16 via a check valve 15 in connection (see Fig. 6)
  • the pressure relief valve 4A or 4B has a piston 4.1, a spring 4.2 and a spring chamber 4.3.
  • the consumer connection A is connected to the spring chamber 4.3 via a throttle 17.
  • a pilot part 18 has a valve cone 18.1, a spring 18.2 and a valve seat 18.3.
  • the spring chamber 4.3 of the pressure relief valve 4A is in the floating position of the valve piston, cf. Fig. 3, via a relief line 19 with a check valve 20 with the first control line system 5 in connection.
  • FIG. 6 shows a circuit diagram of a valve block with four proportional directional control valves assembled.
  • the uppermost proportional directional control valve is a 4/3-way valve in piston rotation position D for a double-acting consumer.
  • the next proportional directional control valve is a 4/4-way valve in the piston rotation position D for a double-acting consumer with an axial floating position, which will be discussed in more detail in connection with FIG. 3.
  • the next proportional directional control valve is a 3/3-way valve in the spool position EB for a single-acting consumer at the consumer port B and the lowest proportional directional valve is a 3/3-way valve in the spool position EA for a single-acting consumer at the consumer port A.
  • the valve block is at the upper end with a End plate 27 covered. At the lower end of the valve block, an input plate 25 with an input pressure compensator 26 for a constant pump is provided at port P. Instead of the inlet plate with inlet pressure compensator and constant pump, a flow regulator with a variable displacement pump can also be provided.
  • the four proportional directional control valves are connected to one another in series via the load feedback line 16 and the relief line 11.
  • valve piston 2 In Fig. 1 the valve piston 2 is in the rotational position D, cf. Fig. 6, shown for double-acting consumers.
  • the central neutral position shown in Fig. 1 applies to all types of consumers, ie rotary positions of the valve piston.
  • the consumer ports A and B are blocked by the valve piston 2.
  • the pressure limitation and suction for the consumer connections takes place as follows. If a pressure in the consumer port B arises from external forces that is greater than the pressure set in the pilot part 18 of the pressure limiting valve 4B, the valve cone 18.1 lifts from its valve seat 18.3 against the spring force of the spring 18.2. A flow of control oil flows to the tank T from the consumer port B via the throttle 17, the spring chamber 4.3, the opened valve seat 18.3 of the valve cone 18.1.
  • the pressure relief valve 4A or 4B then ensures both the pressure limitation and the suction.
  • the consumer ports A and B are not completely pressure-tight on all longitudinal slide directional control valves. A leakage oil flow flows. In order to prevent the pressure drop in the consumer, lowering brake valves or unlockable check valves are used in the consumer lines.
  • a valve piston is now used, in which the consumer connections A and B are connected to each other in the central neutral position, since otherwise the leakage oil would flow from one consumer connection to the other consumer connection and could open the counterbalance valves or unlockable check valves in an uncontrolled manner. With the new proportional directional control valve, this is not possible because the leakage oil drain from the consumer connection A or B either flows into the tank or into the unloaded piston chamber 12.1 and then into the tank via the throttle 14.
  • the piston chamber 12.1 is therefore relieved in the central neutral position, even when the consumer connection A or B is under pressure.
  • the check valve 15 prevents oil from flowing through the load feedback line 16 into the tank or into the spring chamber 13.1 of the individual pressure compensator 3 from the load feedback of another proportional directional valve in a valve block which is in the working position.
  • valve piston 2 is also in the rotational position D, cf. Fig. 6, shown for double-acting consumers.
  • the consumer connection A is subjected to an oil flow and the consumer connection B is connected to the tank T.
  • the oil flow initially flows from the pressure line P via the control edge 12.2 into the piston chamber 12.1 of the individual pressure compensator 3, then via the control notches 9 and a preselected throttle cross-section into the consumer connection A.
  • the radial bore 7.1 of the load feedback is no longer covered by the housing 1, but with connected to the consumer connection A, so that the load pressure in the consumer connection A via the radial bore 7.1, the axial bore 7, the throttle 6, the axial bore 5.1, the radial bore 5.3 and the partial ring duct 5.4 of the control line system 5 into the spring chamber 13.1 of the individual pressure compensator 3 is reported back.
  • the control oil flow that continues to flow via the throttle 14 is no longer significant.
  • the pressure p' in the piston chamber 12.1 of the individual pressure compensator 3 is due to the control edge 12.2 independent of pressure in the pressure line P. Since the force of the spring 13 is a fixed design variable, a constant pressure difference p A -p 'is established and thus a load-independent, constant oil flow Q A at this piston position.
  • valve piston 2 is also in the rotational position D, cf. Fig. 6, shown for double-acting consumers. However, the valve piston 2 is shifted further to the left into a floating position compared to the working position according to FIG. 2, which is done by removing a stop plate 24, shown in FIG. 7, which serves as a stroke limiter. Floating position means that a double-acting consumer can be moved in both directions by external forces without any significant resistance.
  • the pressure p " in the consumer connection A is passed via the radial bore 7.1, the axial bore 7, the throttle 6, the radial bore 5.3, the partial ring channel 5.4 and the open cross-section 21 to the tank T.
  • the consumer connection A can also be used no specific oil flow can be supplied.
  • control oil flow flows freely from the input plate 25 via the relief line 11 and the second ring channel 10.2 through the proportional directional control valve back to the tank, provided the relief line 11 is not interrupted at another proportional directional control valve of the valve block.
  • valve piston 2 is in the rotational position EB, cf. Fig. 6, shown for a single-acting consumer at the consumer connection B.
  • the rotation of the valve piston from the rotary position D of FIGS. 1 to 3 in the rotary position EB of FIGS. 4 and 5 takes place in the present embodiment in that, as shown in FIGS. 7 and 7a, a cover cap 23 from the left end of the valve -Piston 2 removed, the valve piston 2 is rotated 45 ° counterclockwise and is fixed in the new rotational position EB by a corresponding positive connection between corresponding parts on the cover cap 23 and the valve piston 2.
  • valve piston 2 is adjusted to the right in the direction opposite to FIG. 4, as a result of which a state is established as has been described in connection with FIG. 2.
  • the relief line 11 is also interrupted in this position of the valve piston 2.
  • the valve piston 2 is rotated in the manner described above relative to the rotary position D for double-acting consumers by 45 ° clockwise, so that the axial slot 8A and the two axial slots 10A perform the functions described above for slot 8B and axial slots 10B.
  • the consumer connection B is of course also closed by a plug.
  • Fig. 10 different types of detents 1 to 7 are shown in tabular and symbolic form, the return of the valve piston 2 from the non-locked end positions A, B to the central neutral position 0 using the spring 33 of the valve piston 2.
  • the end position B corresponds to the right axial end position
  • the end position A corresponds to the left axial end position
  • the end position S corresponds to the left extreme axial floating position of the valve piston 2.
  • valve piston 2 which can be actuated mechanically by means of a hand lever 28, shown in FIG. 7, the type of detent can be changed by unscrewing detent bolts 31, 32 screwed into the housing 34 and rendering them ineffective by means of washers.
  • the locking bolts 31, 32 can be brought into engagement with a locking ball 29, which is arranged at the end of the lever 28 and is biased by a spring 30.
  • the change in the type of detent can also be carried out by a rotatable detent system, as shown in FIGS. 8, 8a and 8b.
  • this locking system various grooves for the locking types 1 to 7 shown in FIG. 10 are formed in this valve piston at a point on the proportional directional control valve or the valve piston 2 which is suitable for actuating the locking system.
  • a radial groove 35 is provided for the locking position S
  • a radial groove 36 for the locking position A and a radial groove 37 for the locking position B.
  • at least one ball 38 two balls 38 are shown in FIGS.
  • the ball 38 runs with axial displacement of the valve piston 2 with the aid of the spring 33 from the corresponding end positions A and B to the neutral position 0 on axial pans 43, 44 and 45 for the detent types 1 and 6 , 2 and 7 and 3.
  • the ball 38 is spring-centered in a radial groove 46.
  • valve piston 2 is shown only schematically without the grooves and pans with respect to the different rotational positions for the detent types 1 and 6, 2 and 7, 3, 4 and 5.
  • FIG. 9 shows a modified embodiment of the previous locking system, the grooves and pans being formed in a locking sleeve 48 which is connected to the valve piston 2 in the rotational position for the desired locking type by means of a stud screw 49.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Description

Die Erfindung betrifft ein Proportionalwegeventil, dessen Ventilgehäuse einen Druckanschluß, einen Tankanschluß und zwei Verbraucheranschlüsse aufweist, wobei ein die Verbindung dieser Anschlüsse in zwei Arbeitsstellungen steuernder Ventilkolben und eine den Druckanschluß lastdruckabhängig steuernde Einzeldruckwaage angeordnet sind.The invention relates to a proportional directional control valve, the valve housing of which has a pressure connection, a tank connection and two consumer connections, with a valve piston controlling the connection of these connections in two working positions and an individual pressure compensator controlling the pressure connection depending on the load pressure.

