EP0623754B1 - Système hydraulique de contrÔle - Google Patents

Système hydraulique de contrÔle Download PDF

Info

Publication number
EP0623754B1
EP0623754B1 EP94104714A EP94104714A EP0623754B1 EP 0623754 B1 EP0623754 B1 EP 0623754B1 EP 94104714 A EP94104714 A EP 94104714A EP 94104714 A EP94104714 A EP 94104714A EP 0623754 B1 EP0623754 B1 EP 0623754B1
Authority
EP
European Patent Office
Prior art keywords
valve
port
lock
control
outlet
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
EP94104714A
Other languages
German (de)
English (en)
Other versions
EP0623754A3 (fr
EP0623754A2 (fr
Inventor
Matthew Thomas Miller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Deere and Co
Original Assignee
Deere and Co
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Deere and Co filed Critical Deere and Co
Priority to EP96117035A priority Critical patent/EP0756089A3/fr
Publication of EP0623754A2 publication Critical patent/EP0623754A2/fr
Publication of EP0623754A3 publication Critical patent/EP0623754A3/fr
Application granted granted Critical
Publication of EP0623754B1 publication Critical patent/EP0623754B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • 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
    • F15B11/003—Systems with load-holding 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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • 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
    • F15B13/021—Valves for interconnecting the fluid chambers of an actuator
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/3051—Cross-check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • 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

