EP1386084B1 - Dispositif de commande hydraulique destine a la commande de la direction et de la vitesse d'un consommateur hydraulique a action simple et distributeur correspondant - Google Patents

Dispositif de commande hydraulique destine a la commande de la direction et de la vitesse d'un consommateur hydraulique a action simple et distributeur correspondant Download PDF

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Publication number
EP1386084B1
EP1386084B1 EP02742885A EP02742885A EP1386084B1 EP 1386084 B1 EP1386084 B1 EP 1386084B1 EP 02742885 A EP02742885 A EP 02742885A EP 02742885 A EP02742885 A EP 02742885A EP 1386084 B1 EP1386084 B1 EP 1386084B1
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European Patent Office
Prior art keywords
chamber
control
consumer
spool
pressure
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Expired - Lifetime
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EP02742885A
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German (de)
English (en)
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EP1386084A2 (fr
Inventor
Peter BÜTTNER
Tatu Miikkulainen
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Bosch Rexroth AG
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Bosch Rexroth AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F15B13/0418—Load sensing elements sliding within a hollow main valve spool
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
    • F15B2013/006—Modular components with multiple uses, e.g. kits for either normally-open or normally-closed valves, interchangeable or reprogrammable manifolds

Definitions

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

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Mechanically-Actuated Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Servomotors (AREA)
  • Non-Deflectable Wheels, Steering Of Trailers, Or Other Steering (AREA)

Claims (9)