Ein Ventil dieser Gattung ist beispielsweise der DE-A-3302 000 als bekannt zu entnehmen.A valve of this type is known, for example, from DE-A-3302 000.

Proportionalwegeventile der angegebenen Gattung sowie auch ganz allgemein werden zur Steuerung von einfachwirkenden Verbrauchern wie Zylindern mit einer Lastrichtung oder Motoren mit einem Drehrichtung und von doppeltwirkenden Verbrauchen wie Zylindern mit zwei Lastrichtungen und Motoren mit zwei Drehrichtungen eingesetzt. Ein proportionales Verhalten ist gegeben, wenn bei jeder wählbaren Stellung des Ventilkolbens ein lastunabhängiger konstanter Ölstrom an einen Verbraucher abgegeben wird. Jeder Verbraucher fordert entsprechend dem Schaltplan bestimmte funktionelle Eigenschaften, damit seine Arbeitsaufgabe erfüllt wird. Zu den oben genannten vier Arbeitsaufgaben kommt noch die durch "Schwimmstellung" des Ventilkolbens gekennzeichnete Arbeitsaufgabe hinzu, bei welcher ein doppelwirkender Verbraucher ohne nennenswerten Widerstand in beide Richtungen durch äußere Kräfte bewegt werden kann. Die bisher bekannten, marktüblichen Proportionalwegeventile können nur jeweils eine einzige Arbeitsaufgabe erfüllen, d.h. die Ventilkolben dieser Proportionalwegeventile sind speziell für ihre Arbeitsaufgabe konstruiert und gefertigt. Ein Proportionalwegeventil für einfachwirkende Verbraucher mit Arbeitsanschluß A kann also nicht als Proportionalwegeventil für einfachwirkende Verbraucher mit Arbeitsanschluß B oder für doppeltwirkende Verbraucher verwendet werden.Proportional directional control valves of the specified type as well as in general are used to control single-acting consumers such as cylinders with one load direction or motors with one direction of rotation and double-acting consumers such as cylinders with two load directions and motors with two directions of rotation. Proportional behavior occurs when a load-independent constant oil flow is delivered to a consumer at every selectable position of the valve piston. Every consumer demands certain functional properties according to the circuit diagram, so that his work task is fulfilled. In addition to the four work tasks mentioned above, there is the work task characterized by the "floating position" of the valve piston, in which a double-acting consumer can be moved in both directions by external forces without any significant resistance. The previously known proportional directional control valves can only perform one single task at a time, i.e. The valve pistons of these proportional directional control valves are specially designed and manufactured for your work task. A proportional directional control valve for single-acting consumers with working connection A can therefore not be used as a proportional directional control valve for single-acting consumers with working connection B or for double-acting consumers.

Der Herstellungs- und Lageraufwand für die fünf verschiedenen Proportionalwegeventile ist daher sehr groß.The manufacturing and storage costs for the five different proportional directional control valves is therefore very large.

Sind mehrere bekannte Proportionalwegeventile in einem Ventilblock zusammengefaßt, um mehrere Verbraucher unterschiedlicher Art durch eine Pumpe in beliebiger Anzahl, Reihenfolge und/oder Geschwindigkeit auch gleichzeitig zu betätigen, so müssen bei Veränderung der Verbraucher der Ventilblock zerlegt und die entsprechenden Proportionalwegeventile ausgetauscht werden. Diese stellt einen erheblichen Umrüstungsaufwand dar.If several known proportional directional control valves are combined in a valve block in order to actuate several consumers of different types by a pump in any number, sequence and / or speed at the same time, the valve block must be disassembled and the corresponding proportional directional control valves replaced when the consumers change. This represents a considerable changeover effort.

Die Aufgabe der vorliegenden Erfindung besteht darin, den Herstellungs- und Lageraufwand der bekannten Proportionalwegeventile und den bei Veränderung der Verbraucher erforderlichen Umrüstungsaufwand bei in Blockbauweise zusammengeschalteten Proportionalwegeventilen zu verringern.The object of the present invention is to reduce the manufacturing and storage costs of the known proportional directional control valves and the changeover effort required when the consumers change in the case of proportional directional control valves interconnected in a block construction.

Diese Aufgabe wird erfindungsgemäß durch ein Proportionalwegeventil mit Einzeldruckwaage gelöst, welches durch Drehung seines Ventilkolbens für unterschiedliche Arbeitsaufgaben entsprechend den kennzeichnenden Merkmalen des Anspruchs 1 einstellbar ist.This object is achieved according to the invention by a proportional directional control valve with a single pressure compensator, which can be adjusted for different work tasks by rotating its valve piston in accordance with the characterizing features of claim 1.

Vorteilhafte Ausgestaltungen des erfindungsgemäßen Proportionalwegeventils mit Einzeldruckwaage sind in den Unteransprüchen 2 bis 22 angeführt. Erfindungsgemäß ist als nur noch ein einziges Proportionalwegeventil mit Einzeldruckwaage erforderlich, welches durch einfache Verdrehung des Ventilkolbens bzw. Entfernung eines Hubbergrenzers allen in der Praxis vorkommenden Arbeitsaufgaben gerecht wird. Der Herstellungs- und Lageraufwand für Proportionalwegeventile wird daher durch das erfindungsgemäße Proportionalwegeventil drastisch reduziert. Die Änderung der Ventilfunktion kann auch vom Anwender mit wenig geschultem Personal durchgeführt werden. Bei Veränderung von Verbrauchern, die über einen Ventilblock mit mehreren erfindungsgemäßen Proportionalwegeventilen durch eine Pumpe betätigt, werden, ist eine aufwendige Zerlegung des Blockes nicht mehr erforderlich, da die Veränderung der Ventilfunktion am eingebauten Proportionalwegeventil vorgenommen werden kann. Dies kann insbesondere durch Abnahme einer Abdeckkappe und entspchrende Verdrehung des Ventilkolbens mit anschließender formschlüssiger Verbindung zwischen Abdeckkappe und Ventilkolben zur drehfesten Fixierung des Ventilkolbens erfolgen.Advantageous refinements of the proportional directional control valve according to the invention with individual pressure compensators are specified in subclaims 2 to 22. According to the invention, only a single proportional directional control valve with a single pressure compensator is required, which, by simply rotating the valve piston or removing a stroke limiter, does all the work tasks that occur in practice. The manufacturing and storage costs for proportional directional control valves is therefore drastically reduced by the proportional directional control valve according to the invention. The valve function can also be changed by the user with little trained personnel. When changing consumers that are actuated by a pump via a valve block with several proportional directional control valves according to the invention, complex disassembly of the block is no longer necessary since the change in valve function can be carried out on the built-in proportional directional control valve. This can be done in particular by removing a cover cap and rotating the valve piston accordingly, followed by a positive connection between the cover cap and the valve piston for the rotationally fixed fixing of the valve piston.

Durch erfindungsgemäße Ausgestaltungen von Steuerleitungssystemen und Lastrückmeldungsbohrungen im Ventilkolben des Proportionalwegeventils in Verbindung mit der entsprechend zugeordneten und ausgestalteten Einzeldruckwaage und mit vorgesteuerten Druckbegrenzungsventil für die Verbraucherleitungen des Proportionalwegeventils und in Verbindung mit einer Lastrückmeldungsleitung und einer Entlastungsleitung zu der Eingangsplatte mit einer Eingangsdruckwaage einer Konstantpumpe oder zu dem Förderstromregeler einer Verstellpumpe erfolgt ein Verbraucherdruckaufbau bei Verwendung des erfindungsgemäßen Proportionalwegeventils nur bei entsprechender Anforderung durch die Verbraucher, so daß die Pumpenarbeit minimiert werdenkann. Dies gilt auch bei Verwendung eines Ventilblocks mit mehreren zusammengebauten erfindungsgemäßen Proportionalwegeventilen.Through inventive designs of control line systems and load feedback bores in the valve piston of the proportional directional control valve in connection with the correspondingly assigned and designed individual pressure compensator and with pilot operated pressure relief valve for the consumer lines of the proportional directional control valve and in connection with a load feedback line and a relief line to the input plate with an input pressure regulator or an input pressure compensator to an input pressure compensator to an input pressure compensator to an input pressure compensator or to a feed pressure compensator to an input pressure compensator to an input pressure compensator or to a feed pressure compensator for an input pressure compensator or to a feed pressure compensator to an input pressure compensator to a feed regulating valve to a feed pressure compensator A variable pressure pump builds up consumer pressure when the proportional directional control valve according to the invention is used only when the consumer requests it, so that the pump work can be minimized. This also applies when using a valve block with several assembled proportional directional control valves according to the invention.

