EP2597209B1 - Système de réglage d'un dispositif de levage hydro-électronique - Google Patents

Système de réglage d'un dispositif de levage hydro-électronique Download PDF

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Publication number
EP2597209B1
EP2597209B1 EP11190345.6A EP11190345A EP2597209B1 EP 2597209 B1 EP2597209 B1 EP 2597209B1 EP 11190345 A EP11190345 A EP 11190345A EP 2597209 B1 EP2597209 B1 EP 2597209B1
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EP
European Patent Office
Prior art keywords
pressure
valve
pump
hoisting gear
electronic
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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.)
Not-in-force
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EP11190345.6A
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German (de)
English (en)
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EP2597209A1 (fr
Inventor
Recep Macit
Martin Ascherl
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Hawe Hydraulik SE
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Hawe Hydraulik SE
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Priority to EP11190345.6A priority Critical patent/EP2597209B1/fr
Publication of EP2597209A1 publication Critical patent/EP2597209A1/fr
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Publication of EP2597209B1 publication Critical patent/EP2597209B1/fr
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • E02F9/2235—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps including an electronic controller
    • 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
    • F15B11/006—Hydraulic "Wheatstone bridge" circuits, i.e. with four nodes, P-A-T-B, and on-off or proportional valves in each link
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • F15B11/055—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive by adjusting the pump output or bypass
    • 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
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • 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
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/30575—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve in a Wheatstone Bridge arrangement (also half bridges)
    • 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/60—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
    • F15B2211/6057—Load sensing circuits having valve means between output member and the load sensing circuit using directional control 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
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7052—Single-acting output members
    • 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
    • F15B2211/77—Control of direction of movement of the output member
    • F15B2211/7741—Control of direction of movement of the output member with floating mode, e.g. using a direct connection between both lines of a double-acting cylinder

Definitions

  • the invention relates to an electronic-hydraulic hoist control system according to the preamble of patent claim 1.
  • a known Hubwerksregelsystem is a four-position four-way gate valve with two proportional solenoids and two Druckvorwinberichtungen provided for the purpose of load pressure independence on the pump side a supply regulator pressure compensator and on the side of the hoist lifting cylinder associated with a lifting pressure compensator and a lowering pressure compensator.
  • a float position function for the lift cylinder is adjustable in one of the four control positions of the 4/4 damper pressure control valve. For a single-acting lifting cylinder in this case the construction effort is enormous, especially with the leakage-laden four-position slide valve.
  • the invention is based on the object, an electronic-hydraulic Hubtechniksregelsystem of the type mentioned, i. with many different EHR functions, despite being a floating position function structurally simple and quickly appealing.
  • the float position function is set via the control unit on the 2/2-way pressure control valve, at which time the 2/2-black / white solenoid valve shuts off the load pressure signal circuit section in order to prevent unwanted reactions of the hoist control system and / or the pump due to load pressure signal influences. excluded.
  • the floating position function selectable in this way via the EHR control unit makes it possible, for example, to have an attachment on the hoist, such as a plow, snow plow or mower, follow ground unevenness in ground contact under all or part of its own weight, regardless of relative movements of the vehicle Vehicle body of the vehicle equipped with the hoist.
  • an attachment on the hoist such as a plow, snow plow or mower
  • the solenoid valve in the signal circuit section is designed as a seat valve and connected so that when energized black and white magnets, the passage position is adjusted and held by the closing spring.
  • the shut-off position results in selected via the control unit floating position function with energized black and white magnet. In the shut-off position leakage is given in one or both flow directions.
  • the solenoid valve could be reversed.
  • the 2/2-lift pressure control valve can be brought to an at least substantially unthrottled passage position at maximum current supply of the proportional magnet in order to have as little throttle loss as possible in the lifting control.
  • the 2/2-lowering pressure control valve can be brought into throttled passage positions with increasing energization of the proportional solenoid, for example, to produce a desirable hydraulic damping, or, preferably, in a regenerative operation from load movements fed back hydraulic pressure energy in a pressure accumulator or, preferably, one To achieve speed limit.