  1. Un dispositif de commande hydraulique pour la commande d'un récepteur hydraulique à simple effet, en particulier d'un vérin (12) hydraulique à simple effet, en termes de sens et de vitesse,
    doté d'un distributeur (20) présentant un corps (30) de valve et dans celui-ci un alésage (31) de tiroir doté d'une chambre (35) d'alimentation médiane, qui peut être alimentée en fluide de pression à partir d'une source (10) de fluide de pression, doté de deux chambres (38, 39) de récepteur avoisinantes et d'une chambre (44) d'évacuation, qui permet d'évacuer du fluide de pression vers un réservoir (14),
    présentant un tiroir (32) de commande, qui est disposé dans l'alésage (31) de tiroir, qui peut coulisser dans la direction axiale, hors d'une position médiane, dans un premier sens et dans un second sens opposé au premier sous l'effet d'une force de commande, donnée par une consigne pouvant varier, et qui présente de premières rainures (60) de commande commandant l'ouverture d'une connexion entre la chambre (35) d'alimentation et une première chambre (38) de récepteur, lors d'un déplacement hors de la position médiane dans un premier sens, et de secondes rainures (61) de commande commandant l'ouverture de la connexion entre la première chambre (38) de récepteur et la chambre (44) d'évacuation, lors d'un déplacement hors de la position médiane dans le second sens, et
    présentant un tiroir (82) de mesure agissant de concert avec le tiroir (32) de commande de façon telle que, dans le sens opposé à la force de commande et lors d'un déplacement du tiroir (32) de commande dans le second sens, une force de compensation peut être exercée sur le tiroir (32) de commande en appliquant une pression sur le tiroir (82) de mesure,
    caractérisé en ce que le tiroir (82) de mesure puisse être soumis à la pression régnant dans la première chambre (38) de récepteur lors d'un déplacement du tiroir (32) de commande dans le second sens.
  2. Un dispositif de commande hydraulique selon la revendication n° 1, caractérisé en ce qu'une chambre (74) de pression limitrophe à une surface de mesure du tiroir (82) de mesure puisse être raccordée par voie fluide à la seconde chambre (39) de récepteur et cette dernière soit constamment raccordée par voie fluide à la première chambre (38) de récepteur.
  3. Un dispositif de commande hydraulique selon la revendication n° 2, caractérisé en ce que la connexion par voie fluide entre la première chambre (38) de récepteur et la seconde chambre (39) de récepteur soit établie entièrement à l'intérieur du corps (30) de valve.
  4. Un dispositif de commande hydraulique selon la revendication n° 3, caractérisé en ce qu'à l'intérieur du corps (30) de valve, deux canaux (40, 41) de récepteur partant des deux chambres (38, 39) de récepteur soient orientés essentiellement dans la direction perpendiculaire à l'alésage (31) de tiroir et l'un parallèle à l'autre jusqu'à deux zones (42, 43) de raccordement du corps (30) de valve et que les canaux (40, 41) de récepteur soient raccordés l'un à l'autre par un canal (90) de raccordement orienté essentiellement dans une direction parallèle à l'alésage (31) de tiroir.
  5. Un dispositif de commande hydraulique selon la revendication n° 3 ou n° 4, caractérisé en ce que le corps (30) de valve présente un évidement (91) pour un limiteur (92) de pression secondaire et que le canal (90) de raccordement soit accessible à un outil de forage en passant au travers de l'évidement (91).
  6. Un dispositif de commande hydraulique selon une revendication précédente, caractérisé en ce que dans le tiroir (32) de commande soit disposé un alésage (74) axial, servant à la signalisation de la pression en charge du récepteur (12) hydraulique, qui lors d'un déplacement du tiroir (32) de commande dans le premier sens est ouvert sur la première chambre (38) de récepteur par un premier alésage (75) transversal et qui lors d'un déplacement du tiroir (32) de commande dans le second sens est ouvert sur la seconde chambre (39) de récepteur par un deuxième alésage (76) transversal, que la pression de l'alésage (74) axial puisse être transmise à une chambre (64) de signalisation de charge par un troisième alésage (77) transversal lors d'un déplacement du tiroir (32) de commande dans le premier sens et que le tiroir (82) de mesure soit guidé à l'intérieur du tiroir (32) de commande et soit soumis, à l'intérieur du tiroir (32) de commande, à la pression régnant dans l'alésage (74) axial et puisse s'appuyer, à l'extérieur, contre une butée (49) du corps (30) de valve.
  7. Un dispositif de commande hydraulique selon la revendication n° 6, caractérisé en ce que l'alésage (74) axial puisse être isolé de la chambre (64) de signalisation de charge, lors d'un déplacement du tiroir (32) de commande dans le second sens.
  8. Un dispositif de commande hydraulique selon la revendication n° 7, caractérisé en ce que le tiroir (32) de commande présente un premier épaulement (58) de tiroir, doté de premières rainures (60) de commande et de secondes rainures (61) de commande et situé dans la zone de la première chambre (38) de récepteur, une première rainure annulaire, succédant au premier épaulement (58) de tiroir et située dans la zone de la chambre (44) d'évacuation, un épaulement (71) de tiroir supplémentaire, succédant à celle-ci, et une rainure (69) annulaire supplémentaire, succédant à celui-ci et où débouche le troisième alésage (77) transversal, qu'une chambre (63) annulaire, isolée de la chambre (44) d'évacuation par une entretoise de corps, fasse le tour de l'alésage (31) de tiroir, présente une largeur supérieure à la largeur efficace de l'épaulement (71) de tiroir supplémentaire et soit suivie, après une autre entretoise de corps, par la chambre (64) de signalisation de charge, que l'épaulement (71) de tiroir supplémentaire et la chambre (63) annulaire soient disposés l'un par rapport à l'autre de façon telle, que la rainure (69) annulaire supplémentaire est ouverte sur la chambre (44) d'évacuation par la chambre (63) annulaire dans la position médiane du tiroir (32) de commande et est isolée de la chambre (44) d'évacuation par l'épaulement (71) de tiroir supplémentaire après une faible course du tiroir (32) de commande hors de la position médiane et que la largeur de la rainure (69) annulaire supplémentaire ne suffise que pour que l'entretoise de corps supplémentaire isole la rainure (69) annulaire supplémentaire de la chambre (64) de signalisation de charge lors d'un déplacement du tiroir (32) de commande dans le second sens.
  9. Un distributeur (20), présentant un corps (30) de valve et là-dedans un alésage (31) de tiroir doté d'une chambre (3 5) d'alimentation médiane, qui peut être alimentée en fluide de pression à partir d'une source (10) de fluide de pression, doté de deux chambres (38, 39) de récepteur avoisinantes et d'une chambre (44) d'évacuation, qui permet d'évacuer du fluide de pression vers un réservoir (14),
    présentant un tiroir (32) de commande, qui est disposé dans l'alésage (31) de tiroir, qui peut coulisser dans la direction axiale, hors d'une position médiane, dans un premier sens et dans un second sens opposé au premier sous l'effet d'une force de commande, donnée par une consigne pouvant varier, et qui est doté de premières rainures (60) de commande commandant l'ouverture d'une connexion entre la chambre (35) d'alimentation et une première chambre (38) de récepteur, lors d'un déplacement hors de la position médiane dans un premier sens, et de secondes rainures(61) de commande commandant l'ouverture de la connexion entre la première chambre (38) de récepteur et la chambre (44) d'évacuation, lors d'un déplacement hors de la position médiane dans le second sens, et
    présentant un tiroir (82) de mesure agissant de concert avec le tiroir (32) de commande de façon telle que, dans le sens opposé à la force de commande et lors d'un déplacement du tiroir (32) de commande dans le second sens, une force de compensation peut être exercée sur le tiroir (32) de commande en appliquant une pression sur le tiroir (82) de mesure,
    caractérisé en ce que le tiroir (82) de mesure puisse être soumis à la pression régnant dans la première chambre (38) de récepteur lors d'un déplacement du tiroir (32) de commande dans le second sens,
    qu'une chambre (74) de pression limitrophe à une surface de mesure du tiroir (82) de mesure puisse être raccordée par voie fluide à la seconde chambre (39) de récepteur et cette dernière soit constamment raccordée par voie fluide à la première chambre (38) de récepteur et
    que la connexion par voie fluide entre la première chambre (38) de récepteur et la seconde chambre (39) de récepteur soit établie entièrement à l'intérieur du corps (30) de valve.
EP02742885A 2001-05-05 2002-04-11 Dispositif de commande hydraulique destine a la commande de la direction et de la vitesse d'un consommateur hydraulique a action simple et distributeur correspondant Expired - Lifetime EP1386084B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10121924 2001-05-05
DE10121924A DE10121924A1 (de) 2001-05-05 2001-05-05 Hydraulische Steueranordnung zur Steuerung eines einfachwirkenden hydraulischen Verbrauchers hinsichtlich Richtung und Geschwindigkeit und Wegeventil dafür
PCT/EP2002/004022 WO2002090778A2 (fr) 2001-05-05 2002-04-11 Dispositif de commande hydraulique destine a la commande de la direction et de la vitesse d'un consommateur hydraulique a action simple et distributeur correspondant