Erfindungsgemäß kann auch der Aufwand zur Rastrierung des Ventilkolbens in vorgegebenen Endstellung erheblich verringert werden, indem ein drehbares Rastrierungssystem oder bei Verwendung eines Handbetätigungshebels für den Ventilkolben in dem Hebel eine federvorgespannte Rastkugel, welche mit einstellbaren Rastbolzen in Eingriff bringbar ist, vorgesehen ist.According to the invention, the effort for locking the valve piston in the predetermined end position can also be considerably reduced by providing a rotatable locking system or, when using a manual operating lever for the valve piston, a spring-loaded locking ball in the lever, which can be brought into engagement with adjustable locking bolts.

Weitere Vorteile, Merkmale und Anwendungsmöglichkeiten der vorliegenden Erfindung ergeben sich aus der nachfolgenden Beschreibung und Ausführungsbeispielen in Verbindung mit der Zeichnung. Darin zeigen:

  • Fig. 1 eine Schnittdarstellung des erfindungsgemäßen Proportionalwegeventils, eingestellt für doppeltwirkende Verbraucher, mit mittiger Neutralstellung des Ventilkolbens,
  • Fig. 2 eine Schnittdarstellung gemäß Fig. 1, wobei der Ventilkolben in eine Arbeitsstellung nach links verschoben ist,
  • Fig. 3 eine Schnittdarstellung gemäß Fig. 1, wobei der Ventilkolben noch weiter nach links in eine Schwimmstellung verschoben ist,
  • Fig. 4 eine Schnittdarstellung des erfindungsgemäßen Proportionalwegeventils, eingestellt für einen einfachwirkenden Verbraucher am Verbraucheranschluß B, wobei der Verbraucheranschluß B zum Tank geöffnet ist,
  • Fig. 5 eine Schnittdarstellung gemäß Fig. 4, wobei der Verbraucheranschluß B unter Lastdruck steht,
  • Fig. 6 einen Schaltplan eines Ventilblocks mit vier erfindungsgemäßen Proportionalwegeventilen, wobei der Ventilblock mit einer Eingangsplatte mit Eingangsdruckwaage verbunden ist,
  • Fig. 7 eine Schnittdarstellung der erfindungsgemäßen Proportionalwegeventils mit Handbetätigungshebel und erfindungsgemäßen Rastrierungssystem,
  • Fig. 7a eine Schnittdarstellung längs der Linie Vlla-Vlla der Fig. 7,
  • Fig. 8, 8a und 8b Schnittdarstellungen einer anderen Ausführungsform eines erfindungsgemäßen Rastrierungssystems,
  • Fig. 9 eine abgewandelte, schematisch dargestellte Ausführungsform des Rastrierungssystem gemäß Fig. 8, 8a und 8b, und
  • Fig 10 ein tabellarische Auflistung der verschiedenen Rastarten für das erfindungsgemäße Proportionalwegeventil.
Further advantages, features and possible uses of the present invention result from the following description and exemplary embodiments in conjunction with the drawing. In it show:
  • 1 is a sectional view of the proportional directional control valve according to the invention, set for double-acting consumers, with the valve piston in the central neutral position,
  • 2 shows a sectional view according to FIG. 1, the valve piston being shifted to the left into a working position,
  • 3 shows a sectional view according to FIG. 1, the valve piston being shifted even further to the left into a floating position,
  • 4 shows a sectional illustration of the proportional directional control valve according to the invention, set for a single-acting consumer at the consumer connection B, the consumer connection B being open to the tank,
  • 5 is a sectional view of FIG. 4, wherein the consumer connection B is under load pressure,
  • 6 shows a circuit diagram of a valve block with four proportional directional control valves according to the invention, the valve block being connected to an inlet plate with inlet pressure compensator,
  • 7 is a sectional view of the proportional directional control valve according to the invention with manual actuation lever and locking system according to the invention,
  • 7a is a sectional view taken along the line Vlla-Vlla of Fig. 7,
  • 8, 8a and 8b sectional views of another embodiment of a locking system according to the invention,
  • 9 shows a modified, schematically represented embodiment of the locking system according to FIGS. 8, 8a and 8b, and
  • 10 is a tabular listing of the various types of rest for the proportional directional control valve according to the invention.

In den Figuren ist ein Proportionalwegeventil mit einem Ventilgehäuse 1, einem Ventilkolben 2, einer Einzeldruckwaage 3 und vorgesteuerten Druckbegrenzventilen 4A und 4B für Verbraucheranschlüsse A und B dargstellt. Der Ventilkolben 2 weist ein erstes Steuerleitungssytem 5 mit einer inneren axialen Bohrung 5.1, einem Teilringkanal 5.2, einer radialen Bohrung 5.3 und einem axial verbreiterten Teilringkanal 5.4. auf. Das erste Steuerleitungssystem 5 steht über eine Drossel 6 mit einer axialen Lastrückmeldungsbohrung 7 in Verbindung, die über radiale Bohrungen 7.1 und 7.2 jeweils mit den Verbraucheranschlüssen A und B verbindbar ist. Der Teilringkanal 5.2 des Steuerleistungssystem 5 steht in Verbindung mit axialen gefrästen Schlitzen 8A und 8B, die im Verhältnis zum Teilringkanal 5.2 in entgegengesetzte Richtungen verlaufen und welche in Umfangsrichtungen des Ventilkolbens 2 um 90° versetzt zueinander angeordnet sind.In the figures, a proportional directional control valve with a valve housing 1, a valve piston 2, a single pressure compensator 3 and pilot operated pressure relief valves 4A and 4B for consumer connections A and B is shown. The valve piston 2 has a first control line system 5 with an inner axial bore 5.1, a partial ring channel 5.2, a radial bore 5.3 and an axially widened partial ring channel 5.4. on. The first control line system 5 is connected via a throttle 6 to an axial load feedback bore 7 which can be connected to the consumer connections A and B via radial bores 7.1 and 7.2, respectively. The partial ring channel 5.2 of the control power system 5 is connected to axially milled slots 8A and 8B, which run in opposite directions in relation to the partial ring channel 5.2 and which are arranged offset by 90 ° to one another in the circumferential directions of the valve piston 2.

Der Ventilkolben 2 weist darüber hinaus zur Steuerung des Ölstroms Steuerkerben 9 auf. Weiterhin weist der Ventilkolben eine zweites Steuerleitungssystem 10 mit einem ersten Ringkanal 10.1, ersten axialen Schlitzen 10.A, welche in Umfangsrichtung des Ventilkolbens 2 um 180° zueinander versetzt angeordnet sind, zweiten axialen Schlitzen 10.B, die in Umfangsrichtung des Ventilkolbens 2 ebenfalls um 180° versetzt angeordnet sind, wobei die ersten axialen Schlitze 1 Q.A und die zweiten axialen Schlitze 10.B im Verhältnis zum Ringkanal 10.1 in entgegengesetzte Richtungen verlaufen und in Umfangsrichtung des Ventil- kolbens 2 um 90° versetzt zueinander angeordnet sind, und mit einem zweiten Ringkanal 10.2, der in axialem Abstand vom ersten Ringkanal 10.1 angeordnet ist. Das zweite Steuerleitungssystem 10 ist mit einer Entlastungsleitung 11 verbindbar.The valve piston 2 also has control notches 9 for controlling the oil flow. Furthermore, the valve piston has a second control line system 10 with a first ring channel 10.1, first axial slots 10.A, which are arranged offset by 180 ° to one another in the circumferential direction of the valve piston 2, second axial slots 10.B, which likewise in the circumferential direction of the valve piston 2 180 ° offset, the first axial slots 1 Q .A and the second axial slots 10.B in relation to the ring channel 10.1 run in opposite directions and are arranged offset by 90 ° to each other in the circumferential direction of the valve piston 2, and with a second ring channel 10.2, which is arranged at an axial distance from the first ring channel 10.1. The second control line system 10 can be connected to a relief line 11.