Definitions

  • the invention relates to a hydraulic control system for actuating a hydraulic actuator having at least two actuator connections with a main hydraulic source, a reservoir, a pressure-actuated main control valve which contains two work connections which can be connected to the actuator connections and which serves to control liquid flows between the actuator, the main hydraulic source and the reservoir, and with a first and a second control valve for adjusting the main control valve.
  • the main control valve Upon actuation of one of the control valves, the main control valve is moved from a neutral position, in which the actuator is held stationary, to a first position, in which the actuator is caused to move in a first direction.
  • the main control valve is moved from the neutral position into a second position in which the actuator is caused to move in a second direction.
  • a floating position of the main control valve is usually provided for such a floating function.
  • both the retract and float positions are activated by a single control valve, the available modulation range must be divided between these two control modes.
  • the allocation resolution capability which is of particular importance, is thus impaired in the run-in mode.
  • a floating function can also be achieved by using an additional third solenoid valve, through which both actuator connections are connected to the reservoir when the solenoid valve is excited, for example by a separate floating switch.
  • This solution requires an additional solenoid valve. It is desirable to implement a float function in a manner that does not require the main control valve to float or additional solenoid valves.
  • the object on which the invention is based is seen in specifying a hydraulic control system of the type mentioned at the outset with a floating function which avoids the problems mentioned at the outset and in which the liquid distribution in a working mode is not impaired.
  • the floating function should be able to be implemented with a low actuator connection leakage. It should be possible without the main control valve having additional floating positions and without the need for additional magnetic coils.
  • a load kickback function is also to be provided, which works independently of the supply pressure.
  • a pressure-controlled, proportional 4/3-way main control valve controls the fluid flow between an actuator (e.g. a double or single acting cylinder or a hydraulic motor), a pump and a reservoir.
  • a lock-out valve is arranged between each working connection of the main control valve and the associated actuator connections.
  • Each lockout valve includes a pressure control seat valve member which is exposed to the fluid pressure in a lockout chamber.
  • An outlet control valve is arranged between each lock-out valve and an associated, manually adjustable, electromagnetic control valve.
  • Each outlet control valve includes an outlet check valve which controls the liquid drained from the lockout chamber and an outlet valve piston which is urged by spring means to urge the outlet check valve into its closed position so that the liquid cannot escape from the lockout chamber.
  • a logic valve controls a floating valve which changes to a floating position in which both working connections of the main control valve are connected to one another and to the reservoir via the lock-out valves and the floating valve.
  • liquid pressure Via the control valves, liquid pressure also enters a relief chamber of the outlet control valve, whereby the outlet valve piston is lifted off the outlet check valve, so that the pressure in the lock-out chamber can be reduced to the reservoir via the floating valve.
  • the hydraulic control system according to the invention does not affect the liquid allocation in a working mode. Nevertheless, the floating function can be implemented with a low actuator connection leakage. Neither additional floating positions of the main valve nor additional solenoid coils are required to implement the floating function.
  • a load kickback function is provided that operates independently of the supply pressure.
  • the single figure shows the hydraulic diagram of a main control valve system with a floating function, on the basis of which the invention and further advantages and advantageous developments and refinements of the invention are described and explained in more detail below.
  • the hydraulic control system 10 controls an actuator 12, for example a double-acting or single-acting hydraulic cylinder or a two-sided hydraulic motor, which contains two actuator connections 14, 16.
  • a pressure actuatable main control valve 18 controls fluid connections between the cylinder 12, a main pump 20 and a reservoir 22.
  • the main control valve 18 is preferably a proportional, pressure-controlled, spring-centered 4/3-way valve (4-way, 3-position) with two Working connections 26, 28, each of which can be connected to an associated actuator connection 14, 16. Pressure may be applied to a control port 30 to move the control valve 18 to a first or extended position, and pressure may be applied to another control port 32 to move the main control valve 18 to a second or retracted position.
  • a first magnetically actuated control valve 40 which can be adjusted by an operator controls connections between an auxiliary pump 21, the reservoir 22, the control connection 30 and a sequential valve 44.
  • a second magnetically actuated control valve 42 which can be adjusted by an operator controls connections between the auxiliary pump 21, the reservoir 22, the control connection 32 and a sequence valve 46.
  • Each of the sequence valves 44, 46 lies between one of the working connections 26, 28 and the associated actuator connection 14, 16 and serves to reduce leakages between them.
  • Each follower valve 44, 46 includes a pressure sensitive seat valve 48 which is exposed to the fluid pressure in a follower valve chamber 50, a first follower valve port 52 which is connected to an associated working port 28, a second follower valve port 54 which is connected to an associated actuator port 16 , a seat part 56 responsive to pressure differences, which is biased into a closed position by a spring 57, and a throttle bore 58 in the seat part 56, which connects the second sequential valve connection 54 to the sequential valve chamber 50.
  • the hydraulic control system 10 also includes two exhaust control valves 60 and 62.
  • Each exhaust control valve 60, 62 includes an exhaust conduit 64 which connects the sequential valve chamber 50 to the first sequential valve port 52.
  • An outlet check valve 66 controls the flow of liquid through the outlet conduit 64.
  • an outlet valve piston 68 engages the outlet check valve 66, and a biased outlet valve spring 70 urges the outlet valve piston 68 toward the outlet check valve 66, and thereby the outlet check valve 66 to its closed position, in which a liquid outflow occurs the sequence valve chamber 50 is prevented via the outlet line 64.
  • Each outlet control valve 60, 62 includes a relief chamber 72 which communicates with an outlet of an associated control valve 40, 42.
