EP0500419B1 - Proportionales Wegeventil und Steuersystem für mehrere hydraulische Verbrauchen, wobei jeder solch ein Ventil beinhaltet - Google Patents

Proportionales Wegeventil und Steuersystem für mehrere hydraulische Verbrauchen, wobei jeder solch ein Ventil beinhaltet Download PDF

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Publication number
EP0500419B1
EP0500419B1 EP92400358A EP92400358A EP0500419B1 EP 0500419 B1 EP0500419 B1 EP 0500419B1 EP 92400358 A EP92400358 A EP 92400358A EP 92400358 A EP92400358 A EP 92400358A EP 0500419 B1 EP0500419 B1 EP 0500419B1
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EP
European Patent Office
Prior art keywords
slide valve
pressure
compensator slide
compensator
piston
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Expired - Lifetime
Application number
EP92400358A
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English (en)
French (fr)
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EP0500419A1 (de
Inventor
Louis Marcon
André Rousset
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Marrel SA
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Marrel SA
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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
    • F15B13/0416—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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5159—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders

Definitions

  • the invention relates to proportional hydraulic distributors.
  • distributors are devices that are available between a flow generation and a receiver to control the operation of the receiver by adapting the way it is connected to the flow generation.
  • Proportional type distributors include not only a controlled drawer whose position determines the section of a constriction, but also an automatic compensating drawer to maintain constant the pressure difference between the upstream and downstream of this constriction, so that at a given position of the controlled slide corresponds to a given flow of fluid. Consequently, when a receiver is controlled with a proportional distributor, its operating speed is fixed by the position of the controlled drawer, independently of the load that the receiver supports.
  • the circuit includes load detection means called "load-sensing" which bring the pressure of the most loaded receiver towards the generation of flow. , to which pressure responds the generation of flow by producing an operating pressure equal to the load-sensing pressure plus a constant; and secondly, where the distributor has a compensating drawer which automatically takes a position where it produces upstream of the throttle of the controlled drawer a second throttling of appropriate section, the compensating drawer comprising two opposite active surfaces, a first surface subjected to pressure upstream of the first throttle to urge the drawer in the direction of closing, and a second surface subjected to pressure downstream of the first throttle to urge the compensating drawer in the direction of opening.
  • load detection means called "load-sensing" which bring the pressure of the most loaded receiver towards the generation of flow.
  • pressure responds the generation of flow by producing an operating pressure equal to the load-sensing pressure plus a constant
  • the distributor has a compensating drawer which automatically takes a position where it produces upstream of the throttle of the controlled drawer a second
  • the invention proposes that said additional means are provided so that the compensating drawer is further urged in the closing direction by a substantially constant force, said first and second active surfaces of the compensating drawer , and said complementary means being dimensioned so that in service the pressure difference between the upstream and downstream of the first throttle, depends on the difference between the service and load-sensing pressures, according to a linear function with strictly coefficient positive and strictly negative constant.
  • the receivers each slow down in the event of excessive demand for flow, the speed ratios between the receivers each being preserved.
  • proportional distributors according to the invention are therefore particularly advantageous from the safety point of view, for example in public works vehicles where they make it possible to completely avoid the risk of accident in the event of excessive demand for flow, since the various cylinders can no longer escape the driver's control as before.
  • said first and second active surfaces of the compensating slide have a similar dimensioning
  • said first active surfaces of the first and second pistons have a similar dimensioning