Die Einzeldruckwaage 3 weist einen Regelkolben 12 mit einer Kolbenkammer 12.1 und einer Regelkante 12.2 und eine Feder 13 mit einer Federkammer 13.1 auf. Die Kolbenkammer 12.1 steht über eine Drossel 14 mit der Federkammer 13.1 in Verbindung. Eine Druckleitung P liefert bei entsprechender Einstellung des Proportionalwegeventils über die Regelkante 12.2, die Kolbenkammer 12.1 und die Steuerkerben 9 Ölstrom mit dem entsprechenden Verbraucherdruck pA bzw. PB zum Verbraucheranschluß A bzw. B. Die Federkammer 13.1 steht über ein Rückschlagventil 15 mit einer Lastrückmeldungsleitung 16 in Verbindung (siehe Fig. 6)The individual pressure compensator 3 has a control piston 12 with a piston chamber 12.1 and a control edge 12.2 and a spring 13 with a spring chamber 13.1. The piston chamber 12.1 is connected to the spring chamber 13.1 via a throttle 14. A pressure line P, with a corresponding setting of the proportional directional control valve via the control edge 12.2, the piston chamber 12.1 and the control notches 9, supplies oil flow with the corresponding consumer pressure p A or PB to the consumer connection A or B. The spring chamber 13.1 is connected to a load feedback line 16 via a check valve 15 in connection (see Fig. 6)

Das Druckbegrenzungsventil 4A bzw. 4B weist einen Kolben 4.1, eine Feder 4.2 und eine Federkammer 4.3 auf. Der Verbraucheranschluß A steht über eine Drossel 17 mit der Federkammer 4.3 in Verbindung. Ein Vorsteuerteil 18 weist einen Ventilkegel 18.1, eine Feder 18.2 und einen Ventilsitz 18.3 auf. Die Federkammer 4.3 des Druckbegrenzungsventils 4A steht in Schwimmstellung des Ventilkolbens, vgl. Fig. 3, über eine Entlastungsleitung 19 mit einem Rückschlagventil 20 mit dem ersten Steuerleitungssystem 5 in Verbindung.The pressure relief valve 4A or 4B has a piston 4.1, a spring 4.2 and a spring chamber 4.3. The consumer connection A is connected to the spring chamber 4.3 via a throttle 17. A pilot part 18 has a valve cone 18.1, a spring 18.2 and a valve seat 18.3. The spring chamber 4.3 of the pressure relief valve 4A is in the floating position of the valve piston, cf. Fig. 3, via a relief line 19 with a check valve 20 with the first control line system 5 in connection.

In Fig. 6 ist ein Schaltplan eines Ventilblocks mit vier zusammengebauten Proportionalwegeventilen gezeigt. Das oberste Proportionalwegeventil ist ein 4/3-Wegeventil in Kolbendrehstellung D für einen doppeltwirkenden Verbraucher. Das nächste Proportionalwegeventil ist ein 4/4-Wegeventil in Kolbendrehstellung D für einen doppeltwirkenden Verbraucher mit axialer Schwimmstellung, worauf näher in Verbindung mit Fig. 3 eingegangen wird. Das nächste Proportionalwegeventil ist ein 3/3-Wegeventil in Kolbendrehstellung EB für einen einfachwirkenden Verbraucher am Verbraucheranschluß B und das unterste Proportionalwegeventil ist ein 3/3-Wegeventil in Kolbendrehstellung EA für einen einfachwirkenden Verbraucher am Verbraucheranschluß A. Der Ventilblock ist am oberen Ende mit einer Abschlußplatte 27 abgedeckt. Am unteren Ende des Ventilblocks ist eine Eingangsplatte 25 mit einer Eingangsdruckwaage 26 für eine Konstantpumpe am Anschluß P vorgesehen. Anstelle der Eingangsplatte mit Eingangsdruckwaage und Konstantpumpe kann auch ein Förderstromregeler mit einer Vestellpumpe vorgesehen werden. Die vier Proportionalwegeventile sind über die Lastrückmeldungsleitung 16 und die Entlastungsleitung 11 in Reihe miteinander verbunden.6 shows a circuit diagram of a valve block with four proportional directional control valves assembled. The uppermost proportional directional control valve is a 4/3-way valve in piston rotation position D for a double-acting consumer. The next proportional directional control valve is a 4/4-way valve in the piston rotation position D for a double-acting consumer with an axial floating position, which will be discussed in more detail in connection with FIG. 3. The next proportional directional control valve is a 3/3-way valve in the spool position EB for a single-acting consumer at the consumer port B and the lowest proportional directional valve is a 3/3-way valve in the spool position EA for a single-acting consumer at the consumer port A. The valve block is at the upper end with a End plate 27 covered. At the lower end of the valve block, an input plate 25 with an input pressure compensator 26 for a constant pump is provided at port P. Instead of the inlet plate with inlet pressure compensator and constant pump, a flow regulator with a variable displacement pump can also be provided. The four proportional directional control valves are connected to one another in series via the load feedback line 16 and the relief line 11.

Im nachfolgenden wird die Funktionsweise des Proportionalwegeventils in Verbindung mit den einzelnen Figuren beschrieben.The operation of the proportional directional control valve is described below in connection with the individual figures.

In Fig. 1 ist der Ventilkolben 2 in Drehstellung D, vgl. Fig. 6, für doppeltwirkende Verbraucher gezeigt. Die in Fig. 1 dargestellte mittige Neutralstellung gilt für alle Verbraucherarten, d.h. Drehstellungen des Ventilkolbens. Die Verbraucheranschlüsse A und B sind durch den Ventilkolben 2 gesperrt. Die Druckbegrenzung und Nachsaugung für die Verbraucheranschlüsse geschieht folgendermaßen. Entsteht im Verbraucheranschluß B durch äußere Kräfte ein Druck, der größer ist, als der im Vorsteuerteil 18 des Druckbegrenzungsventils 4B eingestellte Druck, so hebt sich der Ventilkegel 18.1 gegen die Federkraft der Feder 18.2 von seinem Ventilsitz 18.3. Vom Verbraucheranschluß B fließt über die Drossel 17, die Federkammer 4.3, den geöffneten Ventilsitz 18.3 des Ventilkegels 18.1 ein Steuerölstrom zum Tank T. Hierdurch wird an der Drossel 17 ein Druckgefälle erzeugt, wodurch der Druck in der Federkammer 4.3 kleiner als im Verbraucheranschluß B wird. Der Kolben 4.1 wird daher nach rechts verschoben, so daß eine unmittelbare Verbindung zwischen dem Verbraucheranschluß B und dem Tank T hergestellt wird. Bei einem doppeltwirkenden Verbraucher entsteht bei einem entsprechenden Überdruck im Verbraucheranschluß B im Verbraucheranschluß A und der Federkammer 4.3 seines Druckbegrenzungsventils 4A ein Unterdruck. Der Druck des Tankes T ist daher größer als der Druck p" im Verbraucheranschluß A. Über die Ringfläche des Kolbens 4.1 wirkt dann eine Kraft gegen die Feder 4.2, welche den Kolben 4.1 nach links verschiebt und den Tank T unmittelbar mit dem Verbraucheranschluß A zum Druckausgleich verbindet. Analogues gilt bei entsprechender Überbelastung des Verbraucheranschlusses A.In Fig. 1 the valve piston 2 is in the rotational position D, cf. Fig. 6, shown for double-acting consumers. The central neutral position shown in Fig. 1 applies to all types of consumers, ie rotary positions of the valve piston. The consumer ports A and B are blocked by the valve piston 2. The pressure limitation and suction for the consumer connections takes place as follows. If a pressure in the consumer port B arises from external forces that is greater than the pressure set in the pilot part 18 of the pressure limiting valve 4B, the valve cone 18.1 lifts from its valve seat 18.3 against the spring force of the spring 18.2. A flow of control oil flows to the tank T from the consumer port B via the throttle 17, the spring chamber 4.3, the opened valve seat 18.3 of the valve cone 18.1. As a result, a pressure drop is generated at the throttle 17, as a result of which the pressure in the spring chamber 4.3 is lower than in the consumer port B. The piston 4.1 is therefore shifted to the right so that a direct connection between the consumer connection B and the tank T is established. In the case of a double-acting consumer, a corresponding overpressure in the consumer connection B in the consumer connection A and the spring chamber 4.3 of its pressure relief valve 4A creates a negative pressure. The pressure of the tank T is therefore greater than the pressure p " in the consumer port A. A force then acts against the spring 4.2 over the annular surface of the piston 4.1, which displaces the piston 4.1 to the left and the tank T directly with the consumer port A for pressure compensation Analogues applies if the consumer connection A is overloaded accordingly.

Ist ein einfachwirkender Verbraucher angeschlossen, so ist der nicht benötigte Verbraucheranschluß mit einem Stopfen verschlossen. Das Druckbegrenzungsventil 4A bzw. 4B sorgt dann sowohl für die Druckbegrenzung als auch für die Nachsaugung.If a single-acting consumer is connected, the unused consumer connection is closed with a plug. The pressure relief valve 4A or 4B then ensures both the pressure limitation and the suction.