  • the pump in the pump / return arrangement may be a variable displacement pump or a fixed displacement pump.
  • the variable displacement pump is controlled from the load pressure signal circuit or load pressure signal circuit section so that a higher flow rate is provided with increasing load pressure signal and is regulated down to a minimum flow rate when the load pressure signal is absent.
  • the fixed displacement pump may contain a circulation circuit, optionally with a pressure compensator valve, as a supply control, which either directs the delivery rate to the return line can flow out or adapted to the needs of the flow or the pressure for the lifting cylinder provides.
  • a check valve blocking the direction of the pump is arranged to be able to charge the pressure accumulator not only by the pump but also by the load pressure, and is in the bypass line upstream of the node blocking towards the node
  • Check valve arranged to prevent the automatic discharge of the pressure accumulator or adjusting the lifting cylinder without influencing the electronic-hydraulic Hubtechnikregelsystems.
  • the 2/2-way pressure control valve acts as a suction check valve opening in the direction of the lifting side of the lifting cylinder. If there is a load reversal on the hoist, i. With a lift lifting the load acting on, then the lifting side of the lifting cylinder pressure medium from the return is sucked.
  • Fig. 1 illustrates a block diagram of a main part of an electronic-hydraulic Hubtechniksregelsystems E of a vehicle, not shown, which is equipped for example behind a rear axle or front of a front axle 2 with a hoist 1 (front or rear hitch).
  • the hoist 1 has, for example in the manner of a three-point lifting device upper link 3, lower link 4 and intermediate link 6, wherein the lower link 4 an attachment point 5 for example, an attachment, such as a plow, a mower or the like., Is provided.
  • the hoist 1 is operated with at least one single-acting hoist lifting cylinder Z, at the lifting side 8 a working line 7 is connected.
  • E u.a. perform multiple EHR control functions, which usually allow a position control, a draft control, a mixed control, a slip control, a pressure control, a force setting, a vibration damping, an external control, possibly a weighing function and the like in the vehicle, plus a floating position function, for example is needed so that an attachment on the hoist in ground contact uneven ground regardless of driving movements of the vehicle is able to follow, under the full dead weight or under an adjustable portion of its own weight.
  • the electronic-hydraulic Hubtechniksregelsystem E is supplied from a pump / return assembly 9 with a pump 10, in the embodiment of a variable displacement, and a pressure medium vorhaltptenden return 13.
  • the pump 10 is associated with a supply control 11, which may be incorporated into a load pressure signal circuit, not shown, and in the embodiment shown is connected to a load pressure signal circuit section 36 and, for example, the delivery rate or the pressure in a supply line 12 output of the pump 10 is adjusted depending on demand.
  • the pump 10 could be a constant-flow pump whose supply control 11 has, for example, a circulation control with a pressure compensator, which can either flow out into the return 13 depending on the load pressure signal or provide the delivery rate or the pressure as needed.
  • the electronic-hydraulic hoist control system E has at least one electronic control unit CU, which may have an input section 14, and is connected via lines 15 to various sensors (not shown) in the vehicle, hoist 1 or on the attachment.
  • the sensors may be speed or velocity sensors, force sensors, position sensors and the like.
  • the control unit CU is further connected to electrical components of the hydraulic control between the pump 10 and the lifting cylinder Z.
  • the supply line 12 from the output of the pump 10 leads to a node 17 in the working line 7.
  • a 2/2-lifting pressure control valve 18 is arranged in a poppet-type, which is actuated by a proportional solenoid 20, a has load-independent pressure feedforward control 21, and is held by a spring 19 at de-energized proportional solenoid 20 in the shut-off position shown, in which the supply line 12 is shut off leak-free in the direction of the node 17.
  • corresponding pressure-regulating passage positions can be set for the energization, with an at least substantially unthrottled passage position 28 given at maximum current flow.
  • a pilot line 22 indicated by dashed lines can branch off to the pressure pilot 21 in order to report the load pressure acting on the lifting side 8 upstream in the passage positions of the 2/2-lift pressure regulating valve 18.