  • said second active surfaces of the first and second pistons have a similar dimensioning
  • each distributor has a compensating drawer operating according to the same linear function.
  • At least one of the distributors has a compensating drawer operating according to a different linear function.
  • the distributor 70 illustrated in FIG. 1 is similar to that described in French patent FR-B-2,562,632, with the exception of its pressure compensating device.
  • stator block 1 in the bore 2 of which slides a cylindrical controlled drawer 3.
  • switching of the hydraulic circuits is effected by displacement of the grooves of the drawer 3 in front of the lights of the stator.
  • the drawer 3 is provided with a spring return device of known type, comprising a helical spring 4, compressed between the shoulders 5 and 6 of two rings 7 and 8, trapped between two shoulders of the end 9 of the drawer 3, around which they can slide.
  • a spring return device of known type, comprising a helical spring 4, compressed between the shoulders 5 and 6 of two rings 7 and 8, trapped between two shoulders of the end 9 of the drawer 3, around which they can slide.
  • the drawer 3 is spontaneously returned to a neutral rest position, while it is pushed to the right (FIG. 1) when a pilot pressure is sent into an opening 10 of the fixed cap 61.
  • a pilot pressure is sent opposite, in an opening 11 of the cap 62 at its other end.
  • the three-position slide 3 is used to control a double-acting hydraulic cylinder 12.
  • one of the sections of the cylinder 12 is connected to a first channel use 13 of the stator 1, while the opposite section of the jack 12 is connected to a second use pipe 14 of the stator 1.
  • the distributor receives in an annular chamber 15, the pressure sent by a generation of flow 71.
  • the supply chamber 15 surrounds a cylindrical compensating slide 16 provided with a radial bore 22, communicating with a blind axial bore 23.
  • the latter opens onto a seat capable of being closed off or unmasked by a ball 24 whose return spring 25 is compressed inside the compensating drawer 16.
  • the chamber containing the ball 24 and the spring 25 opens through a lateral opening 26 in an annular chamber 27 surrounding the central part of the controlled drawer 3.
  • the controlled slide 3 has an axial internal housing, 28 on the left, 29 on the right.
  • the housing 28 communicates with the outside of the drawer by two radial bores referenced respectively 30 and 31. Likewise, the housing 29 opens onto two radial bores 32 and 33.
  • the bore 30 faces a solid part 34 of the stator which closes it, between two annular chambers 35 and 36.
  • the chamber 35 communicates with the first use pipe 13, while the chamber 36 is connected to the return circuit.
  • the bore 32 is closed at rest, by a solid part 37, located between two annular chambers 38 and 39.
  • the chamber 38 communicates with the second use pipe 14, while the chamber 39 is connected to the return circuit .
  • the stator defines, in the bore, a solid part 40, in front of which is capable of moving a groove 41 of the drawer 3.
  • annular stator chamber 42 Around the drawer 3, in the zone situated around the bore 31 when the drawer 3 is pushed to the right (FIG. 1), there is an annular stator chamber 42.
  • the drawer 3 has a groove 43 movable in front of a solid part 44 of the stator.
  • a solid part 44 of the stator Around passage 33 when drawer 3 is pushed to the left, there is an annular stator chamber 45.
  • the two chambers 42 and 45 are connected by a pipe 46 called the load sensing pipe.
  • a first booster valve 52 is mounted in parallel on the first use pipe 13.
  • a booster valve 53 is mounted in parallel on the second user pipe 14. Behind the valves 52 and 53, is finds a chamber 54 connected to the oil return circuit.
  • a pressure relief valve, respectively 55 and 56, is provided on the side of each of the use pipes 13, 14, which can thus flow into the return chambers, respectively 36, 39.
  • the chambers 27, 35 and 38 are closed, so that the jack 12 is immobilized while no flow passes through the distributor.
  • the pipe 46 communicates through the grooves 41 and 43 respectively with the chamber 36 and the chamber 39, that is to say that it is connected to the return circuit.
  • the slide 3 slides to the right with an amplitude determined by the value of the pilot pressure, which is balanced with the opposing thrust of the spring 4, more or less compressed.
  • the supply pressure of the chamber 27 is sent into the line 13 through the groove 49 and the chamber 35, while the line 14 communicates with the return chamber 39 through the groove 51.