Bei allen Längsschieberwegeventilen sind die Verbraucheranschlüsse A und B nicht völlig druckdicht. Es fließt ein Leckölstrom. Um bei den Verbrauchern ein Absinken des Druckkes zu verhindern, werden in die Verbraucherleitungen Senkbremsventile oder entsperrbare Rückschlagventile eingesetzt. Bei den gebräuchlichen Proportionalwegeventilen wird nun ein Ventilkolben eingesetzt, bei dem in der mittigen Neutralstellung die Verbraucheranschlüsse A und B miteinander zum Tank verbunden sind, da sonst das Lecköl von einem Verbraucheranschluß zum anderen Verbraucheranschluß überströmen würde und die Senkbremsventile oder entsperrbaren Rückschlagventile unkontrolliert öffnen könnte. Bei dem neuen Proportionalwegeventil ist dies nicht möglich, da der Leckölabfluß vom Verbraucheranschluß A oder B entweder in den Tank oder in die entlastete Kolbenkammer 12.1 und dann über die Drossel 14 in den Tank fließt. Bei dem neuen Proportionalwegeventil ist die Kolbenkammer 12.1 daher in mittiger Neutralstellung entlastet, auch wenn der Verbraucheranschluß A oder B unter Druck steht. Das Rück-schlagventil 15 verhindert, daß aus der Lastrückmeldung eines anderen Proportionalwegeventils in einem Ventilblock, das sich in Arbeitsstellung befindet, Öl über die Lastrückmeldungsleitung 16 in den Tank bzw. in die Federkammer 13.1 der Einzeldruckwaage 3 fließt.The consumer ports A and B are not completely pressure-tight on all longitudinal slide directional control valves. A leakage oil flow flows. In order to prevent the pressure drop in the consumer, lowering brake valves or unlockable check valves are used in the consumer lines. In the conventional proportional directional control valves, a valve piston is now used, in which the consumer connections A and B are connected to each other in the central neutral position, since otherwise the leakage oil would flow from one consumer connection to the other consumer connection and could open the counterbalance valves or unlockable check valves in an uncontrolled manner. With the new proportional directional control valve, this is not possible because the leakage oil drain from the consumer connection A or B either flows into the tank or into the unloaded piston chamber 12.1 and then into the tank via the throttle 14. With the new proportional directional control valve, the piston chamber 12.1 is therefore relieved in the central neutral position, even when the consumer connection A or B is under pressure. The check valve 15 prevents oil from flowing through the load feedback line 16 into the tank or into the spring chamber 13.1 of the individual pressure compensator 3 from the load feedback of another proportional directional valve in a valve block which is in the working position.

In der in Fig. 1 geziegten mittigen Neutralstellung des Ventilkolbens 2 fließt der Steuerölstrom von der Eingangsplatte 25 über die Entlastungsleitung 11 und den ersten Ringkanal 10.1 das Steuerleitungssystems 10 ungehindert durch das Proportionalwegeventil. Wenn kein anderes Proportionalwegeventil im Ventilblock in Arbeitsstellung ist, baut sich kein Pumpendruck, außer dem Mindestregeldruck der Eingangsplatte von ca. 3 bis 5 bar, auf, da der Steuerölstrom ungehindert zum Tank T geleitet wird.In the central neutral position of the valve piston 2 shown in FIG. 1, the control oil flow flows from the input plate 25 via the relief line 11 and the first ring channel 10.1 of the control line system 10 unhindered by the proportional directional control valve. If no other proportional directional control valve in the valve block is in the working position, no pump pressure builds up, apart from the minimum control pressure of the inlet plate of approx. 3 to 5 bar, since the control oil flow is directed to tank T unhindered.

In Fig. 2 ist der Ventilkolben 2 ebenfalls in Drehstellung D, vgl. Fig. 6, für doppeltwirkende Verbraucher gezeigt. Bei der in Fig. 2 gezeigten nach links verschobenen Arbeistellung wird der Verbraucheranschluß A mit einem Ölstrom beaufschlagt und der Verbraucheranschluß B mit dem Tank T verbunden. Der Ölstrom fließt zunächst von der Druckleitung P über die Regelkante 12.2 in die Kolbenkammer 12.1 der Einzeldruckwaage 3, dann über die Steuerkerben 9 und einen vorgewählten Drosselquerschnitt in den Verbraucheranschluß A. Die radiale Bohrung 7.1 der Lastrückmeldung ist nicht mehr vom Gehäuse 1 überdeckt, sondern mit dem Verbraucheranschluß A verbunden, so daß der Lastdruck im Verbraucheranschluß A über die radiale Bohrung 7.1, die axiale Bohrung 7, die Drossel 6, die axiale Bohrung 5.1, die radiale Bohrung 5.3 und den Teilringkanal 5.4 des Steuerleitungssystem 5 in die Federkammer 13.1 der Einzeldruckwaage 3 zurückgemeldet wird. Gegenüber diesem Haupt- ölstrom hat der weiterhin über die Drossel 14 fließende Steuerölstrom keine Bedeutung mehr. Über die Regelkante 12.2 wird der Ölstrom so geregelt, daß an der Einzeldruckwaage 3 Gleichgewichtsbedingung herrscht, d.h. (pA-p')xA-4=Kraft der Feder 13. Der Druck p' in der Kolbenkammer 12.1 der Einzeldruckwaage 3 ist wegen der Regelkante 12.2 unabhängig von Druck in der Druckleitung P. Da die Kraft der Feder 13 eine feste konstruktive Größe ist, stellt sich eine konstante Druckdifferenz pA-p' und damit bei dieser Kolbenstellung ein lastunabhängiger, konstanter Ölstrom QA ein.2, the valve piston 2 is also in the rotational position D, cf. Fig. 6, shown for double-acting consumers. In the working position shifted to the left in FIG. 2, the consumer connection A is subjected to an oil flow and the consumer connection B is connected to the tank T. The oil flow initially flows from the pressure line P via the control edge 12.2 into the piston chamber 12.1 of the individual pressure compensator 3, then via the control notches 9 and a preselected throttle cross-section into the consumer connection A. The radial bore 7.1 of the load feedback is no longer covered by the housing 1, but with connected to the consumer connection A, so that the load pressure in the consumer connection A via the radial bore 7.1, the axial bore 7, the throttle 6, the axial bore 5.1, the radial bore 5.3 and the partial ring duct 5.4 of the control line system 5 into the spring chamber 13.1 of the individual pressure compensator 3 is reported back. Compared to this main oil flow, the control oil flow that continues to flow via the throttle 14 is no longer significant. The oil flow is regulated via the control edge 12.2 so that there is an equilibrium condition on the individual pressure compensator 3, ie (p A -p ') xA-4 = force of the spring 13. The pressure p' in the piston chamber 12.1 of the individual pressure compensator 3 is due to the control edge 12.2 independent of pressure in the pressure line P. Since the force of the spring 13 is a fixed design variable, a constant pressure difference p A -p 'is established and thus a load-independent, constant oil flow Q A at this piston position.

Da der Teilringkanal 5.2 des Steuerleitungssystems 5 nicht mehr mit dem Tank T in Verbindung steht, findet keine Entlastung der Federkammer 13.1 der Einzeldruckwaage 3 statt. Wenn diese Proportionalwegeventil das am höchsten belastete aktive Proportionalwegeventil in einem Ventilblock ist, so würde der Lastdruck p" über das Rückschlagventil 15 und die Lastrückmeldungsleitung 16 an die Eingangsdruckwaage 2.6 in der Eingangsplatte 25 gegeben.Since the sub-ring duct 5.2 of the control line system 5 is no longer connected to the tank T, the spring chamber 13.1 of the individual pressure compensator 3 is not relieved. If this proportional directional control valve is the most heavily loaded active proportional directional control valve in a valve block, then the load pressure p "would be given via the check valve 15 and the load feedback line 16 to the inlet pressure compensator 2.6 in the inlet plate 25.

In der in Fig. 2 gezeigten Stellung des Ventilkolbens 2 ist der drucklose Umlauf des Steuerölstroms über die Entlastungsleitung 11 aufgehoben, da der Steuerölstrom den Ventilkolben 2 nicht mehr über einen Ringkanal 10.1 oder 10.2 passieren kann. An der Pumpe muß sich daher der maximale Verbraucherdruk und zusätzlich der Regeldruck einstellen.In the position of the valve piston 2 shown in FIG. 2, the pressureless circulation of the control oil current over the relief line 11 canceled, since the control oil flow can no longer pass the valve piston 2 via an annular channel 10.1 or 10.2. The maximum consumer pressure and the control pressure must therefore be set on the pump.

In Fig. 3 ist der Ventilkolben 2 ebenfalls in Drehstellung D, vgl. Fig. 6, für doppeltwirkende Verbraucher gezeigt. Allerdings ist der Ventilkolben 2 gegenüber der Arbeitsstellung gemäß Fig. 2 noch weiter nach links in eine Schwimmstellung verschoben, was durch Entfernung einer Anschlagplatte 24, gezeigt in Fig. 7, erfolgt, die als Hubbegrenzer dient. Schwimmstellung bedeutet hierbei, daß ein doppeltwirkender Verbraucher ohne nennenswerten Widerstand durch äußere Kräfte in beide Richtungen bewegt werden kann.In Fig. 3 the valve piston 2 is also in the rotational position D, cf. Fig. 6, shown for double-acting consumers. However, the valve piston 2 is shifted further to the left into a floating position compared to the working position according to FIG. 2, which is done by removing a stop plate 24, shown in FIG. 7, which serves as a stroke limiter. Floating position means that a double-acting consumer can be moved in both directions by external forces without any significant resistance.

