EP2251299B1 - Accumulateur d'énergie sous pression - Google Patents

Accumulateur d'énergie sous pression Download PDF

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Publication number
EP2251299B1
EP2251299B1 EP20090006610 EP09006610A EP2251299B1 EP 2251299 B1 EP2251299 B1 EP 2251299B1 EP 20090006610 EP20090006610 EP 20090006610 EP 09006610 A EP09006610 A EP 09006610A EP 2251299 B1 EP2251299 B1 EP 2251299B1
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EP
European Patent Office
Prior art keywords
hydraulic
pressure
hydraulic motor
valve
way
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.)
Not-in-force
Application number
EP20090006610
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German (de)
English (en)
Other versions
EP2251299A1 (fr
Inventor
Recept Macit
Christoph Stönner
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.)
Hawe Hydraulik SE
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Hawe Hydraulik SE
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Publication date
Application filed by Hawe Hydraulik SE filed Critical Hawe Hydraulik SE
Priority to EP20090006610 priority Critical patent/EP2251299B1/fr
Publication of EP2251299A1 publication Critical patent/EP2251299A1/fr
Application granted granted Critical
Publication of EP2251299B1 publication Critical patent/EP2251299B1/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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/004—Fluid pressure supply failure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/20—Means for actuating or controlling masts, platforms, or forks
    • B66F9/22—Hydraulic devices or systems
    • 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
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • 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
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • 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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/863—Control during or prevention of abnormal conditions the abnormal condition being a hydraulic or pneumatic failure
    • F15B2211/8633—Pressure source supply failure
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/875—Control measures for coping with failures
    • F15B2211/8752—Emergency operation mode, e.g. fail-safe operation mode