Publications (2)

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

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EP02742885A Expired - Lifetime EP1386084B1 (fr) 2001-05-05 2002-04-11 Dispositif de commande hydraulique destine a la commande de la direction et de la vitesse d'un consommateur hydraulique a action simple et distributeur correspondant

Country Status (5)

Country Link
EP (1) EP1386084B1 (fr)
AT (1) ATE315728T1 (fr)
DE (2) DE10121924A1 (fr)
DK (1) DK1386084T3 (fr)
WO (1) WO2002090778A2 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2311686A1 (fr) * 2009-10-15 2011-04-20 Hyva International B.V. Valve pour système de basculement
FI20115108L (fi) 2011-02-03 2012-08-04 Parker Hannifin Mfg Finland Oy Painesäädöllä varustettu suuntaventtiili
DE102011120302A1 (de) * 2011-12-03 2013-06-06 Robert Bosch Gmbh Hydraulisches Wegeventil für das Hubwerk eines landwirtschaftlichen Fahrzeugs
DE102013017093A1 (de) * 2013-10-15 2015-04-16 Hydac Filtertechnik Gmbh Steuervorrichtung
CN105570220B (zh) 2014-10-17 2017-08-11 徐工集团工程机械股份有限公司 多路阀及液压流量共享系统

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DE19631803B4 (de) * 1996-08-07 2007-08-02 Bosch Rexroth Aktiengesellschaft Hydraulische Steuervorrichtung

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DK1386084T3 (da) 2006-05-22
WO2002090778A3 (fr) 2003-02-20
EP1386084A2 (fr) 2004-02-04
DE10121924A1 (de) 2002-11-07
WO2002090778A2 (fr) 2002-11-14

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