Der Druck p" in dem Verbraucheranschluß A wird über die radiale Bohrung 7.1 die axiale Bohrung 7, die Drossel 6, die radiale Bohrung 5.3, den Teilringkanal 5.4 und den geöffneten Querschnitt 21 zum Tank T geleitet. Eine Lastrückmeldung in die Federkammer 13.1 der Einzeldruckwaage 3 erfolgt nicht. Damit stellt sich für die Einzeldruckwaage das gleiche Lastverhältnis wie bei der in Fig. 1 gezeigten mittigen Neutralstellung ein, d.h. von der Druckleitung P fließt nur ein kleiner, von der Drossel 14 bestimmter Steuerölstrom in die Kolbenkammer 12.1. Der Verbraucheranschluß A kann mit keinem konkreten Ölstrom versorgt werden.The pressure p " in the consumer connection A is passed via the radial bore 7.1, the axial bore 7, the throttle 6, the radial bore 5.3, the partial ring channel 5.4 and the open cross-section 21 to the tank T. A load feedback into the spring chamber 13.1 of the individual pressure compensator 3 1, that is, the same load ratio as in the central neutral position shown in FIG. 1, ie only a small control oil flow, determined by the throttle 14, flows into the piston chamber 12.1 from the pressure line P. The consumer connection A can also be used no specific oil flow can be supplied.

Wird der Verbraucher am Verbraucheranschluß A durch eine äußere Kraft so bewegt, daß Öl in den Verbraucheranschluß A zurückströmt, kann sich in der Federkammer 4.3 des Druckbegrenzungsventils 4A kein Druck aufbauen, da die Federkammer 4.3 über die Entlastungsleitung 19, das Rückschlagventil 20, das Steuerleitungssystem 5 und den Querschnitt 21 mit den Tank T verbunden ist. Hierdurch wird das Vorsteuerteil 18 des Druckbegrenzungsventils 4A umgangen.If the consumer at the consumer port A is moved by an external force so that oil flows back into the consumer port A, no pressure can build up in the spring chamber 4.3 of the pressure relief valve 4A, since the spring chamber 4.3 via the relief line 19, the check valve 20, the control line system 5 and the cross section 21 is connected to the tank T. This bypasses the pilot part 18 of the pressure relief valve 4A.

Entsteht im Verbraucheranschluß A durch eine entgegengesetzte Bewegung des Verbrauchers ein Unterdruck gegenüber dem Tankdruck, so erfolgt, wie in Verbindung mit Fig. 1 beschrieben, eine Nachsaugung durch eine Verschiebung des Kolbens 4.1 nach links und die hierdurch bewirkte unmittelbare Verbindung zwischen Verbraucheranschluß A und Tank T. Das Rückschlagventil 20 in der Entlastungsleitung 19 verhindert, daß sich in der Federkammer 4.3 ein Tankdruck aufbaut, der den Nachsaugvorgang verhindern würde. Da der Verbraucheranschluß B über den Ventilkolben 2 unmittelbar mit dem Tank T verbunden ist, ist bei entsprechender, von außer veranlaßter Bewegung des Verbrauchers am Verbraucheranschluß B ein Ölabfluß und ein Ölzufluß gegeben.If there is a vacuum in the consumer connection A due to an opposite movement of the consumer compared to the tank pressure, then, as described in connection with FIG. 1, suction is carried out by displacing the piston 4.1 to the left and the direct connection between the consumer connection A and the tank T which is caused thereby The check valve 20 in the relief line 19 prevents a tank pressure from building up in the spring chamber 4.3, which would prevent the suction process. Since the consumer connection B is connected directly to the tank T via the valve piston 2, there is an oil drain and an oil inflow with a corresponding movement of the consumer at the consumer connection B which is not caused.

In der in Fig. 3 gezeigten Schwimmstellung des Ventilkolbens 2 fließt Steuerölstrom von der Eingangsplatte 25 über die Entlastungsleitung 11 und den zweiten Ringkanal 10.2 ungehindert durch das Proportionalwegeventil zurück zum Tank, vorausgesetzt, die Entlastungsleitung 11 ist nicht an einem anderen Proportionalwegeventil des Ventilblocks unterbrochen.In the floating position of the valve piston 2 shown in FIG. 3, control oil flow flows freely from the input plate 25 via the relief line 11 and the second ring channel 10.2 through the proportional directional control valve back to the tank, provided the relief line 11 is not interrupted at another proportional directional control valve of the valve block.

In den Fig. 4 und 5 ist der Ventilkolben 2 in Drehstellung EB, vgl. Fig. 6, für einen einfachwirkenden Verbraucher am Verbraucheranschluß B dargestellt. Die Drehung des Ventilkolbens von der Drehstellung D der Fig. 1 bis 3 in die Drehstellung EB der Fig. 4 und 5 erfolgt bei dem vorliegenden Ausführungsbeispiel dadurch, daß, wie in Fig. 7 und 7a dargstellt, eine Abdeckkappe 23 vom linken Ende des Ventil-kolbens 2 abgenommen, der Ventilkolben 2 um 45° im Gegenuhrzeigersinn gedreht und in der neuen Drehstellung EB durch einen entsprechenden Formschluß zwischen entsprechenden Teilen an der Abdeckkappe 23 und dem Ventilkolben 2 fixiert wird.4 and 5, the valve piston 2 is in the rotational position EB, cf. Fig. 6, shown for a single-acting consumer at the consumer connection B. The rotation of the valve piston from the rotary position D of FIGS. 1 to 3 in the rotary position EB of FIGS. 4 and 5 takes place in the present embodiment in that, as shown in FIGS. 7 and 7a, a cover cap 23 from the left end of the valve -Piston 2 removed, the valve piston 2 is rotated 45 ° counterclockwise and is fixed in the new rotational position EB by a corresponding positive connection between corresponding parts on the cover cap 23 and the valve piston 2.

Wie in Verbindung mit Fig. 1 angemerkt, liegen in der mittigen Neutralstellung des Ventilkolbens 2 in der in den Fig. 4 und 5 gezeigten Drehstellung EB die gleichen Verhältnisse vor wie bei anderen Drehstellungen des Ventilkolbens 2, wobei natürlich hier der nicht benötigte Verbraucheranschluß A durch einen Stopfen 22 verschlossen ist. In Fig. 4 ist der Verbraucheranschluß B entsprechend der gewählten axialen Stellung des Ventilkolbens 2 unmittelbar über den Ventilkolben 2 mit den Tank T verbunden. Trotz axialer Auslenkung des Ventilkolbens 2 baut sich jedoch im Verbraucheranschluß A kein Betriebsdruck auf, da die Federkammer 13.1 der Einzeldruckwaage 3 über das Steuerleitungssystem 5 und den axialen Schlitz 8B zum Tank T entlastet ist. Der Steuerölstrom von der Druckleitung P in die Kolbenkammer 12.1 der Einzeldruckwaage 3 fließt über die Drossel 14 zum Tank T ab. Außerdem fliebt ein geringer Reststrom, z.B. ca. 0,7 1/min über die Drossel 6 zum Tank T ab.As noted in connection with FIG. 1, in the central neutral position of the valve piston 2, in the rotational position EB shown in FIGS. 4 and 5, the same conditions are present as in other rotational positions of the valve piston 2, with of course the consumer connection A not required here a plug 22 is closed. 4, the consumer connection B is connected directly to the tank T via the valve piston 2 in accordance with the selected axial position of the valve piston 2. Despite the axial deflection of the valve piston 2, however, no operating pressure builds up in the consumer port A, since the spring chamber 13.1 of the individual pressure compensator 3 is relieved to the tank T via the control line system 5 and the axial slot 8B. The control oil flow from the pressure line P into the piston chamber 12.1 of the individual pressure compensator 3 flows through the throttle 14 to the tank T. In addition, there is a small residual current, e.g. 0.7 l / min via throttle 6 to tank T.

Da die axialen Schlitze 10B die Entlastungsleitung 11 in der in Fig. 4 geziegten Stellung des Ventilkolbens 2 überdecken, hält das so eingestellt Proportionalwegeventil die Entlastungsleitung 11 in einem Ventilblock offen.Since the axial slots 10B cover the relief line 11 in the position of the valve piston 2 shown in FIG. 4, the proportional directional control valve thus set keeps the relief line 11 open in a valve block.