Definitions

  • the present invention relates to an apparatus and a method for providing a pressure reserve in a hydraulic system.
  • hydraulic accumulators are provided, in which hydraulic energy is stored, which is also available when no drive energy is available, so that an emergency operation is ensured. Furthermore, such a hydraulic accumulator allows a faster cold start of the system, as immediately after the start of the vehicle hydraulic energy for steering and braking is available. This means that pressure does not have to be built up by the pump until the system is started.
  • Such a hydraulic system is for example from the US 2008/0152513 known.
  • FIG. 1 shows an example of a hydraulic system in a vehicle, for.
  • a forklift which is equipped with such a hydraulic accumulator S.
  • FIG. 1 shows a hydraulic power source 70 and various hydraulic consumers 10, 20, 40, 50, 60 and 80, which are powered by the hydraulic power source 70 with drive energy.
  • Hydraulic consumers may be, for example, a service brake 60, a parking brake 40, a battery lock 50, and various work units 10, 20 and 80.
  • lifting units 10 and tilting units 20 can be provided as working elements in a forklift.
  • the working elements are realized with hydraulic cylinders 83, 10-1, 10-2, 20-1 and 20-2, so-called linear motors.
  • the cylinders 10-1, 10-2, 20-1 and 20-2 are controlled via 4/3-way valves 11, 21 and 22.
  • double acting cylinders 10-1 and 10-2 are often used in combination with a load holding valve block 12 each having one load holding valve 12-1 and 12-2 for each working chamber of the double acting cylinder.
  • a proportional 4/3 way spool valve 11 is often used to control the lift cylinders 10-1 and 10-2 for flow control of the fluid material.
  • the hydraulic system can also plunger cylinder 83, the z. B. used for damping include, which may optionally be used with required flow control devices 82 and other protective devices such as pressure relief valves 81 and line breakages LB.
  • FIG. 1 Other elements in the hydraulic state-of-the-art system according to FIG. 1 are a service brake 60 with inlet and outlet control elements 61 and 62, a battery lock 50 with control valve 51 and a parking brake 40 with associated controls 41, 42 and 43.
  • a hand pump 30 z. B. for Notbehellung the hydraulic accumulator S may be part of the hydraulic system.
  • the hydraulic consumers 10, 20, 40, 50, 60 and 80 are supplied by the pump unit 70 via the pressure line P with pressure energy.
  • the memory S is charged via the pressure control valve 41.
  • the hydraulic consumers 40, 50 and 60 are supplied from the memory S with pressure.
  • the remaining hydraulic consumers 10, 20 and 80 are separated via the check valve 42 from the pressure supply through the memory S, so that only safety-related systems are supplied with pressure and no pressure energy is wasted.
  • a hydraulic accumulator pressure vessels which store a liquid under pressure and thus can deliver hydraulic energy.
  • a hydraulic fluid is forced under pressure into a pressure vessel filled with gas, usually nitrogen.
  • the hydraulic fluid compresses the gas and is available as stored energy at a later time.
  • the Gas and the hydraulic fluid are separated by a separator, z.
  • a separator As a membrane, separated from each other.
  • hydraulic accumulators require space and requires in mobile technology, eg. B. when used in commercial vehicles, due to the additional weight more drive energy.
  • the object is achieved by a device for providing a pressure reserve according to claim 1.
  • Such a device has at least one hydraulic motor for use as a lifting drive, wherein a hydraulic connection of the at least one hydraulic motor via a respective valve arrangement with at least one hydraulic consumer is connected leak-free.
  • a hydraulic connection of the at least one hydraulic motor via a respective valve arrangement with at least one hydraulic consumer is connected leak-free.
  • the apparatus further includes a controller adapted to move the hydraulic motor to a biased position before the controller is shut down or placed in an idle state. Since the hydraulic motor is used as a lifting drive, a pressure reserve is only available when the lifting device is in a raised position, since only then usable potential energy is stored.
  • the control device causes the lifting drive to be in a raised position before the system is switched off or before the system is put into a resting state moves. As a result, pressure energy is available immediately when starting the commercial vehicle. For example, immediately after starting the battery can be unlocked and the system can be braked or steered. The pressure does not have to be built up by the pump first.
  • the hydraulic motor for use as a lifting drive is a lifting cylinder.
  • a cylinder as a linear actuator represents the simplest possible realization of such a linear actuator, although other linear actuators are conceivable.
  • a rotary motor capable of lifting a load such as a cable winch would be possible.