  • the load pressure message can also be done without own pilot control line 22 in the interior of the 2/2-lift pressure control valve 18, and serves, for example, to generate a load force proportional to the load pressure via a variable from the proportional solenoid 20 variable throttle against the actuating force of the proportional solenoid, the proportional solenoid 20th processed as a controlled variable to be able to control load pressure independent.
  • the load pressure signal circuit section 36 branches off from the branch 35 to the supply control 11.
  • the section 36 may for example be incorporated via a not shown shuttle valve in the load pressure signal circuit, not shown, and performs a load pressure signal as soon as the proportional solenoid 20 of the 2/2-lift pressure control valve 18 is energized.
  • system pressure limiting valve 25 (secondary pressure limiting) is included, the response pressure is adjustable.
  • a 2/2-way pressure control valve 27 is included in the seat valve design, which has a proportional solenoid 30 for actuating a load pressure independent pressure pilot control 31.
  • a proportional solenoid 30 for actuating a load pressure independent pressure pilot control 31.
  • the 2/2-way pressure control valve 27 although in the shut-off position set by a spring 29 when the proportional solenoid 30 is de-energized, leakage-free sealing at least in the direction of flow to the return 13 can prevail, but here e.g. paired with a Nachsaug-checkback function in the flow direction from the return line 13 to the node 17.
  • the 2/2-lowering pressure control valve 27, in contrast to the 2/2-lift pressure control valve 18 depending on the energization of the proportional solenoid 30 assume variable throttled passage positions 31.
  • a dashed line indicated pilot line 32 may be provided to report the load pressure on the lifting side 8 to the pressure pilot 31, so that, as mentioned, here also with the proportional solenoid 30 is controlled by a load pressure-dependent force strictly independent of the load pressure.
  • the load pressure can alternatively be tapped inside the valve 27 for generating the control force (elimination of pilot power 32).
  • a 2/2 black and white solenoid valve 37 having a black and white switching magnet 38 acting against a closing spring 39, e.g. is connected so that it holds when energized black / white magnet 38, the set by the closing spring 39 passage position, however, shuts off when energized the black / white switching magnet 38.
  • Fig. 2 shown embodiment of the electronic-hydraulic Hubtechniksregelsystems E differs from that of Fig. 1 in that a regenerative operation with energy recovery is possible because a 2/2-lifting pressure control valve 18 bypassing line 40 leads from the supply line 12 to node 17, to which a pressure accumulator 41 (eg with gas pressure bias or spring preload) is connected. Furthermore, here is the output of the pump 10 a blocking to the pump check valve 42 is disposed, and upstream of the node 17 in the direction of node 17 blocking check valve 43.
  • a 2/2-lifting pressure control valve 18 bypassing line 40 leads from the supply line 12 to node 17, to which a pressure accumulator 41 (eg with gas pressure bias or spring preload) is connected.
  • a blocking to the pump check valve 42 is disposed, and upstream of the node 17 in the direction of node 17 blocking check valve 43.
  • the load pressure on the lifting side 8 of the lifting cylinder Z can be used to load the pressure accumulator 41, or can be used, for example, resulting from driving movements or when terminating a lowering movement of a load for this purpose load pressure increases.
  • the recovered hydraulic pressure energy can be used to relieve the pressure of the pump 10 by first energizing the proportional solenoid 20 of the 2/2-lift pressure control valve 18, the stored energy the pressure accumulator 41 is used without the help of the pump 10.
  • the pressure accumulator 41 to be charged also by the pump 10 allows a predetermined hydraulic damping effect.
  • the proportional solenoid 20 is energized in a corresponding to the desired lifting speed corresponding extent to extend the lifting cylinder Z in de-energized proportional solenoid 30, the 2/2-black / white solenoid valve 37 is in the illustrated passage position and the load pressure at the junction 35 tapped and is transmitted to the supply control 11.
  • the lifting movement of the lifting cylinder Z takes place at the selected speed load pressure independent. If the hoist 1 to block hydraulically or stop, both proportional solenoids 20, 30 are de-energized.
  • the load pressure on the lifting side 8 can load the pressure accumulator 41.