  • Each of the grooves 49 and 51 determines a constriction whose cross section is determined by the position of the drawer 3.
  • the pipe 46 communicates on the left with the pipe 13 through the passages 31, 28 and 30, while on the right it is closed. The pressure downstream of the throttle provided by the groove 49 is thus transmitted to the pipe 46.
  • the slide 3 slides to the left to a position determined by the amplitude of the pilot pressure.
  • the supply pressure of the chamber 27 is sent into the line 14 passing through the groove 50 and the chamber 38, while the line 13 communicates with the return chamber 36 through the groove 48.
  • Each of the grooves 48 and 50 determines a constriction, the section of which is determined by the position of the drawer 3.
  • the pipe 46 communicates on the right with the pipe 14 by the holes 33, 29 and 32, while on the left it is closed. The pressure downstream of the throttle provided by the groove 50 is thus transmitted to the pipe 46.
  • the circuit selector 99 (also called OR function) has one of its inputs which communicates with the pipe 46 by a channel 72, and its other input which communicates with a channel 73 connected to the output pipe of the circuit selector d '' a similar distributor.
  • the pressure in the line 46 is the highest, so that the circuit selector 99 adopts the illustrated position where it transmits by its output to the line 74 the operating pressure of the cylinder 12, which is the pressure of highest use of all receivers that feeds the flow generation 71. More generally, as is clearly seen in FIG. 2, it is always the pressure of the most loaded receiver which is applied to the pipe 74, this pressure known as load sensing being transmitted to the generation of flow 71 which produces a working pressure normally equal to the load sensing pressure plus a constant.
  • the compensating slide 16 also called a balance, is movable in a bore 80 of the stator 1 and has around the channel 22 a groove 81 which produces, depending on the position of the slide, a more or less significant constriction upstream of the constriction provided by the drawer 3 on the supply line of the jack 12, according to the position taken by the drawer 16.
  • This comprises two opposite active surfaces, on the left a surface 82 subjected to the pressure upstream of the throttle provided by the slide 3, and on the right a surface 83 subjected to the pressure prevailing in the pipe 46, that is to say that is to say the operating pressure of the jack 12.
  • This slide 16 is biased on the left in the direction of closing the throttle that it produces, and on the right in the direction of opening.
  • each piston 84 or 85 comes into contact with the compensating slide by a stud, and slides in a cylinder, respectively 86 or 87, screwed into the stator 1 coaxially with the bore 80, each cylinder being open on the inside and closed on the side. outside, the cylinder 86 sealingly crossing the pipe 46.
  • the pistons 84 and 85 are similar and each have L-shaped passages which allow the chamber located between the piston and the bottom of the cylinder to communicate with the pipe 89 or 90, respectively.
  • Line 89 is connected to the load sensing line of the flow generation, so that it is brought to the load sensing pressure, while the pipe 90 is connected to the service line so that it is brought to the service pressure.
  • the pistons 84 and 85 each have two opposite active surfaces, one of which (91 for the cylinder 84 and 92 for the cylinder 85) is opposite the corresponding active surface of the drawer 16 (respectively 82 and 83), and subjected to the same pressure.
  • the second active surface 93 of the piston 84 is subjected to the load sensing pressure, and the second active surface 94 of the piston 85 is subjected to the operating pressure.
  • a spring 95 applies the piston 84 against the drawer 16.
  • the effective value of surfaces 82 and 83 is similar (denoted S1), the same is true for the effective value of surfaces 91 and 92 (denoted S2), and also the same for the effective value of surfaces 93 and 94 (denoted S3 ).
  • conduits 89 and and 90 pass through the entire distributor 70, so that the possibility remains of making all the connections between distributors, by simply joining these latter end-to-end.
  • FIG. 2 schematically shows the distributor 70 attached to a similar distributor 70 ', all the elements relating to the latter bearing the same reference as above but assigned an index premium.
  • the distributor furthest from the pump, here 70 ′ does not receive a circuit selector with an input connected to the reservoir, but has its channel 74 directly connected to the pipe 46.