  • the hydraulic control system 10 further includes a pressure controlled float valve 80, in the housing 82 of which a valve bore 83, a reservoir port 84 connected to the reservoir 22, a first port 84 connected to the working port 26, a second port 88 connected to the working port 28 and a control port 90 are embedded.
  • a valve part 92 movably arranged in the valve bore 83 contains an axial bore 93, which intersects a transverse bore 94 and a throttle bore 96 which connects the transverse bore 94 to the control connection 90.
  • the valve member 92 is between a first position, in which the first and second connections 86, 88 are blocked, and a second position, in which the first and second connections 86, 88 are connected to one another via the transverse bore 94 and via the axial bore 93 to the Storage container connection 84 are connected.
  • a preloaded spring 98 urges valve member 92 into its first position. If pressure is applied to the control connection 90, the valve part 92 moves into its second position.
  • the hydraulic control system 10 further includes a logic valve 100 through which the control port 90 is only pressurized when both control valves 40, 42 are operated simultaneously.
  • the logic valve 100 includes an inlet 104 connected to an output of one of the control valves 40 and 42, an outlet port 106 which is connected to the control port 90 of the float valve 80, and a control port 108 which is connected to an output of the other of the control valves 40 and 42 is connected.
  • the logic valve 100 can be moved from a first position, in which the inlet 104 and the outlet connection 106 are blocked, to a second position, in which the inlet 104 is connected to the outlet connection 106.
  • a preloaded spring 112 urges logic valve 100 into its first position. If pressure is applied to the control connection 108, the logic valve 100 moves into its second position.
  • control valves 40, 42 applies that when its solenoid is switched off, the corresponding control connection 30, 32 (as shown) with the reservoir 22nd is connected, and then when its solenoid is energized, the corresponding control terminal 30, 32 is connected to the auxiliary pump 21. It follows that when the control valve 40 is energized, the control port 30 is under pressure and the main control valve 18 connects the pump 20 to the working port 28 and the actuator port 16 and connects the reservoir 22 to the working port 26 and the actuator port 14 so that the cylinder 12 extends becomes.
  • control valve 42 when the control valve 42 is energized, the control port 32 is under pressure, the main control valve 18 connecting the pump 20 to the working port 26 and the actuator port 14, and the reservoir 22 to the working port 28 and the actuator port 16, so that the cylinder 12 is retracted.
  • the independent control valves 40, 42 provide a control pressure that is proportional to the electrical input signal and acts on the ends of the main control valve 18.
  • the main control valve 18 then moves to a position in which it is in equilibrium between the control pressure force and the centering springs. The flow direction and quantity can thus be controlled by the type of movement of the main control valve 18 described here.
  • control connection 30 When the control valve 40 is actuated, the control connection 30 is pressurized so that the main control valve 18 moves to the right with respect to the figure and enables the flow from the main pump 20 to the working connection 28 and the actuator connection 16 and the actuator 12 extends. In a corresponding manner, the actuator 12 is retracted when the control valve 42 is actuated.
  • both control valves 40, 42 When both control valves 40, 42 are energized, both control ports 30, 32 are pressurized so that the main control valve 18 does not move.
  • the logic valve 100 moves into its second position, in which the control connection 90 is pressurized and the float valve 80 is moved into its second position.
  • the two actuator connections 14 and 16 are connected to one another via the sequence valves 44, 46 and to the reservoir 22 via the float valve 80.
  • This provides a floating function that is independent of the main control valve 18. Furthermore, this floating function is achieved without the need for additional magnetic coils and without jeopardizing the modulation range available for the additional control valves.
  • the control valves 40, 42 also direct the pump pressure to the relief chambers 72 of the outlet control valves 60 and 62. This pressure raises the outlet valve pistons 68 from the outlet check valves 66, allowing the pressure in the follower valve chamber 50 to escape into the reservoir 22 via the float valve 80. As a result, only a slight pressure differential across the seat portions 56 is required to overcome the weak biasing force of the springs 57, lift the seat portion 56 from its valve seat, and close the connection between the sequential valve ports 52 and 54 to open. This enables free flow in both directions between the actuator connections 14 and 16 and from these to the reservoir 22, which takes place via the float valve 80.
  • pressure relief at the actuator connections 14 and 16 is provided within the sequence valves 44 and 46. This enables a pressure build-up at the actuator connections that goes beyond the system pressure, which can be caused by thermal expansion or a pressure increase, is reduced.
  • the pressure boost mentioned can occur in systems that prevent leakage.
  • This pressure relief occurs whenever the pressure applied to the actuator connection, which acts on the seat side of the outlet check valve 66, generates a force which is greater than the counterforce of the outlet valve spring 70. In this case, the outlet check valve 66 lifts off its seat and flows through an amount of oil sufficient to relieve the working port pressure before it closes again.
  • the present design achieves a low actuator connection leakage with simultaneous low hysteresis, which is attributable to the large gap between the main slide and its bore that is permitted here.
  • control valves 40 and 42 Since the entire control pressure range of the control valves 40 and 42 can be used for extending and retracting the cylinder 12, there is an improved flow control.
  • the floating function (which has not been used frequently so far) is implemented without affecting the metering flow during extension or retraction.
  • An inlet load check valve is not necessary because only the sequence valve connected to the return-side actuator connection is relieved of pressure during pressure operation.
  • the follower valve which is on the actuator port side to which pressure is supplied by the main control valve 18, is kept open by the flow-induced pressure difference across the seat part. If the pressure supply to the main pump 20 results in a pressure in the working connection which is lower is as the actuator port pressure, closes the sequence valve due to the sign reversal of the pressure difference across the seat member 56 and prevents oil drainage from the actuator port.
  • the sequence valves can be dispensed with if no small leakage at the actuator connections is required for the application.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Magnetically Actuated Valves (AREA)
  • Float Valves (AREA)

