EP3530962B1 - Procédé de commande d'une pression de descente d'un levage assisté électrohydraulique et levage électrohydraulique - Google Patents

Procédé de commande d'une pression de descente d'un levage assisté électrohydraulique et levage électrohydraulique Download PDF

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Publication number
EP3530962B1
EP3530962B1 EP19158718.7A EP19158718A EP3530962B1 EP 3530962 B1 EP3530962 B1 EP 3530962B1 EP 19158718 A EP19158718 A EP 19158718A EP 3530962 B1 EP3530962 B1 EP 3530962B1
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EP
European Patent Office
Prior art keywords
pressure
lowering
lifting
valve
effective area
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.)
Active
Application number
EP19158718.7A
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German (de)
English (en)
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EP3530962A1 (fr
Inventor
Peter Schmuttermair
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.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Priority claimed from DE102018204568.2A external-priority patent/DE102018204568A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP3530962A1 publication Critical patent/EP3530962A1/fr
Application granted granted Critical
Publication of EP3530962B1 publication Critical patent/EP3530962B1/fr
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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
    • 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
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • 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
    • F15B2211/50554—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure downstream of the pressure control means, e.g. pressure reducing 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5158—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and an 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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/526—Pressure 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • 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
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6653—Pressure control
    • 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
    • F15B2211/7053—Double-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
    • F15B2211/76—Control of force or torque of the output member