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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)

Claims (9)

  1. Proportionales Wegeventil zur Steuerung eines hydraulischen Verbrauchers (12), der in geeigneter Weise mit einem Druckfluiderzeuger (71) in Verbindung zu bringen ist, welcher einen Betriebsdruck erzeugt, der normalerweise gleich einem dem Druckfluiderzeuger zugeleiteten, als Lastsignal bezeichneten Steuerdruck zuzüglich einer Konstanten ist, mit einem Steuerschieber (3), dessen Stellung den Querschnitt einer Drosselstelle bestimmt, einem Ausgleichsschieber (16) zur Regelung der Differenz der Drücke vor und hinter der Drosselstelle, der automatisch eine Stellung einnimmt, in der er vor der Drosselstelle eine zweite Drosselstelle mit geeignetem Querschnitt bildet, und zwei entgegengesetzte Kolbenflächen (82, 83) aufweist, deren erste (82) mit dem Druck vor der ersten Drosselstelle beaufschlagbar ist, um den Schieber (16) in Schließrichtung zu drängen, und deren zweite (83) mit dem Druck hinter der ersten Drosselstelle beaufschlagbar ist, um den Ausgleichsschieber in Öffnungsrichtung zu drängen, und mit zusätzlichen Mitteln, um den Ausgleichsschieber (16) außerdem durch den Druck des Lastsignals in Schließrichtung und durch den Betriebsdruck in Öffnungsrichtung zu drängen, dadurch gekennzeichnet, daß die zusätzlichen Mittel vorgesehen sind, um den Ausgleichsschieber durch eine im wesentlichen konstante Kraft in Schließrichtung zu drängen, wobei die erste und zweite Kolbenfläche (82, 83) des Ausgleichsschiebers und die zusätzlichen Mittel (84, 85, 95) so dimensioniert sind, daß im Betrieb die Differenz der Drücke vor und hinter der ersten Drosselstelle von der Differenz zwischen dem Betriebsdruck und dem Druck des Lastsignals abhängig ist gemäß einer linearen Funktion mit einem ausschließlich positiven Koeffizienten und einer ausschließlich negativen Konstanten.
  2. Wegeventil nach Anspruch 1, dadurch gekennzeichnet, daß zu den zusätzlichen Mitteln gehören:
    - auf jeder Seite des Ausgleichsschiebers (16) ein koaxial beweglicher Kolben (84, 85), der in Anlage an den Ausgleichsschieber kommt oder mit diesem verbunden ist und zwei entgegengesetzte Kolbenflächen hat, deren erste (91, 92) einer der Kolbenflächen (82, 83) des Ausgleichsschiebers gegenüberliegt und mit demselben Druck beaufschlagt ist, und deren zweite (93, 94) bei dem ersten Kolben (84), dessen erste Kolbenfläche (91) der ersten Kolbenfläche (82) des Ausgleichsschiebers gegenüberliegt, mit dem Lastsignal und bei dem zweiten Kolben (85), dessen erste Kolbenfläche (92) der zweiten Kolbenfläche (83) des Ausgleichsschiebers gegenüberliegt, mit dem Betriebsdruck beaufschlagbar ist; und
    - eine Feder (95), welche den ersten Kolben zum Ausgleichsschieber drängt.
  3. Wegeventil nach Anspruch 2, dadurch gekennzeichnet, daß die ersten und zweiten Kolbenflächen (82, 83) des Ausgleichsschiebers eine ähnliche Bemessung haben, die ersten Kolbenflächen (91, 92) des ersten und des zweiten Kolbens eine ähnliche Bemessung haben und die zweiten Kolbenflächen (93, 94) des ersten und des zweiten Kolbens eine ähnliche Bemessung haben.
  4. Wegeventil nach einem der Ansprüche 2 oder 3, dadurch gekennzeichnet, daß es einen Statorkörper (1) mit einer Bohrung (80) aufweist, in welcher der Ausgleichsschieber (16) bewegbar ist, und die ersten und zweiten Kolben (84, 85) in Zylindern (86, 87) bewegbar sind, die koaxial am Statorkörper angeordnet sind.
  5. Wegeventil nach Anspruch 4, dadurch gekennzeichnet, daß es Querbohrungen (89, 90) aufweist, die an die Leitung mit dem Lastsignal bzw. an die Leitung mit dem Betriebsdruck angeschlossen sind, während jeder Kolben (84, 85) mit einer Bohrung versehen ist, um den Druck des Lastsignals bzw. den Betriebsdruck in eine Kammer zu leiten, die sich zwischen dem Kolben (84, 85) und dem Boden des Zylinders (86, 87) befindet.
  6. Wegeventil nach einem der Ansprüche 2 bis 5, dadurch gekennzeichnet, daß der Kontakt zwischen den Kolben (84, 85) und dem Ausgleichsschieber (16) über Ansätze stattfindet.
  7. Steuervorrichtung für eine Mehrzahl hydraulischer Verbraucher, deren jeder ein Wegeventil nach einem oder mehreren der Ansprüche 1 bis 6 aufweist.
  8. Steuervorrichtung nach Anspruch 7, dadurch gekennzeichnet, daß jeder Ausgleichsschieber nach derselben linearen Funktion arbeitet.
  9. Steuervorrichtung nach Anspruch 7, dadurch gekennzeichnet, daß wenigstens eines der Wegeventile einen Ausgleichsschieber aufweist, der nach einer anderen linearen Funktion arbeitet.
EP92400358A 1991-02-15 1992-02-11 Proportionales Wegeventil und Steuersystem für mehrere hydraulische Verbrauchen, wobei jeder solch ein Ventil beinhaltet Expired - Lifetime EP0500419B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9101848A FR2672944A1 (fr) 1991-02-15 1991-02-15 Distributeur proportionnel et ensemble de commande d'une pluralite de recepteurs hydrauliques comportant pour chaque recepteur un tel distributeur.
FR9101848 1991-02-15