Claims (8)

  1. Système de commande hydraulique pour actionner un organe de réglage hydraulique (12) possédant au moins deux raccords (14,16), et comportant une source hydraulique principale (20), un réservoir (22), une soupape de commande principale (18) pouvant être actionnée par une pression et qui contient deux raccords de travail (26,28) pouvant être reliés aux raccords (14,16) de l'organe de réglage et sert à commander des écoulements de liquide entre l'organe de réglage (12), la source hydraulique principale (20) et le réservoir (22), et comportant des première et seconde soupapes de commande (40,42) pour régler la soupape de commande principale (18), l'une des soupapes de commande (40,42) pouvant être actionnée de manière à amener la soupape de commande principale (18) d'une position neutre, dans laquelle l'organe de réglage (12) est maintenu de façon fixe, dans une première position, dans laquelle l'organe de réglage (12) est amené à se déplacer dans une première direction, et l'autre soupape de commande (40,42) pouvant être actionnée de manière à amener la soupape de commande principale (18) de la position neutre dans une seconde position, dans laquelle l'organe de réglage (12) est amené à se déplacer dans une seconde direction, caractérisé par une soupape flottante (80), qui est séparée de la soupape de commande principale (18) et répond à des actionnements des deux soupapes de commande (40,42), est reliée aux deux raccords de travail (26,28) et, dans le cas d'un actionnement simultané des deux soupapes de commande (40,42) relie les deux raccords de travail (26,28) au réservoir (22).
  2. Système de commande hydraulique selon la revendication 1, caractérisé par une soupape flottante (80) comportant
    - un boîtier (82), qui contient un raccord de réservoir (84), qui est relié au réservoir (22), un premier raccord (86) qui est relié à l'un des raccords de travail (26), un second raccord (88) relié à l'autre raccord de travail (28) et un raccord de commande (90), et comportant
    - une partie (92) de la soupape flottante, qui, dans une première position, bloque les premier et second raccords (86,88), et dans une seconde position, relie les premier et second raccords (86,88) au raccord de réservoir (84) et qui est repoussée par des moyens formant ressort (98) dans sa première position, la partie (92) de la soupape flottante pouvant être amenée dans sa seconde position, à l'encontre de la force du ressort, par une pression appliquée au raccord de commande (90), et
    par des moyens formant soupape logique (100), qui placent sous pression le raccord de commande (90), lorsqu'aussi bien la première soupape de commande (40) que la seconde soupape de commande (42) sont actionnées simultanément.
  3. Système de commande hydraulique selon la revendication 2, caractérisé par des moyens formant soupape logique (100) comportant
    - une entrée (104), qui est reliée à l'une des sorties des première et seconde soupapes de commande (40,42), un raccord de commande (108), qui est relié à une sortie de l'autre des deux soupapes de commande (40,42), un raccord de sortie (106), qui est relié au raccord de commande (90) de la soupape flottante (80), et
    - des moyens formant ressort (112), qui sont précontraints de manière à repousser les moyens formant soupape logique (100) dans une première position, dans laquelle l'entrée (104) et le raccord de sortie (106) sont bloqués, les moyens formant soupape logique (100) pouvant être amenés à l'encontre de la force d'un ressort, lorsqu'une pression est appliquée à leur raccord de commande (108), dans une seconde position, dans laquelle l'entrée (104) est reliée au raccord de sortie (106).
  4. Système de commande hydraulique selon l'une des revendications 1 à 3, caractérisé par deux soupapes de blocage (44,46), qui sont raccordées respectivement entre l'un des raccords de travail (26,28) et un raccord associé (14,16) de l'organe de réglage et sont agencées de telle sorte qu'elles réduisent les fuites de liquide provenant des raccords (14,16) de l'organe de réglage.
  5. Système de commande hydraulique selon l'une des revendications 1 à 4, caractérisé par