Definitions

  • the invention relates to a method for controlling a lowering pressure of an electrohydraulic power lift, which has at least one working cylinder with a piston, with a lifting side, which the piston delimits with a lifting-side effective area, to which pressure medium is supplied for lifting a load and in which a lifting pressure is present, and with a lowering side, which the piston delimits with a lowering-side effective area, to which pressure medium is supplied for lowering a load and in which the lowering pressure is present.
  • the electrohydraulic power lift also comprises a first pressure sensor for detecting the lifting pressure and a second pressure sensor for detecting the lowering pressure, an adjustable pressure valve for setting a lowering pressure and an electronic control unit, to which the pressures detected by the pressure sensors are fed and by which the pressure valve can be controlled.
  • the lifting side and the lowering side can be compared to the EP2 884 118
  • the arrangement shown may also be reversed.
  • the ground-side Cylinder chamber is the lifting side
  • the rod-side cylinder chamber usually represents the lifting side.
  • the one from the EP 2 884 118 A1 Known electro-hydraulic power lifts have an adjustable pressure control valve assigned to the lowering side, with which a certain pressure can be regulated on the lowering side. There is also a pressure sensor with which the pressure on the lifting side can be recorded. The pressure sensor is intended to detect certain operating situations, for example excessive pressure on the lifting side or a pressure drop on the lifting side, and then to change the control of the pressure control valve.
  • the invention is based on the object of specifying a method with which the functioning of an electro-hydraulic power lift with the features specified at the outset is improved.
  • the equivalent sink pressure is set equal to zero for the formation of the pressure value if the ongoing determination of the equivalent sink pressure results in a negative value.
  • the pressure valve is advantageously controlled according to the lowest pressure that can be set on it. Usually, the pressure valve is not controlled in this case. Unless it is a pressure valve with a negative characteristic, such as one in the EP 2 884 118 A1 is shown.
  • the pressure setting on the sink side can be further improved by increasing or decreasing the control signal for the pressure valve depending on the current volume flow and its sign in order to compensate for a volume flow-related pressure drop between the pressure valve and the sink side.
  • the control signal for the pressure valve can be increased or decreased according to a characteristic curve. It is also possible to increase or decrease it according to a factor.
  • the electro-hydraulic power lift includes a load-compensated LS directional valve that can be connected to the lifting side of the working cylinder, a volume flow flowing between the pressure valve and the lowering side of the working cylinder, in particular a volume flow flowing away from the lowering side, can be determined via the control signal with which the LS (load sensing) directional valve is controlled.
  • the lifting mode is particularly suitable for determining the volume flow in this way, since lifting is usually load-compensated via the LS directional valve and the target volume flow given as a control signal to the LS directional valve corresponds to the actual volume flow, as long as no stop is reached or the hydraulic energy is limited and a pump does not deliver as much pressure medium as required.
  • a volume flow between the pressure valve and the lowering side of the working cylinder can also be determined by deriving the signal from a position sensor assigned to the working cylinder. This is particularly advantageous when lowering, as it prevents overpressure. The pressure value is only increased when a volume flow is also flowing.
  • different target pressures can be specified by the control unit.
  • a shut-off valve can be arranged between the pressure valve and the lowering side of the working cylinder, and pressure medium can be discharged from the lowering side of the working cylinder via a relief valve, bypassing the pressure valve. It can be advantageous if the shut-off valve is closed and the relief valve is opened when the target volume flow to the lifting side and thus the target speed for lifting exceeds a certain value and the pressure value falls below a certain value.
  • the pressure valve is preferably a pressure control valve.
  • a pressure control valve usually has a consumer connection connected to a hydraulic consumer - here to the lower side of the working cylinder - a pressure connection and a tank connection and is able to allow pressure medium to flow to the hydraulic consumer as well as to flow away from the hydraulic consumer for pressure control.