In Fig. 5 ist der Ventilkolben 2 in die zu Fig. 4 entgegengesetzte Richtung nach rechts verstellt, wodurch sich ein Zustand einstellt, wie er in Verbindung mit Fig. 2 beschrieben worden ist. Die Entlastungsleitung 11 ist bei dieser Stellung des Ventilkolbens 2 also ebenfalls unterbrochen.In FIG. 5, the valve piston 2 is adjusted to the right in the direction opposite to FIG. 4, as a result of which a state is established as has been described in connection with FIG. 2. The relief line 11 is also interrupted in this position of the valve piston 2.

Wenn das Proportionalwegeventil in ein Drehstellung EA, vgl. Fig. 6, für einen einfachwirkenden Verbraucher am Verbraucheranschluß A gebracht werden soll, so wird der Ventilkolben 2 in der oben beschriebenen Weise gegenüber der Drehtellung D für doppeltwirkende Verbraucher um 45° im Uhrzeigersinn gedreht, so daß der axiale Schlitz 8A und die beiden axialen Schlitze 10A die dem Schlitz 8B und den axialen Schlitzen 10B entsprechenden, oben beschriebenen Funktionen übernehmen. Der Verbraucheranschluß B ist hierbei natürlich ebenfalls durch einen Stopfen verschlossen.If the proportional directional control valve is in a rotary position EA, cf. Fig. 6, for a single-acting consumer to be brought to consumer port A, the valve piston 2 is rotated in the manner described above relative to the rotary position D for double-acting consumers by 45 ° clockwise, so that the axial slot 8A and the two axial slots 10A perform the functions described above for slot 8B and axial slots 10B. The consumer connection B is of course also closed by a plug.

Für verschiedene Anwendungen werden in der Praxis Rasten gefordert, die den Ventilkolben 2 in vorgegebenen Endstellungen mechanism festhalten. Die Lösung dieser Rastung erfolgt durch Handkraft. Bisher ist bei den bekannten Proportionalwegeventilen für jede Rastart ein anderer Rastkörper erforderlich. Dies erfordert eine nur durch geschultes Personal durchzuführende aufwendige Umrüstung.In practice, detents are required for various applications, which hold the valve piston 2 in the predetermined end positions mechanism. This detent is released by hand. So far there is a different rest for the known proportional directional control valves for each type of rest body required. This requires extensive retrofitting that can only be carried out by trained personnel.

In Fig. 10 sind verschiedene Rastarten 1 bis 7 tabellarisch und symbolisch dargestellt, wobei die Rückstellung des Ventilkolbens 2 von den nicht gerasteten Endstellungen A, B in die mittige Neutralstellung 0 mit Hilfe der Feder 33 des Ventilkolbens 2 erfolgt. Die Endstellung B entspricht der rechten axialen Endstellung, die Endstellung A entspricht der linken axialen Endstellung, und die Endstellung S entspricht der linken extremen axialen Schwimmstellung des Ventil- kolbens 2.In Fig. 10 different types of detents 1 to 7 are shown in tabular and symbolic form, the return of the valve piston 2 from the non-locked end positions A, B to the central neutral position 0 using the spring 33 of the valve piston 2. The end position B corresponds to the right axial end position, the end position A corresponds to the left axial end position, and the end position S corresponds to the left extreme axial floating position of the valve piston 2.

Bei einem mechanisch mittels eines Handhebels 28 betätigbaren Ventilkolbens 2, dargestellt in Fig. 7, kann die Veränderung der Rastart dadurch erfolgen, daß im Gehäuse 34 eingeschraubte Rastbolzen 31, 32 herausgeschraubt und durch Unterlegscheiben unwirksam gemacht werden. Die Rastbolzen 31, 32 können mit einer Rastkugel 29 in Eingriff gebracht werden, die am Ende des Hebels 28 angeordnet und mittels einer Feder 30 vorgespannt ist. Durch Verschwenken des Hebels 28 können die drei verschiedenen Endstellungen, nämlich Stellung B (Rastbolzen 32), Stellung A (Rastbolzen 31) und Stellung S (kein Rastbolzen gezeigt) verwirklicht werden.In the case of a valve piston 2 which can be actuated mechanically by means of a hand lever 28, shown in FIG. 7, the type of detent can be changed by unscrewing detent bolts 31, 32 screwed into the housing 34 and rendering them ineffective by means of washers. The locking bolts 31, 32 can be brought into engagement with a locking ball 29, which is arranged at the end of the lever 28 and is biased by a spring 30. By pivoting the lever 28, the three different end positions, namely position B (locking pin 32), position A (locking pin 31) and position S (no locking pin shown) can be achieved.

Ähnlich der Veränderung der Ventilfunktion des neuen Proportionalwegeventils durch Drehung des Ventilkolbens kann die Veränderung der Rastart auch durch ein drehbares Rastierungssystem erfolgen, wie es in den Fig. 8, 8a und 8b darstellt ist. Bei diesem Rastrierungsystem sind an einer für die Betätigung des Rastrierungssystem geeigneten Stelle des Proportionalwegeventils bzw. des Ventilkolbens 2 in diesem Ventilkolben verschiedene Nuten für die in Fig. 10 angeführten Rastarten 1 bis 7 eingeformt. Hierbei ist eine radiale Nut 35 für die Raststellung S, eine radiale Nut 36 für die Raststellung A und eine radiale Nut 37 für die Raststellung B vorgesehen. In diese Nuten rastet bei entsprechender Raststellung jeweils mindestens eine Kugel 38 (in Fig. 8 und 8b sind zwei Kugeln 38 dargestellt) ein, die jeweils mittels eines Klemmstückes 39 und einer Feder 40, die in einer axialen Nut 41 in einem Ring 42 angeordnet sind, vorgespannt ist. Der Ring 42 und das Klemmstück 39 sind mittels eines Stiftes 47 gegen Verdrehung geschichert. Die Einstellung der Rastarten 1 bis 7 gemäß Fig. 10 erfolgt durch Drehen des Ringes 42, wie dies in Fig. 8b durch den Doppelpfeil angeduetet ist. Die Raststellungen A, B oder S werden durch axiales Verschieben des Ringes 42 eingestellt. Ist bei einer bestimmten Rastart keine Raststellung eingestellt, so läuft die Kugel 38 bei axialer Verschiebung ds Ventilkolbens 2 mit Hilfe der Feder 33 von den entsprechenden Endstellungen A und B zur Neutralstellung 0 auf axialen Pfannen 43, 44 bzw. 45 für die Rastarten 1 und 6, 2 und 7 bzw. 3. Bei der Rastart 4 und 5 ist die Kugel 38 hierbei in einer radialen Nut 46 federzentriert.Similar to the change in the valve function of the new proportional directional control valve by rotating the valve piston, the change in the type of detent can also be carried out by a rotatable detent system, as shown in FIGS. 8, 8a and 8b. In this locking system, various grooves for the locking types 1 to 7 shown in FIG. 10 are formed in this valve piston at a point on the proportional directional control valve or the valve piston 2 which is suitable for actuating the locking system. Here, a radial groove 35 is provided for the locking position S, a radial groove 36 for the locking position A and a radial groove 37 for the locking position B. With a corresponding locking position, at least one ball 38 (two balls 38 are shown in FIGS. 8 and 8b) latches into these grooves, each by means of a clamping piece 39 and a spring 40, which are arranged in an axial groove 41 in a ring 42 , is biased. The ring 42 and the clamping piece 39 are secured against rotation by means of a pin 47. The locking types 1 to 7 according to FIG. 10 are set by rotating the ring 42, as indicated by the double arrow in FIG. 8b. The locking positions A, B or S are set by axially displacing the ring 42. If no detent position is set for a certain type of detent, the ball 38 runs with axial displacement of the valve piston 2 with the aid of the spring 33 from the corresponding end positions A and B to the neutral position 0 on axial pans 43, 44 and 45 for the detent types 1 and 6 , 2 and 7 and 3. In the detent types 4 and 5, the ball 38 is spring-centered in a radial groove 46.

In Fig. 8b ist der Ventilkolben 2 nur schematisch ohne die Nuten und Pfannen bezüglich der verschiedenen Drehstellungen für die Rastarten 1 und 6, 2 und 7, 3, 4 und 5 dargestellt.In Fig. 8b, the valve piston 2 is shown only schematically without the grooves and pans with respect to the different rotational positions for the detent types 1 and 6, 2 and 7, 3, 4 and 5.

In Fig. 9 ist eine abgewandelte Ausführungsform des vorhergehenden Rastrierungssystems dargestellt, wobei die Nuten und Pfannen in einer Rasthülse 48 eingeformt sind, welche mittels einer Stiftschraube 49 mit dem Ventilkolben 2 in der Drehstellung für die gewünschte Rastart verbunden wird.FIG. 9 shows a modified embodiment of the previous locking system, the grooves and pans being formed in a locking sleeve 48 which is connected to the valve piston 2 in the rotational position for the desired locking type by means of a stud screw 49.