    - une soupape de blocage (44,46) comportant une partie formant siège (56), qui répond à une pression et peut être déplacée en fonction de la pression du liquide, qui règne dans une chambre de blocage (50), pour commander une liaison entre un raccord de travail (26,28) de la soupape de commande principale (18) et le raccord associé (14,16) de l'organe de réglage, et en outre un premier raccord de blocage (52), qui est relié à un raccord de travail correspondant (26,28) de la soupape de commande principale (18), et en outre un second raccord de blocage (54), qui est relié à un raccord correspondant (14,16) de l'organe de blocage, et en outre une ouverture de sortie (58), qui relie le second raccord de blocage (54) à la chambre de blocage (50),
    - une canalisation de sortie (64) qui relie la chambre de blocage (50) à la soupape de commande principale (18),
    - une soupape de commande de sortie (60,62), qui commande la circulation du liquide dans la canalisation de sortie (64),
    - des moyens formant ressort (70), à l'aide desquels la soupape de commande de sortie (60,62) est repoussée dans une position fermée, dans laquelle un écoulement de liquide depuis la chambre de blocage (50) par l'intermédiaire de la canalisation de sortie (64) est empêché,
    - des moyens (68,72) répondant à la pression de liquide et qui sont reliés à l'une des deux soupapes de commande (40,42) de manière à ouvrir la soupape de commande de sortie (60,62) à l'encontre de la force d'un ressort, lorsque la soupape de commande (40,42) est actionnée.
  6. Soupape de commande hydraulique selon la revendication 5, caractérisée en ce que chaque soupape de sortie (44,46) contient :
    - une soupape à siège (48), qui répond à une pression et comporte une chambre de blocage (50), un premier raccord de blocage (52), qui est relié à un raccord de travail associé (26,28), un second raccord de blocage (54), qui est relié à un raccord associé (14,16) de l'organe de réglage, une ouverture de sortie (58), qui relie le second raccord de blocage (54) à la chambre de blocage (50), et une partie formant siège de soupape (56), qui est repoussée par des moyens formant ressort (57) dans sa position fermée, pour interrompre normalement un écoulement de liquide depuis le second raccord de sortie (54) à la chambre de blocage (50),
    - une canalisation de sortie (64), qui relie la chambre de blocage (50) au premier raccord de blocage (52),
    - une soupape antiretour de sortie (66) pour commander l'écoulement de liquide dans la canalisation de sortie (64),
    - un piston de sortie (68), qui peut être amené à engrener avec la soupape antiretour de sortie (66),
    - des moyens formant ressort précontraint (70) de la soupape de sortie, qui attaquent le piston de sortie (68) et repoussent ce dernier en direction de la soupape antiretour de sortie (66), pour fermer cette dernière, une sortie de liquide hors de la chambre de blocage (50) par l'intermédiaire de la canalisation de sortie (64) étant empêchée, et
    - une chambre de détente (72), qui est reliée à la sortie de l'une associée des deux soupapes de commande (40,42), auquel cas lors de l'établissement d'une pression dans la chambre de détente (72) le piston de sortie (72) est écarté de la soupape antiretour de sortie (66), à l'encontre de la force du ressort de sorte que cette soupape peut s'ouvrir et réduire la pression de liquide dans la chambre de blocage (50), ce qui permet également l'ouverture de la partie formant siège de soupape (56) et permet un écoulement de liquide depuis le second raccord de blocage (54) en direction du premier raccord de blocage (52).
  7. Système de commande hydraulique selon la revendication 5 ou 6, caractérisé en ce que chaque élément de siège de soupape (56) possède une zone qui répond à des pressions différentielles.
  8. Système de commande hydraulique selon l'une des revendications 1 à 7, caractérisé en ce que les soupapes de commande (40,42) commandent la pression hydraulique d'une source hydraulique auxiliaire (21).
EP94104714A 1993-04-05 1994-03-24 Système hydraulique de contrÔle Expired - Lifetime EP0623754B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP96117035A EP0756089A3 (fr) 1993-04-05 1994-03-24 Système hydraulique de contrÔle