  • the invention is also implemented in an electro-hydraulic power lift, which has at least one working cylinder with a piston, with a lifting side, which the piston delimits with a lifting-side effective surface, to which pressure medium is supplied for lifting a load and in which a lifting pressure is present, and with a lowering side, which the piston delimits with a lowering-side effective surface, to which pressure medium is supplied for lowering a load and in which the lowering pressure is present, a first pressure sensor for detecting the lifting pressure and a second pressure sensor for detecting the lowering pressure, an adjustable pressure valve for setting a lowering pressure and an electronic control unit, to which the pressures detected by the pressure sensors are supplied and by which the pressure valve can be controlled, wherein the electronic control unit is designed to carry out a method as described above.
  • the electro-hydraulic power lift shown is in this case the rear lifting mechanism on a tractor and has a working cylinder 10. Inside a housing of the working cylinder, a piston 11 is movable, to which a piston rod 12 is attached on one side, which emerges from the housing on one end, the so-called head of the working cylinder.
  • the piston and the piston rod form and separate a cylinder chamber 13 on the rod side or base side and a ring-shaped cylinder chamber 14 on the rod side.
  • pressure medium is supplied to the base side cylinder chamber 13 for lifting and to the rod side cylinder chamber 14 for lowering.
  • the cylinder chamber on the bottom side therefore represents the lifting side and the cylinder chamber on the rod side represents the lowering side of the working cylinder.
  • the lifting-side effective surface 15, with which the piston 11 limits the lifting side is larger than the lowering-side, annular effective surface 16, with which the piston limits the lowering side.
  • the free end of the piston rod 12 is connected to an attachment, shown here as a plow, via lifting arms 17 hinged to the tractor.
  • the connection is drawn very schematically.
  • the position assumed by the lifting arms 17 is detected by a position sensor 18 and converted into an electrical signal.
  • the pressure in the cylinder chamber 13 can be detected by a first pressure sensor 19.
  • the pressure in the cylinder chamber 14 can be detected by a second pressure sensor 20, which, like the first pressure sensor, converts the pressure into an electrical signal.
  • the electro-hydraulic power lift shown also has a load-sensing controlled variable displacement pump 25, which sucks pressure medium from a tank 26 and discharges it into a pump line 27.
  • Load-sensing controlled means that the variable displacement pump delivers so much pressure medium that the pressure in the pump line 27 is a certain pressure difference above a control pressure reported to the load-sensing regulator 28 of the variable displacement pump, which is usually the highest load pressure of all hydraulic consumers simultaneously supplied with pressure medium.
  • a pressure control valve 35 which is proportionally adjustable with the aid of a proportional electromagnet 36, is connected with a pressure connection 37 to the pump line 27 and with a relief connection 38 to a tank line 39, via which pressure medium flows back from the hydraulic consumers of the tractor, in particular from the working cylinder 10, to the tank 26.
  • the pressure at a control connection 40 of the pressure control valve which can be connected to the rod-side cylinder chamber 14, is fed back to a measuring surface on the pressure control valve via a control line 41 and generates a force on the measuring surface which, together with a force exerted by a control spring 42, acts against the force of the proportional electromagnet 36.
  • the pressure control valve 35 is shown as a directly controlled pressure control valve. However, a pilot-operated pressure control valve can also be used.
  • a shut-off valve 45 is arranged between the control connection 40 of the pressure control valve 35 and the rod-side cylinder chamber 14, which is designed as a 2/2-way seat valve, assumes its blocking position under the action of a return spring 46, in which the connection between the control connection 40 and the cylinder chamber 14 is interrupted, and can be brought by a switching magnet 47 against the force of the return spring 46 into a through position in which the connection between the control connection 40 and the cylinder chamber 14 is open.
  • a relief valve 50 is arranged between the rod-side cylinder chamber 14 of the working cylinder 10 and the tank line 39. Like the valve 45, this relief valve is designed as a 2/2-way seat valve. Under the action of a return spring 51, it assumes its blocking position in which the connection between the tank line 39 and the cylinder chamber 14 is interrupted. It can be brought into a through position by a switching magnet 52 against the force of the return spring 51, in which the connection between the cylinder chamber 14 and the tank line 39 is open.
  • the relief valve 50 is used in certain operating states to complete pressure relief of the rod-side cylinder chamber 14. When the relief valve 50 is open, the shut-off valve 45 is closed. When the shut-off valve 45 is open, the relief valve 50 is closed.
  • the inflow of pressure medium to the cylinder chamber 13 on the bottom of the working cylinder 10 and the outflow of pressure medium from this cylinder chamber can be controlled with an electrohydraulic lifting gear control valve arrangement 60.
  • the lifting gear control valve arrangement 60 has a consumer connection 61 that is fluidically connected to the cylinder chamber 13.