  • the proportional solenoid 30 is energized to control the lowering movement with a proportional to the current speed, for example, a certain damping or speed limit can be adjusted and initially, if necessary, the pressure accumulator 40 is loaded.
  • the control unit CU switches the proportional solenoid 20 de-energized, the proportional solenoid 30 is optionally energized maximum, and at the same time the black / white switching magnet 38 is energized, so that in the shut-off position of the 2/2-lifting Pressure control valve 18, the 2/2-way pressure control valve 27 its throttling full passage position (or, if desired, a throttled intermediate-passage position) and at the same time the load pressure signal circuit section 36 is shut off, so that no load pressure signals to the supply control 11 arrive.
  • the pressure control valves 18, 27 are ideal load pressure independent work, for example, accordingly EP 10 195 693.6 or maybe even EP 2 270 340 A .
  • the 2/2-lowering pressure control valve 27 could work independently of load pressure, because the 2/2-lift pressure control valve 18 is optionally supported by the supply control 11 via the load pressure signal so that in the combination load pressure independence is achieved.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (9)

  1. Système de régulation hydro-électronique (E) de groupe de relevage, destiné à au moins un vérin de levage de groupe de relevage (Z), à simple effet, comprenant un appareil de commande EHR (CU), un circuit de signal de pression de charge, et au moins une vanne de régulation de pression qui peut être actionnée par l'appareil de commande (CU) par l'intermédiaire d'un aimant proportionnel (20, 30), et est située entre un agencement de pompe/retour (9) et un côté levage (8) du vérin de levage de groupe de relevage, la pompe (10) pouvant être commandée à partir du circuit de signal de pression de charge pour alimenter une conduite de travail (7) menant au côté levage (8), et une fonction de position flottante du vérin de levage pouvant être réglée en plus de multiples fonctions de régulation EHR, par l'intermédiaire de l'appareil de commande EHR (CU), caractérisé en ce qu'entre la pompe (10) et un noeud (17) de la conduite de travail (7), est prévue une vanne de régulation de pression de levage 2/2 (18) du type vanne à siège avec aimant proportionnel (20) et commande pilote de pression (21) indépendante de la pression de charge, et entre le noeud (17) et le retour (13), est prévue une vanne de régulation de pression d'abaissement 2/2 (27) du type vanne à siège avec aimant proportionnel (30) et commande pilote de pression (31) indépendante de la pression de charge, et en ce que dans un tronçon de circuit de signal de pression de charge (36) dérivé entre la vanne de régulation de pression de levage 2/2 (18) et le noeud (17) et raccordé à un dispositif de régulation d'alimentation (11) de la pompe (10), est agencée une électrovanne 2/2 tout ou rien (37), qui est ouverte dans le cas où sont réglées des fonctions de régulation EHR, et qui ferme lorsque la fonction de position flottante est réglée et que l'aimant proportionnel (30) de la vanne de régulation de pression d'abaissement 2/2 (27) est alimenté en courant.
  2. Système de régulation hydro-électronique de groupe de relevage selon la revendication 1, caractérisé en ce que l'électrovanne 2/2 tout ou rien (37) est une vanne à siège avec un ressort de fermeture (39) réglant la position de passage pour un aimant tout ou rien (38) non alimenté en courant, la vanne à siège pouvant être amenée dans la position de fermeture lorsque la fonction de position flottante est sélectionnée par l'appareil de commande (CU) et que l'aimant tout ou rien (38) est alimenté en courant.
  3. Système de régulation hydro-électronique de groupe de relevage selon la revendication 1, caractérisé en ce que la vanne de régulation de pression de levage 2/2 (18) peut être amenée, par une alimentation en courant maximum de l'aimant proportionnel (20), jusqu'à une position de passage (28) sensiblement non étranglée, et en ce que la vanne de régulation de pression d'abaissement 2/2 (27) ne peut être amenée, par une alimentation croissante en courant de l'aimant proportionnel (30), que dans des positions de passage étranglées (34), de préférence dans des positions de passage étranglées de manière proportionnellement variable.