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US43059 1993-04-05
US08/043,059 US5331882A (en) 1993-04-05 1993-04-05 Control valve system with float valve

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP96117035A Division EP0756089A3 (fr) 1993-04-05 1994-03-24 Système hydraulique de contrÔle
EP96117035.4 Division-Into 1996-10-24

Publications (3)

Publication Number Publication Date
EP0623754A2 EP0623754A2 (fr) 1994-11-09
EP0623754A3 EP0623754A3 (fr) 1995-03-01
EP0623754B1 true EP0623754B1 (fr) 1997-06-25

Family

ID=21925249

Family Applications (2)

Application Number Title Priority Date Filing Date
EP94104714A Expired - Lifetime EP0623754B1 (fr) 1993-04-05 1994-03-24 Système hydraulique de contrÔle
EP96117035A Withdrawn EP0756089A3 (fr) 1993-04-05 1994-03-24 Système hydraulique de contrÔle

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP96117035A Withdrawn EP0756089A3 (fr) 1993-04-05 1994-03-24 Système hydraulique de contrÔle

Country Status (7)

Country Link
US (1) US5331882A (fr)
EP (2) EP0623754B1 (fr)
JP (1) JP3476533B2 (fr)
BR (1) BR9401332A (fr)
CA (1) CA2119616C (fr)
DE (1) DE59403208D1 (fr)
ES (1) ES2103514T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112014004214B4 (de) 2013-09-13 2019-10-31 Kyb Corp. Fluid-Druck-Steuergerät

Families Citing this family (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5577532A (en) * 1994-07-11 1996-11-26 Palmer; Thomas W. Valve actuator
JP3478931B2 (ja) * 1996-09-20 2003-12-15 新キャタピラー三菱株式会社 油圧回路
KR100474259B1 (ko) * 1996-11-26 2005-06-20 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 건설기계의작업장치용실린더를위한유압장치
AT406357B (de) * 1998-10-15 2000-04-25 Hoerbiger Hydraulik Anordnung zur hydraulischen betätigung eines verdecks, eines heckdeckels od. dgl.
US6622939B2 (en) * 1999-02-01 2003-09-23 Exactrix Global Systems Apparatus for applying liquid fertilizers and pesticides using a dual stage variable rate distribution manifold
US6186044B1 (en) 1999-03-08 2001-02-13 Caterpillar Inc. Fluid control system with float capability
DE19919015C2 (de) * 1999-04-27 2001-11-15 Sauer Danfoss Nordborg As Nord Hydraulische Ventilanordnung mit Verriegelungs- und Schwimmfunktion
US6173639B1 (en) 1999-05-07 2001-01-16 Caterpillar Inc. Fluid control system having float control
US6389952B1 (en) * 1999-05-28 2002-05-21 Caterpillar Inc. Apparatus and method of operating a fluid cylinder of a work machine
DE19931142C2 (de) * 1999-07-06 2002-07-18 Sauer Danfoss Holding As Nordb Hydraulische Ventilanordnung mit Verriegelungsfunktion
US6282893B1 (en) 1999-08-19 2001-09-04 Delaware Capital Formation, Inc. Self-contained actuator
US6516706B2 (en) 1999-08-19 2003-02-11 Delaware Capital Formation, Inc. Actuator having internal valve structure
DE19958341A1 (de) * 1999-12-03 2001-07-12 Claas Industrietechnik Gmbh Erntemaschine mit frontseitig angebautem Erntevorsatz
DE10045404C2 (de) * 2000-09-14 2002-10-24 Sauer Danfoss Holding As Nordb Hydraulische Ventilanordnung
AUPR170400A0 (en) * 2000-11-28 2000-12-21 Ifield Technology Ltd Emergency energy release for hydraulic energy storage systems
JP2004301214A (ja) * 2003-03-31 2004-10-28 Hitachi Constr Mach Co Ltd 作業用車両の油圧駆動装置
US7004090B2 (en) * 2003-09-09 2006-02-28 Exactrix Llc Fertilizer injector wing for disc openers
US20050220596A1 (en) * 2004-03-30 2005-10-06 Cnh America Llc Method and apparatus for hydraulically produced ground following of an unloading ramp for a cotton harvester
DE102004020371A1 (de) * 2004-04-23 2005-11-10 Botschafter-Knopff, Ilse Hydraulische Steuereinrichtung
EP1915538B1 (fr) * 2005-08-19 2012-04-04 Bucher Hydraulics AG Montage pour commander un cylindre d'entrainement hydraulique a double effet
US20070290152A1 (en) * 2006-06-16 2007-12-20 Pengfei Ma Poppet valve
US20070290151A1 (en) * 2006-06-16 2007-12-20 Matthew Thomas Muller Valve
US8424836B2 (en) * 2006-06-16 2013-04-23 Caterpillar Inc. Bidirectional force feedback poppet valve
EP1895169A1 (fr) * 2006-09-04 2008-03-05 OIL CONTROL S.p.A. Ensemble de soupapes de décharge et de contrôle
US8893818B2 (en) * 2010-12-17 2014-11-25 Caterpillar Inc. Hydraulic system having dual tilt blade control
US8925439B2 (en) * 2011-01-13 2015-01-06 Husco International, Inc. Valve control valve circuit for operating a single acting hydraulic cylinder
DE112013006501T5 (de) 2013-01-24 2016-03-31 Volvo Construction Equipment Ab Vorrichtung und Verfahren zum Steuern einer Flussrate bei Baumaschinen
CN104675780A (zh) * 2013-12-02 2015-06-03 江苏神通阀门股份有限公司 一种高炉煤气发电管网系统用隔离阀
CN104482248B (zh) * 2014-11-03 2017-05-10 济南数锐电子科技有限公司 液控换向阀
US20170023149A1 (en) * 2015-07-22 2017-01-26 Cnh Industrial America Llc Hydraulic signal control system and method
DE102017117335B4 (de) * 2017-07-31 2024-12-05 Bürkert Werke GmbH & Co. KG Betätigungseinheit für ein Prozessventil sowie Prozessventil
JPWO2019053783A1 (ja) * 2017-09-12 2019-12-12 株式会社島津製作所 コントロールバルブ
CN108980129B (zh) * 2018-07-24 2020-04-07 中国航空工业集团公司西安飞行自动控制研究所 一种负载保持控制阀
CN112384662A (zh) * 2018-08-30 2021-02-19 沃尔沃建筑设备公司 用于建筑设备的液压回路
CN117570082A (zh) * 2019-02-06 2024-02-20 克斯美库股份有限公司 带保持阀的空气压力缸装置