  • the lifting gear control valve arrangement has a pump connection 62 connected to the pump line 27 and a tank connection 63 connected to the tank line 39.
  • the lifting gear control valve arrangement 60 comprises an individual pressure compensator (not shown in detail) that keeps the pressure drop constant via an adjustable metering orifice so that the amount of pressure medium flowing through the metering orifice only depends on the current flow cross-section of the metering orifice.
  • the outflow of pressure medium from the cylinder chamber 13 is not controlled independently of the load pressure.
  • the lifting gear valve arrangement 60 also has a load sensing connection 64, from which a control line 65 leads to a first input of a shuttle valve 66.
  • the second input of the shuttle valve 66 is connected to the control connection 40 of the pressure control valve 35 via a control line 67.
  • the output of the shuttle valve 66 is connected to the load sensing regulator 28 of the variable displacement pump 25.
  • the load sensing regulator 28 is therefore informed of the higher of the pressures present in the cylinder chambers 13 and 14.
  • an electronic control unit 70 to which the electrical signals of the position sensor 18, the two pressure sensors 19 and 20 and an electrical target signal, which is generated with the aid of an operating element 71, are fed via electrical lines 72, 73, 74 and 75.
  • the electronic control unit calculates control signals for the electromagnets of the pressure control valve 35, the shut-off valve 45, the relief valve 50 and the lifting gear valve arrangement 60 from the electrical signals supplied and controls the electromagnets accordingly via electrical lines 76, 77, 78 and 79.
  • a lowering pressure of, for example, 50 bar is specified on the control element 71 for the rod-side cylinder chamber 14.
  • the ratio k between the lifting-side effective area and the lowering-side effective area on the piston 11 of the working cylinder 10 is 1.25.
  • the raised plough is supposed to generate a lifting pressure of, for example, 200 bar in the bottom-side cylinder chamber 13. This lifting pressure therefore prevails in the bottom-side cylinder chamber 13 when there is no pressure in the rod-side cylinder chamber.
  • the electronic control unit 70 continuously determines an equivalent lowering pressure by forming the difference between the lifting pressure (DS carrying) multiplied by k and recorded by the pressure sensor 19 as the minuend and the lowering pressure (DS pressing) recorded by the pressure sensor 20 as the subtrahend.
  • the equivalent lowering pressure is therefore 200 bar times 1.25 - 0, equal to 250 bar.
  • the calculated equivalent lowering pressures are filtered using a low-pass filter (filter (low-pass)).
  • a pressure value is determined as the difference between the target pressure on the lowering side specified using the control element 71 and transmitted to the control unit 70 and stored there as the minuend and the equivalent lowering pressure as the subtrahend. If the equivalent lowering pressure is negative, a value of 0 is assumed for the equivalent lowering pressure to determine the pressure value. In this case, the equivalent lowering pressure is 250 bar. The pressure value is therefore 50 bar minus 250 equals minus 200 bar. However, the fact that the pressure value is negative means that the lifting gear is still supporting the plow. This information is processed in the electronic control unit 70. Accordingly, the electronic control unit 70 does not control the pressure control valve 35, so that it is set to the smallest setting value.
  • the electronic control unit begins to control the pressure control valve 35 with a control signal greater than zero when the bearing pressure has dropped to 40 bar. From this point on, the control signal for the pressure control valve 35 (static DRV setpoint) increases to the setpoint of 50 bar.
  • the procedure according to Figure 2 can be supplemented by a volume flow compensation, as shown in two alternatives in the Figures 3 and 4 is shown.
  • the volume flow is multiplied by a proportionality factor (P-Gain), especially during lifting, whereby a correction value for a pressure is determined.
  • the correction value is subtracted from the static setpoint for the pressure control valve (static DRV setpoint). If the difference is positive, it is equal to a dynamic setpoint for the pressure control valve 35 during lifting.
  • the volume flow that is displaced from the rod-side cylinder chamber 14 during lifting can be determined from the control signal for the electrohydraulic lifting valve arrangement, which is a measure of the amount of pressure medium flowing into the cylinder chamber 13, and the area ratio k of the working cylinder 10.
  • the signal of the position sensor 18 is derived over time and multiplied by a proportionality factor (P-Gain).
  • P-Gain proportionality factor
  • the difference is formed between the static setpoint for the pressure control valve and a correction pressure corresponding to the volume flow, whereby only negative correction values are taken into account due to the opposite flow direction of the pressure medium compared to the lifting.
  • the difference is equal to the dynamic setpoint of the control signal for the pressure control valve 35 when lowering.
  • pMax maximum pressure