  4. Système de régulation hydro-électronique de groupe de relevage selon la revendication 1, caractérisé en ce que la pompe (10) est une pompe à cylindrée variable ou une pompe constante, avec dans chaque cas une régulation d'alimentation (11) pour la conduite de travail (7), raccordée au tronçon de circuit de signal de pression de charge (36) renfermant l'électrovanne 2/2 tout ou rien (37).
  5. Système de régulation hydro-électronique de groupe de relevage selon la revendication 1, caractérisé en ce qu'entre la dérivation (35) du tronçon de circuit de signal de pression de charge (36) et le noeud (17) est agencé un clapet antiretour (23) bloquant en direction de la pompe (10).
  6. Système de régulation hydro-électronique de groupe de relevage selon la revendication 1, caractérisé en ce qu'à une conduite de contournement (40) de la vanne de régulation de pression de levage 2/2 (18), entre la pompe (10) et le noeud (17) est agencé un accumulateur de pression (41) avec précontrainte à ressort ou à gaz.
  7. Système de régulation hydro-électronique de groupe de relevage selon la revendication 6, caractérisé en ce qu'en amont de la conduite de contournement (40) est agencé un clapet antiretour (42) bloquant en direction de la pompe (10), et dans la conduite de contournement (40), en amont du noeud (17), est agencé un clapet antiretour (43) bloquant en direction du noeud (17).
  8. Système de régulation hydro-électronique de groupe de relevage selon la revendication 1, caractérisé en ce que la vanne de régulation de pression d'abaissement 2/2 (27) fait office, au moins dans le cas où l'aimant proportionnel (30) n'est pas alimenté en courant, de vanne antiretour de ré-aspiration (33) ouvrant en direction du côté levage (8).
  9. Système de régulation hydro-électronique de groupe de relevage selon l'une au moins des revendications précédentes, caractérisé en ce que dans ou au niveau de la commande pilote de pression (21, 31) respective, lors de l'alimentation en courant de l'aimant proportionnel (20, 30), il est possible de produire hydrauliquement, à partir de la pression de charge respective du côté levage (8), une force de réglage proportionnelle à la pression de charge et agissant à l'encontre de la force d'actionnement de l'aimant proportionnel, de préférence par l'intermédiaire d'un étranglement de réglage pouvant être actionné par l'aimant proportionnel (20, 30) et intégré à la commande pilote de pression (21, 31).
EP11190345.6A 2011-11-23 2011-11-23 Système de réglage d'un dispositif de levage hydro-électronique Not-in-force EP2597209B1 (fr)

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DE102019209932A1 (de) * 2019-07-05 2021-01-07 Robert Bosch Gmbh Wassertanksystem zur Bereitstellung von Wasser für ein mit Brennstoffzellen betriebenes Fahrzeug
US11624377B1 (en) * 2022-03-08 2023-04-11 Turk Traktor Ve Ziraat Makineleri A.S. Single solenoid-controlled electro-hydraulic liftomatic system

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US6397655B1 (en) * 2000-04-03 2002-06-04 Husco International, Inc. Auto-calibration of a solenoid operated valve
ITBO20020612A1 (it) * 2002-09-27 2004-03-28 Cnh Italia Spa Dispositivo di attacco di attrezzi agricoli ad un trattore.
DE20317749U1 (de) * 2003-11-18 2005-03-24 Hawe Hydraulik Gmbh & Co Kg Elektrohydraulische Regenerativ-Steuervorrichtung
DE102005005314A1 (de) 2004-12-20 2006-06-22 Bosch Rexroth Aktiengesellschaft Ventilanordnung und Verfahren zur Ansteuerung eines doppeltwirkenden Verbrauchers
US7921880B2 (en) * 2007-08-20 2011-04-12 Hydraforce, Inc. Three-way poppet valve with intermediate pilot port
DE102007040877A1 (de) 2007-08-29 2009-03-05 Robert Bosch Gmbh Hubwerk und Verfahren zum Ansteuern eines Hubwerkes
EP2270340B1 (fr) 2009-07-02 2013-01-09 HAWE Hydraulik SE Soupape hydraulique pilotée à siège

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