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3304842A (en) * 1964-04-20 1967-02-21 Homer J Shafer Non-hammer poppet valve control
SE326666B (fr) 1968-11-29 1970-07-27 Akermans Verkstad Ab
US3643696A (en) * 1970-09-02 1972-02-22 Rex Chainbelt Inc Hydraulic control circuit
US3943825A (en) * 1972-04-17 1976-03-16 Caterpillar Tractor Co. Hydraulic control system for load supporting hydraulic motors
US4206688A (en) * 1978-06-09 1980-06-10 Caterpillar Tractor Co. Overrunning load control for hydraulic motors
US4201052A (en) * 1979-03-26 1980-05-06 Sperry Rand Corporation Power transmission
FR2459894A1 (fr) * 1979-06-26 1981-01-16 Poclain Sa Dispositif de commande d'un recepteur a fluide sous pression.
US4340087A (en) * 1980-08-21 1982-07-20 Sperry Corporation Power transmission
US4359931A (en) * 1981-01-19 1982-11-23 The Warner & Swasey Company Regenerative and anticavitation hydraulic system for an excavator
US4418612A (en) * 1981-05-28 1983-12-06 Vickers, Incorporated Power transmission
US4611528A (en) * 1981-11-12 1986-09-16 Vickers, Incorporated Power transmission
DE3201546C2 (de) * 1982-01-20 1986-03-27 Mannesmann Rexroth GmbH, 8770 Lohr Vorrichtung zum Steuern eines Hydromotors
US4860788A (en) * 1987-06-29 1989-08-29 Kayaba Industry Co. Ltd. Metering valve
FR2627838B1 (fr) * 1988-02-25 1991-01-11 Bennes Marrel Valve de securite pour recepteur hydraulique et circuit hydraulique la comportant
JPH01133503U (fr) * 1988-03-03 1989-09-12
DE9005983U1 (de) * 1990-05-26 1991-09-19 Robert Bosch Gmbh, 7000 Stuttgart Steuereinrichtung für einen Arbeitszylinder
US5235809A (en) * 1991-09-09 1993-08-17 Vickers, Incorporated Hydraulic circuit for shaking a bucket on a vehicle