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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 (12)

  1. Procédé de commande d'une pression d'abaissement d'un levage assisté électrohydraulique, qui présente au moins un cylindre de travail (10) avec un piston (11), avec un côté de levage (13), que le piston (11) délimite par une surface active (15) du côté du levage, auquel est amené un fluide sous pression pour le levage d'une charge et dans lequel une pression de levage est présente, et avec un côté d'abaissement (14), que le piston (10) délimite par une surface active (16) du côté de l'abaissement, auquel est amené un fluide sous pression pour abaisser une charge et dans lequel la pression d'abaissement est présente, un premier capteur de pression (19) pour détecter la pression de levage et un deuxième capteur de pression (20) pour détecter la pression d'abaissement, une soupape de pression réglable (35) pour régler une pression d'abaissement et une unité de commande électronique (70) à laquelle sont amenées les pressions détectées par les capteurs de pression (19, 20) et par laquelle la soupape de pression (35) peut être commandée,
    caractérisé par les étapes suivantes :
    la détermination en cours d'une pression d'abaissement équivalente en formant la différence entre la pression de levage multipliée par k en tant que diminuende et la pression d'abaissement en tant que diminuteur dans l'unité de commande électronique (70), k étant le rapport entre la taille de la surface active du côté du levage (15) et la taille de la surface active du côté de l'abaissement (16) du piston (11) ;
    la formation d'une valeur de pression en tant que différence entre une pression de consigne réglée sur l'appareil de commande électronique (70) du côté de l'abaissement en tant que diminuende et la pression d'abaissement équivalente en tant que diminuteur ;
    la commande de la soupape de pression (35) avec un signal de commande correspondant à la valeur de pression.
  2. Procédé selon la revendication 1, dans lequel, pour la formation de la valeur de pression, la pression d'abaissement équivalente est fixée à zéro si la détermination courante de la pression d'abaissement équivalente donne une valeur négative.
  3. Procédé selon la revendication 1 ou 2, dans lequel la soupape de pression (35) est commandée en fonction de la pression la plus faible pouvant être réglée sur celle-ci lorsqu'il en résulte une valeur de pression négative.
  4. Procédé selon une revendication précédente, dans lequel la pression d'abaissement équivalente est atténuée par un filtre électronique.
  5. Procédé selon une revendication précédente, dans lequel, pour compenser une chute de pression due au débit volumique entre la soupape de pression (35) et le côté d'abaissement, le signal de commande pour la soupape de pression (35) est augmenté ou diminué en fonction du débit volumique actuel et de son signe.
  6. Procédé selon la revendication 5, dans lequel le signal de commande pour la soupape de pression (35) est augmenté ou diminué selon une courbe caractéristique.
  7. Procédé selon la revendication 5 ou 6, dans lequel un distributeur LS (60) compensé en charge peut être relié au côté de levage (13) du cylindre de travail (10) et un débit volumique s'écoulant entre la soupape de pression (35) et le côté d'abaissement (14) du cylindre de travail (10), notamment un débit volumique s'éloignant du côté d'abaissement, est déterminé par le biais du signal de commande avec lequel le distributeur LS (60) est commandé.
  8. Procédé selon la revendication 5, 6 ou 7, dans lequel un débit volumique s'écoulant entre la soupape de pression (35) et le côté d'abaissement (14) du cylindre de travail (10) est déterminé par le biais de la dérivation du signal d'un capteur de position (18) associé au cylindre de travail (10).
  9. Procédé selon une revendication précédente, dans lequel différentes pressions de consigne sont prédéfinies par l'appareil de commande électronique (70) en fonction du signe et/ou du montant de la pression d'abaissement équivalente déterminée.
  10. Procédé selon une revendication précédente, dans lequel une soupape d'arrêt (45) est agencée entre la soupape de pression (35) et le côté d'abaissement (14) du cylindre de travail (10) et dans lequel du fluide sous pression peut être évacué du côté d'abaissement (14) du cylindre de travail (10) en contournant la soupape de pression (35) par le biais d'une soupape de décharge (50) et dans lequel la soupape d'arrêt (45) est fermée et la soupape de décharge (50) est ouverte, lorsque le débit volumique de consigne vers le côté de levage (13) et donc la vitesse de consigne pour un levage dépasse une certaine valeur et que la valeur de pression est inférieure à une certaine valeur.
  11. Procédé selon une revendication précédente, dans lequel la soupape de pression (35) est une soupape de régulation de pression.
  12. Levage assisté électrohydraulique, qui présente au moins un cylindre de travail (10) avec un piston (11), avec un côté de levage (13) que le piston (11) délimite par une surface active (15) du côté du levage, auquel un fluide sous pression est amené pour le levage d'une charge et dans lequel une pression de levage est présente, et avec un côté d'abaissement (14) que le piston (10) délimite par une surface active (16) du côté de l'abaissement, auquel un fluide sous pression est amené pour l'abaissement d'une charge et dans lequel la pression d'abaissement est présente, un premier capteur de pression (19) pour détecter la pression de levage et un deuxième capteur de pression (20) pour détecter la pression d'abaissement, une soupape de pression réglable (35) pour régler une pression d'abaissement et une unité de commande électronique (70) à laquelle sont amenées les pressions détectées par les capteurs de pression (19, 20) et par laquelle la soupape de pression (35) peut être commandée, caractérisé en ce que l'unité de commande électronique (70) est configurée pour exécuter un procédé selon l'une quelconque des revendications 1 à 11.
EP19158718.7A 2018-02-27 2019-02-22 Procédé de commande d'une pression de descente d'un levage assisté électrohydraulique et levage électrohydraulique Active EP3530962B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018202899 2018-02-27
DE102018204568.2A DE102018204568A1 (de) 2018-02-27 2018-03-26 Verfahren zur Steuerung eines Senkendrucks eines elektrohydraulischen Krafthebers und elektrohydraulischer Kraftheber

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EP3530962A1 EP3530962A1 (fr) 2019-08-28
EP3530962B1 true EP3530962B1 (fr) 2024-05-29

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DE102021002610A1 (de) * 2021-05-18 2022-11-24 Hydac Mobilhydraulik Gmbh Fahrbare Arbeitsmaschine

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DE10138389A1 (de) 2001-08-04 2003-02-20 Bosch Gmbh Robert Elektrohydraulische Einrichtung zur Steuerung eines doppelt wirkenden Motors
GB201319154D0 (en) 2013-10-30 2013-12-11 Agco Int Gmbh Hydraulic system supply
US10321621B2 (en) * 2016-08-11 2019-06-18 Deere & Company Electronic latching circuit

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