Publications (2)

Publication Number Publication Date
EP0500419A1 EP0500419A1 (de) 1992-08-26
EP0500419B1 true EP0500419B1 (de) 1995-11-22

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EP92400358A Expired - Lifetime EP0500419B1 (de) 1991-02-15 1992-02-11 Proportionales Wegeventil und Steuersystem für mehrere hydraulische Verbrauchen, wobei jeder solch ein Ventil beinhaltet

Country Status (5)

Country Link
US (1) US5222426A (de)
EP (1) EP0500419B1 (de)
JP (1) JPH04312202A (de)
DE (1) DE69206170T2 (de)
FR (1) FR2672944A1 (de)

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FR2694606B1 (fr) * 1992-08-04 1994-11-04 Bennes Marrel Ensemble de commande d'une pluralité de récepteurs hydrauliques.
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WO2019083961A1 (en) * 2017-10-27 2019-05-02 Tri Tool Inc. PIPE CHAMFINTING MACHINE SYSTEM
CN108869431B (zh) * 2018-09-21 2019-11-26 浙江达柏林阀门有限公司 一种液控比比例可调的平衡阀

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US4487018A (en) * 1982-03-11 1984-12-11 Caterpillar Tractor Co. Compensated fluid flow control
US4570672A (en) * 1983-06-13 1986-02-18 Koehring Company Hydraulic control valve with independently operable bypass valve
DE3321483A1 (de) * 1983-06-14 1984-12-20 Linde Ag, 6200 Wiesbaden Hydraulische einrichtung mit einer pumpe und mindestens zwei von dieser beaufschlagten verbrauchern hydraulischer energie
US4610194A (en) * 1985-03-01 1986-09-09 Caterpillar Inc. Load sensing circuit of load responsive direction control valve
DE3532816A1 (de) * 1985-09-13 1987-03-26 Rexroth Mannesmann Gmbh Steueranordnung fuer mindestens zwei von mindestens einer pumpe gespeiste hydraulische verbraucher
FR2619192B2 (fr) * 1987-08-03 1989-12-29 Bennes Marrel Distributeur hydraulique du type proportionnel avec prise d'informations concernant les plus fortes pressions dans les circuits d'utilisation
US4799420A (en) * 1987-08-27 1989-01-24 Caterpillar Inc. Load responsive control system adapted to use of negative load pressure in operation of system controls
IN171213B (de) * 1988-01-27 1992-08-15 Hitachi Construction Machinery
JP2683244B2 (ja) * 1988-04-14 1997-11-26 株式会社ゼクセル 制御弁
DE68910721T2 (de) * 1988-05-12 1994-03-10 Hitachi Construction Machinery Hydraulische Antriebseinrichtung für Raupenbaufahrzeuge.
JPH0786361B2 (ja) * 1988-11-10 1995-09-20 株式会社ゼクセル 油圧制御弁
FR2641583A1 (fr) * 1989-01-06 1990-07-13 Tardy Maurice Distributeur proportionnel pour la commande de recepteurs hydrauliques
WO1990013748A1 (en) * 1989-05-02 1990-11-15 Hitachi Construction Machinery Co., Ltd. Hydraulic driving device of construction equipment

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Publication number Publication date
US5222426A (en) 1993-06-29
JPH04312202A (ja) 1992-11-04
FR2672944B1 (de) 1995-01-27
FR2672944A1 (fr) 1992-08-21
EP0500419A1 (de) 1992-08-26
DE69206170D1 (de) 1996-01-04
DE69206170T2 (de) 1996-08-22

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