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112014004214B4 (de) 2013-09-13 2019-10-31 Kyb Corp. Fluid-Druck-Steuergerät

Also Published As

Publication number Publication date
BR9401332A (pt) 1994-10-18
US5331882A (en) 1994-07-26
ES2103514T3 (es) 1997-09-16
CA2119616A1 (fr) 1994-10-06
CA2119616C (fr) 1998-09-01
JPH074403A (ja) 1995-01-10
DE59403208D1 (de) 1997-07-31
EP0756089A3 (fr) 1998-03-25
JP3476533B2 (ja) 2003-12-10
EP0623754A3 (fr) 1995-03-01
EP0756089A2 (fr) 1997-01-29
EP0623754A2 (fr) 1994-11-09

Similar Documents

Publication Publication Date Title
EP0623754B1 (fr) Système hydraulique de contrÔle
DE68909069T2 (de) Hydraulische Schaltung für Zylinder.
DE1921977C3 (de) Ventileinrichtung zur Steuerung der Druckmittelwege eines doppelwirkenden Servomotors
EP1450048A1 (fr) Agencement de vanne
DE3323363A1 (de) Vorgesteuertes druckreduzierventil
DE2513919C2 (de) Druckkompensierter Hydraulikkreis
DE60304663T2 (de) Hydraulische Ventileinrichtung
DE69922158T2 (de) Steuervorrichtung für einen hydraulikmotor
DE60032732T2 (de) Rohrbruch steuerventil vorrichtung
EP0650558B1 (fr) Dispositif de commande pour au moins un consommateur hydraulique
EP0935713A1 (fr) Systeme de soupape et procede de realisation
WO2005015030A1 (fr) Systeme de commande hydraulique pour engins de construction, en particulier pour excavateurs
DE3744064A1 (de) Steuersystem fuer frontlader-ausleger- und -schaufelbetriebssysteme
EP0115590B1 (fr) Dispositif de commande hydraulique
EP2157320B1 (fr) Commande hydraulique pour un moteur hydraulique
EP0198119B1 (fr) Distributeur hydraulique pour commande indépendamment de la charge
DE3225132A1 (de) Hydraulisches sicherheitsbremsventil
EP0491155B1 (fr) Distributeur pour commande d'un moteur hydraulique
EP0219052A2 (fr) Dispositif de commande hydraulique
WO2003102427A1 (fr) Cylindre hydraulique dote d'un ensemble soupapes
WO1995033136A1 (fr) Systeme de regulation d'un dispositif de levage avec soupape de regulation
DE3920131C2 (de) Steuerblock für einen Hydraulikantrieb in einem Flugzeug
EP0376023B1 (fr) Soupape électrohydraulique proportionnelle
WO2006105765A1 (fr) Soupape a tiroirs et dispositif de commande equipe de ladite soupape
DE2833971C2 (de) Leitungsbruchsicherungs-Vorrichtung zur Anordnung zwischen einem hydraulischen Steuergerät und wenigstens einem Arbeitszylinder

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE ES FR GB IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE ES FR GB IT

17P Request for examination filed

Effective date: 19950209

17Q First examination report despatched

Effective date: 19950420

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR GB IT

XX Miscellaneous (additional remarks)

Free format text: TEILANMELDUNG 96117035.4 EINGEREICHT AM 24/10/96.

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19970626

REF Corresponds to:

Ref document number: 59403208

Country of ref document: DE

Date of ref document: 19970731

ET Fr: translation filed
REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2103514

Country of ref document: ES

Kind code of ref document: T3

ITF It: translation for a ep patent filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20040318

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20040407

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20050316

Year of fee payment: 12

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050326

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20051130

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20051130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060324

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20050326

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20060324

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20120327

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20130220

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 59403208

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20140325