  • the apparatus further comprises a control device which is designed so that it drives the lifting cylinder in a raised position before the control device is switched off or put into a resting state.
  • a lifting cylinder corresponds to the raised position of a biased position. This ensures that even after switching off the system stored pressure energy is available.
  • the hydraulic consumer is a hydraulic steering and / or a hydraulic brake.
  • these two hydraulic consumers are the most important components for an emergency operation, so that the vehicle remains steerable and brakable even if the pump fails.
  • the valve assembly comprises an electrically actuated multiway seat valve with additional possibility for Manual operation. Since the valve assembly should be largely leak-free and to handle the complex switching operations when switching between a normal operation of the hydraulic system and an emergency operation, the use of a Mehrwegesitzventil represents the most rational and cost-effective implementation of such a valve assembly, since standard multiway seat valves from manufacturer catalogs are used and no Special solutions are needed. In the course of automation, the multi-way seat valve is electrically actuated. In order to ensure emergency operation of the hydraulic system even in the event of a power failure, the multi-way seat valve is additionally manually operable, so that the pressure reserve can be used even in the event of a power failure.
  • the hydraulic brake is designed so that it brakes in the unpressurized state
  • the valve arrangement between the hydraulic brake and the lifting cylinder comprises a 3/2-way seat valve with spring bias, which connects a brake cylinder with a return line in the valve resting state and a connection between the brake cylinder and pressure supply (pressure line or pressure reserve) interrupts, wherein the 3/2-way seat valve is electrically actuated and energized in normal operation (ie not in the idle state).
  • the 3/2-way seat valve In normal operation, when the 3/2-way seat valve is energized, the 3/2-way seat valve establishes a connection between the pressure supply and the brake cylinder, so that the brake cylinder is under pressure and the brake does not brake. In the event of a power failure, the 3/2-way seat valve switches to the idle state, so that the brake cylinder is relieved into the return line and the brake is activated.
  • This configuration therefore fulfills the safety function that automatically brakes the vehicle in the event of a power failure.
  • fluid communication between the 3/2-way seated valve and the pressure supply splits into a first branch and a second branch, the first branch fluidly communicating with the pressure line via a first check valve which blocks toward the pressure line. and wherein the second branch provides fluid communication with the hydraulic motor for use as a lift actuator via a second check valve which blocks in the direction of the hydraulic motor.
  • the poppet valve assembly between the hydraulic steering and the lifting cylinder is arranged and includes a 2/2 way poppet valve which locks in the idle state, the 2/2 way poppet valve electrically actuated and de-energized in normal operation (ie at rest) is.
  • the 2/2-way seat valve Through the 2/2-way seat valve, the pressure reserve in the lift cylinder is separated from the steering unit.
  • the complete separation of the steering unit from the lifting cylinder during normal operation has the advantage that steering movements can not react on the lifting cylinder.
  • the 2/2-way seat valve is therefore designed so that it interrupts the connection between the lifting cylinder and steering unit and is de-energized in the idle state. In emergency operation, the 2/2-way seat valve must be operated electrically or manually, so that the vehicle remains steerable via the pressure reserve in the lifting cylinder, even if the pressure supplies in the pressure supply line fails.
  • the lifting cylinder has a device for detecting a position of a piston in the lifting cylinder, and / or the hydraulic motor has a device for detecting a pressure in the hydraulic motor.
  • the control device can better regulate the pressure reserve from the lifting cylinder.
  • a method for providing a pressure reserve in a hydraulic system comprises the leak-free connection of a hydraulic motor, which is used as a lifting drive, to a hydraulic system, and the provision of a leak-free connection of the hydraulic motor to at least one hydraulic consumer.
  • the leak-free connection of a hydraulic motor which is used as a lifting drive, has the advantage that in the idle state or in the off state, the pressure energy stored in the hydraulic motor is maintained.
  • the method further includes biasing the hydraulic motor prior to shutting down the hydraulic system. As a result, pressure is immediately available to brake, steer or unlatch the battery as soon as the system is turned on, accelerating a cold start.