Claims (22)

1. A proportional directional control valve whose valve housing has a pressure port (P), a tank port (T) and two load ports (A, B), wherein there are provided a valve spool (2) for controlling the communication of said ports (P, T, A, B) in two working positions and a separate pressure balance means (3) for controlling the pressure port (P) in dependence on load pressure, characterised in that the valve spool (2) has the following control conduit systems (5, 10) in three different rotational positions which are fixed in the valve housing (1) by positive connection, about its longitudinal axis:
a) in a first rotational position (D) in both working positions of the valve spool (2) the load pressure (PA, PB) of the pressurized load port (A, B) of a double-acting load is fed to the separate pressure balance means (3);
b) in a second rotational position (EB) in one working position of the valve spool (2) the load pressure of the pressurised load port (B) of a single-acting load is supplied to the separate pressure balance means (3) while in the other working position of the valve spool (2) the load port (A) which is not required and which is therefore closed, like also the separate pressure balance means (3), are relieved towards the tank (T); and
c) in a third rotational position (EA) control is effected as in b) but with interchange of the load ports (A, B).
2. A proportional directional control valve according to Claim 1 characterised in that the valve spool (2) has at least one axial slot (8A, 8B) by way of which a spring chamber (13.1) of the separate pressure balance means (3) can be communicated with the tank (T) when the valve spool is set for a single-acting load by way of a control conduit system (5) in the valve spool.
3. A proportional directional control valve according to Claim 2 characterised in that the valve spool (2) has two axial slots (8A, 8B) which extend in opposite directions in relation to the control conduit system (5) in the valve spool and which are arranged in circumferentially displaced relationship with each other.
4. A proportional directional control valve according to Claim 3 characterised in that the axial slots (8A, 8B) are arranged displaced relative to each other through 90° in the circumferential direction of the valve spool (2).
5. A proportional directional control valve according to at least one of Claims 2 to 4 characterised in that the control conduit system (5) in the valve spool (2) can be communicated with the load ports (A, B) by way of load feedback bores (7, 7.1, 7.2) in the valve spool and that the radial load feedback bores (7.1, 7.2) completely overlap with control grooves (9) in the valve spool.
6. A proportional directional control valve according to Claim 5, characterised in that the load feedback bores (7, 7.1, 7.2) are communicated with the first control conduit system (5) by way of a throttle (6).
7. A proportional directional control valve according to at least one of Claims 2 to 6 characterised in that the control conduit system (5) comprises an inner axial bore (5.1), a part-annular duct (5.2) which communicates therewith, a radial bore (5.3) communicating with said bore (5.1) and a part-annular duct (5.4) which is axially increased in width and which communicates with the radial bore and which communicates the control conduit system with the spring chamber (13.1) of the separate pressure balance means (3) in any position of the valve spool (2).
8. A proportional directional control valve according to at least one of Claims 1 to 7 characterised by a pilot-controlled pressure limiting valve (4A, 4B) for load pressure safeguarding purposes with integrated after-suction.
9. A proportional directional control valve according to Claim 8 characterised in that the after-suction is effected by way of a differential surface area at the main spool (4.1) of the pressure limiting valve (4A, 4B).
10. A proportional directional control valve according to at least one of Claims 1 to 9 characterised in that there is provided a stroke limiting means (24) for the valve spool (2) and that the valve spool can be brought into a float position by removal of the stroke limiting means.
11. A proportional directional control valve according to Claim 10 characterised in that a spring chamber (4.3) of a pressure limiting valve (4A, 4B) can be communicated with the control conduit system (5) by way of a relief conduit (19) in the float position of the valve spool (2)..
12. A proportional directional control valve according to Claim 11 characterised in that a check valve (20) is provided in the relief conduit (19).
13. A proportional directional control valve according to at least one of Claims 1 to 12 characterised in that a spool chamber (12.1) of the separate pressure balance means (3) is communicated with a spring chamber (13.1) of the pressure balance means (3) by way of a throttle (14).
14. A proportional directional control valve according to at least one of Claims 1 to 13 characterised in that the spring chamber (13.1) of the separate pressure balance means (3) can be communicated by way of a check valve (15) with a load feedback conduit (16) to an input plate (25) with an input pressure balance means (26) of a constant pump or to a delivery flow regulator of an adjustable pump.
15. A proportional directional control valve according to at least one of Claims 1 to 14 characterised in that provided in the valve spool (2) is a further control conduit system (10) by way of which the valve can be communicated by way of a relief conduit (11) with an input plate (25) with an input pressure balance means (26) of a constant pump or a delivery flow regulator of an adjustable pump.
16. A proportional directional control valve according to Claim 15 characterised in that the further control conduit system (10) comprises a first annular duct (10.1), two first axial slots (10A) which communicate with the first annular duct and which extend in the same direction in relation to the first annular duct and which are arranged in displaced relationship with each other through 180°C in the circumferential direction of the valve spool, two second axial slots (10B) which communicate with the first annular duct and which extend in the opposite direction in relation in the first axial slots, in relation to the first annular duct, and are arranged in displaced relationship with each other through 180° in the circumferential direction of the valve spool, wherein the two first axial slots (10A) are arranged in displaced relationship with the two second axial slots (10B) in the circumferential direction of the valve spool, and a second annular duct (10.2), wherein the spacing between the first and second annular ducts corresponds to the adjusting travel of the valve spool between a central neutral position and a float position.
17. A proportional directional control valve according to Claim 16 characterised in that the two first axial slots (10A) are arranged in displaced relationship with each other through 90° relative to the two second axial slots (10B) in the circumferential direction of the valve spool (2).
18. A proportional directional control valve according to Claim 16, or Claim 17 characterised in that the axial slots (8A, 10A, 8B, 10B), which extend in the same direction, of the control conduit system (5) and the further control conduit system (10), are arranged in displaced relationship with each other through 90° in the circumferential direction of the valve spool (2).
19. A proportional directional control valve according to at least one of Claims 1 to 18 characterised in that the valve spool (2) can be rotationally fixed by positive connection between corresponding portions at one of its ends and a removable cover cap (23).
20. A proportional directional control valve according to at least one of Claims 1 to 19 characterised by a rotatable retaining system (35 to 47) for retention of the valve spool (2) in predetermined end positions (A, B, S).
21. A proportional directional control valve according to at least one of Claims 1 to 19 characterised in that the valve spool (2) is actu- able by means of a hand lever (28) and arranged at the end of the hand lever is a spring-biased retaining wall (29) which can be brought into engagement with adjustable retaining pins (31, 32) for retention of the valve spool in predetermined end positions (A, B).
22. A valve system having at least two proportional directional control valves according to at least one of Claims 1 to 21 in a modular construction characterised in that the individual proportional directional control valves are connected in series by way of a load feedback conduit (16) according to Claim 14 and a relief conduit (11) according to Claim 15.
EP86116954A 1985-12-06 1986-12-05 Proportional directional valve with single pressure balance Expired - Lifetime EP0224936B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3543231 1985-12-06
DE19853543231 DE3543231A1 (en) 1985-12-06 1985-12-06 PROPORTIONAL-WAY VALVE WITH SINGLE PRESSURE SCALE

Publications (3)

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EP0224936A2 EP0224936A2 (en) 1987-06-10
EP0224936A3 EP0224936A3 (en) 1988-11-09
EP0224936B1 true EP0224936B1 (en) 1990-06-06

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EP86116954A Expired - Lifetime EP0224936B1 (en) 1985-12-06 1986-12-05 Proportional directional valve with single pressure balance

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DE (2) DE3543231A1 (en)

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US4958553A (en) * 1988-04-22 1990-09-25 Diesel Kiki Co., Ltd. Hydraulic controller
DE3921445A1 (en) * 1989-06-30 1991-01-03 Bosch Gmbh Robert HYDRAULIC CONTROL DEVICE
DE4013504A1 (en) * 1990-04-23 1991-10-24 Knapp Mikrohydraulik Gmbh Hydraulic fluid-proportioning valve - has rotary plate with control groove curving round axis of rotation
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
DE102007048324A1 (en) * 2007-10-09 2009-04-16 Volkswagen Ag Valve device for hydraulic speed selector system of motor vehicle has housing for valve spool formed as bore providing precision fit for spool, wherein valve block is produced as cast part
CN108869431B (en) * 2018-09-21 2019-11-26 浙江达柏林阀门有限公司 A kind of hydraulic control balanced valve more adjustable than ratio
CN110319067B (en) * 2019-08-05 2024-03-22 安徽理工大学 Dual-motor-based proportional flow control and high-speed switch dual-purpose valve

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Also Published As

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DE3543231C2 (en) 1990-08-30
EP0224936A2 (en) 1987-06-10
EP0224936A3 (en) 1988-11-09
DE3671784D1 (en) 1990-07-12
DE3543231A1 (en) 1987-06-11

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