  • a control device monitors a pressure in the hydraulic motor and controls it so that it does not fall below a predetermined value in a normal situation. It is thereby achieved that, as a rule, pressure energy always remains stored in the hydraulic motor in order to provide a pressure reserve if the pump suddenly fails.
  • the control device controls the pressure in the hydraulic motor so that it can be lowered in an exceptional situation below the predetermined value, wherein the exceptional situation may be a vehicle standstill with active hydraulics.
  • the exceptional situation may be a vehicle standstill with active hydraulics.
  • the hydraulic motor is a lifting cylinder and the control device moves the lifting cylinder to a raised position before the control device is switched off or put into a resting state.
  • FIG. 2 shown embodiment of the present invention shows a part of a hydraulic system with a steering unit 100, a lifting unit 200 and a brake unit 300.
  • Each of the units 100, 200 and 300 is the input side to a pressure line P and a return line R connected, and is the output side with a hydraulic Consumers, eg. Hydraulic cylinders 100-1, 200-1 and 300-1.
  • the pressure line P and the return line R are realized as BUS lines to which a variety of consumers 100, 200 and 300 can be connected in parallel.
  • the steering control unit 100 is fluidly connected to a steering drive unit 100-1 or 100-2 through the fluid lines Li and Re.
  • the steering control unit 100 is further connected to the pressure line P and the return line R.
  • the steering control unit 100 connects due to steering control signals from a steering wheel, the pressure line P with one of the two working lines Li or Re and connects the other working line Li or Re to the return line R.
  • the steering control unit 100 also has a connection for an emergency operating line X by a check valve 101 is separated from the pressure line P, which blocks in the direction of the pressure line P. By the emergency operating line X, the steering can be supplied with pressure when the pressure on the pressure line P should be too low to operate the steering.
  • a double-acting constant velocity cylinder 100-1 or a rotary motor 100-2 can be used as a steering drive z. B.
  • a double-acting constant velocity cylinder 100-1 or a rotary motor 100-2 can be used as a steering drive z. B.
  • the brake control unit 300 is connected on the input side to the pressure line P and the return line R. On the output side, the brake control unit 300 is connected via the working line FS to the brake cylinder 300-1.
  • a single-acting cylinder with a spring that pushes the piston rod out of the cylinder is shown. If pressure medium flows via the working line FS into the brake cylinder 300-1, the piston rod of the brake cylinder 300-1 retracts into the cylinder and compresses the spring.
  • the in FIG. 2 shown brake cylinder 300-1 can therefore develop its braking force in the unpressurized state.
  • brake can z. B. be used as a parking brake.
  • the brake cylinder 300-1 is driven by a 3/2-way seat valve 303.
  • the 3/2-way seat valve 303 has three fluid ports connected to the pressure line P, to the return line R and to the working line FS.
  • the pressure line P is connected to the working line FS. Therefore, in the position A, pressure fluid flows into the working chamber of the brake cylinder 300-1, and the piston rod of the brake cylinder 300-1 retracts into the cylinder. The brake is deactivated and the vehicle can be moved without hindrance.
  • position B the working line FS is connected to the return line R.
  • the 3/2-way seat valve 303 is held by a spring at rest in the B position. That is, pressure fluid can flow from the brake cylinder 300-1 in the return line and the vehicle brakes in this position. If the vehicle is to be moved normally, the electromagnet M2 of the 3/2-way seat valve must be energized so that the valve goes to position A and pressure medium can flow into the brake cylinder 300-1. In order to be able to set the vehicle in motion during a power failure, the 3/2-way seat valve 303 is manually operated, so that the valve 303 can be switched by hand in position A and thus the brake can be unlocked.
  • the embodiment shown also shows a pressure switch 304 in the brake control unit 300.
  • a pressure switch 304 By the pressure switch 304, an electrical signal can be generated which indicates whether the brake is active or not active.
  • the pressure switch 304 may also serve as a pressure monitoring system by which a failure of a pump can be detected, whereby an emergency operation can be triggered.
  • FIG. 2 shows as a further consumer a lifting cylinder 200-1, the z. B. can be used in a forklift as a linear actuator.
  • the lifting cylinder 200-1 is connected to the stroke control device 200 via the working line H.
  • the stroke control device 200 connects the working chamber of the lifting cylinder 200-1 either with the pressure line P or with the return line R.
  • the control of the lifting cylinder 200-1 via the valve block 205 via which can be specified whether pressure medium in the working chamber of the lifting cylinder 200-. 1 flows from the pressure line or whether pressure fluid is discharged from the working chamber of the lifting cylinder 200-1 in the return line R, or as a third possibility that the stroke position is held.
  • 4/3-way valves are used to control lifting cylinders.
  • connection unit 210 and 310 are on one side with the working line H to the lifting cylinder 200-1 and on the other side with the steering control unit 100th It should be noted that the connections to the steering control unit 100 and the brake control unit 300 with respect to the pressure line P are secured with check valves 101 and 302, so that a pressure drop of the pressure reserve in the lifting cylinder 200-1 in the pressure line P. can. That is, the check valves 101 and 302 lock in the direction of pressure line P.
  • the connections 210 and 310 can be realized in a simple manner by a check valve which locks in the direction of working line H, as shown in the connection unit 310 by way of example.
  • a better separation of the components is achieved via a 2/2-way valve seat 203, as shown by way of example in the connection unit 210.
  • the 2/2-way seat valve 203 is in the rest position due to the spring force of a spring in position B.
  • the connection between the working line H and the steering control unit 100 is interrupted.
  • the lifting cylinder 200-1 is fluidly connected to the steering control unit 100, so that stored pressure energy can be used in the lifting cylinder 200-1 for steering.
  • the valve 203 can be brought into position A by manual operation or by energizing the solenoid M1.
  • connection unit 210 Since in normal operation steering movements stress the pressure line E more than the operation of the brake, it is better to realize the connection unit 210 through the 2/2-way seat valve, which allows a better separation of the steering cylinder 100-1 and the lifting cylinder 200-1. On the other hand, due to the lower load on the pressure line P through the brake cylinder 300-1, a simple check valve 301 for the connection unit 310 is sufficient and less expensive.
  • the valve block 205 for controlling the lifting movement of the lifting cylinder 200-1 can be realized in various ways. Depending on whether single-acting or Double-acting cylinders can be used as lifting cylinders, 4/3-way valves or 3/3-way valves with additional load-holding devices can be used. In any case, care should be taken that leakage losses are low to maintain a stored pressure in the lift cylinder 200-1.
  • the valve block 205 may consist of a combination of a 3/2-way seat valve analogous to the valve 303 in the brake control unit 300 and a check valve which is arranged between the pressure line P and the 3/2-way seat valve.
  • the 3/2-way seat valve 303 is energized and the 2/2-way seat valve 203 is not energized.
  • the brake is released because the brake cylinder 300-1 is under pressure, and the connection between the working line H and the steering control unit 100 is interrupted. That is, the steering and the brake are supplied exclusively via the pressure line P.
  • the pressure in the pressure line P decreases and the steering stops, since no more pressure is available for the operation of the steering drive 100-1 or 100-2.
  • a control device ensures that the piston of the lifting cylinder 200-1 does not fall below a certain height X1, which is detected by a position detector 201, so that there is always a pressure reserve.
  • the control device determines that the pressure in the pressure line P drops below a certain value, the control device energizes the 2/2-way seat valve 203 and establishes a connection between the working line H and the steering control unit 100.
  • the pressure reserve in the lifting cylinder 200-1 can thereby be used for steering.
  • the pressure reserve in the lift cylinder 200-1 maintains the pressure in the brake cylinder 300-1 via the connection unit 310, since the 3/2-way seat valve 303 is constantly supplied with power and is in position A.
  • a pressure sensor 202 may also be used.
  • the 3/2-way seat valve 303 switches to the idle state B, whereby the brake cylinder 300-1 is depressurized and the vehicle brakes automatically as a safety device.
  • the vehicle in a safe end position bring the valves 203 and 303 can be manually operated in the position A, so that the brake is unlocked and the steering can be operated.
  • control device monitors that as far as possible a pressure reserve and thus a minimum stroke of the lifting cylinder 200-1 is present, but the forklift may need to lower the fork to the end position X0, such a case should be programmed as an exceptional situation.
  • the controller should raise the lifting cylinder before switching off the system. Since the lifting cylinder is advantageously connected via seat valve combinations with the rest of the hydraulic system, pressure losses are kept low by leakage and the system can start faster after longer periods, as there is immediate pressure in the system.
  • valve combinations represent only examples of possible realizations of the desired functions and can be realized otherwise.
  • valves shown represent a simple and inexpensive realization of the desired functions.

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  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Civil Engineering (AREA)
  • Transportation (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Physics & Mathematics (AREA)
  • Combustion & Propulsion (AREA)
  • Analytical Chemistry (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)

Claims (13)

  1. Dispositif destiné à fournir une réserve de pression dans un système hydraulique, comprenant :
    au moins un moteur hydraulique (200-1) pour l'utilisation en tant que commande de levage ;
    un raccordement hydraulique dudit au moins un moteur hydraulique relié sans fuites à au moins un consommateur hydraulique (100-1, 100-2, 300-1) par l'intermédiaire de respectivement un agencement de soupape à siège (203, 303, 301),
    caractérisé par
    un dispositif de commande, qui est conçu de sorte qu'il amène le moteur hydraulique (200-1) dans une position de précontrainte, avant que le dispositif de commande ne soit déconnecté ou amené dans un état de repos.
  2. Dispositif selon la revendication 1, dans lequel le moteur hydraulique est un cylindre de levage (200-1).
  3. Dispositif selon la revendication 2, dans lequel le dispositif de commande est conçu de sorte qu'il amène le cylindre de levage (200-1) dans une position de levée, avant que le dispositif de commande ne soit déconnecté ou amené dans un état de repos.
  4. Dispositif selon l'une des revendications 1 à 3, dans lequel le consommateur hydraulique est une direction hydraulique (100-1, 100-2) et/ou un frein hydraulique (300-1).
  5. Dispositif selon l'une des revendications 1 à 4, dans lequel l'agencement de soupapes (203, 303) comprend une soupape à siège à plusieurs voies (203, 303) actionnable aussi bien électriquement que manuellement.
  6. Dispositif selon l'une des revendications 4 et 4 et 5, dans lequel le frein hydraulique (300-1) est conçu de sorte qu'il freine dans l'état sans pression, et
    dans lequel l'agencement de soupape (303) comprend entre le frein hydraulique (300-1) et le moteur hydraulique (200-1), pour l'utilisation en tant que commande de levage, une soupape à siège à 3/2 voies avec précontrainte de ressort, qui relie dans l'état de repos un cylindre de freinage (300-1) à une conduite de retour (R) et coupe une liaison entre le cylindre de freinage (300-1) et une alimentation en pression (R, 200-1), la soupape à siège à 3/2 voies (303) étant actionnable électriquement et alimentée en courant en service normal.
  7. Dispositif selon la revendication 6, dans lequel une liaison fluidique entre la soupape à siège à 3/2 voies et l'alimentation en pression (P, 201-1) se partage en une première branche et en une seconde branche, la première branche créant une liaison fluidique avec la conduite sous pression (P) par l'intermédiaire d'une première soupape anti-retour, qui ferme en direction de la conduite sous pression (P), et la seconde branche créant une liaison fluidique avec le moteur hydraulique (200-1), pour l'utilisation en tant que commande de levage, par l'intermédiaire d'une seconde soupape anti-retour, qui ferme en direction du moteur hydraulique (200-1).
  8. Dispositif selon la revendication 4 et l'une des revendications 5, 6 et 7, dans lequel l'agencement de soupape à siège (203) est disposé entre la direction hydraulique (100-1, 100-2) et le cylindre de levage (200-1) et comprend une soupape à siège à 2/2 voies, qui ferme dans l'état de repos, la soupape à siège à 2/2 voies (203) étant actionnable électriquement et sans courant en service normal.
  9. Dispositif selon l'une des revendications 2 à 7, dans lequel le cylindre de levage (200-1) présente un dispositif (201) pour détecter une position d'un piston dans le cylindre de levage (200-1) et/ou dans lequel le moteur hydraulique (200-1) présente un dispositif (202) pour détecter une pression dans le moteur hydraulique (200-1).
  10. Procédé destiné à fournir une réserve de pression dans un système hydraulique, comprenant :
    le raccordement sans fuite d'un moteur hydraulique (200-1), utilisé en tant que commande de levage, à un système hydraulique ;
    la préparation d'une liaison sans fuite du moteur hydraulique (200-1) à au moins un consommateur hydraulique (100-1, 100-2, 300-1) ; et
    la précontrainte du moteur hydraulique (200-1) avant la coupure du système hydraulique.
  11. Procédé selon la revendication 10, dans lequel un dispositif de commande surveille une pression dans le moteur hydraulique (200-1) et la contrôle de sorte qu'elle ne chute pas, dans une situation normale, au-dessous d'une valeur prédéfinie.
  12. Procédé selon la revendication 11, dans lequel le dispositif de commande contrôle la pression dans le moteur hydraulique (200-1) de sorte qu'elle peut être abaissée, dans une situation d'exception, au-dessous de la valeur prédéfinie, la situation d'exception pouvant être un arrêt du véhicule en présence d'une hydraulique active.
  13. Procédé selon l'une des revendications 10 à 12, dans lequel le moteur hydraulique (200-1) est un cylindre de levage (200-1), et dans lequel un dispositif de commande amène le cylindre de levage dans une position de levée, avant que le dispositif de commande ne soit déconnecté ou amené dans un état de repos.
EP20090006610 2009-05-15 2009-05-15 Accumulateur d'énergie sous pression Not-in-force EP2251299B1 (fr)

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EP2251299B1 true EP2251299B1 (fr) 2012-09-12

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112805440B (zh) * 2018-10-02 2023-03-14 沃尔沃建筑设备公司 用于控制建筑设备的工作单元的装置
CN109488662A (zh) * 2018-12-07 2019-03-19 浙江鼎诚炉业科技有限公司 一种步进加热炉液压控制系统
CN113586557B (zh) * 2021-07-23 2023-11-17 三一汽车制造有限公司 泵送车辆的臂架控制方法、装置、系统及泵送车辆

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3710776A1 (de) * 1987-03-31 1988-10-20 Jungheinrich Kg Gabelhubwagen mit einem lenkbaren antriebsteil und einem an diesem gefuehrten hoehenbeweglichen lastteil
DE3614986A1 (de) * 1986-05-02 1987-11-05 Jungheinrich Kg Gabelhubwagen mit einem lenkbaren antriebsteil und einem hoehenbeweglichen lastteil
JPH0228500A (ja) * 1988-07-13 1990-01-30 Toyota Autom Loom Works Ltd バッテリ式産業車両における油圧装置
DE19721739A1 (de) * 1997-05-24 1998-11-26 Mannesmann Rexroth Ag Hydraulische Steueranordnung, insbesondere für einen Gabelstapler
JP2006117406A (ja) * 2004-10-22 2006-05-11 Mitsubishi Heavy Ind Ltd バッテリ式産業車両の液圧装置
DE102006060351B8 (de) * 2006-12-20 2008-07-24 Sauer-Danfoss Gmbh & Co Ohg Hydraulische Schaltungsanordnung mit Energierückgewinnung

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