EP3601805B1 - Dispositif de régulation d'une machine hydraulique - Google Patents

Dispositif de régulation d'une machine hydraulique Download PDF

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Publication number
EP3601805B1
EP3601805B1 EP18705117.2A EP18705117A EP3601805B1 EP 3601805 B1 EP3601805 B1 EP 3601805B1 EP 18705117 A EP18705117 A EP 18705117A EP 3601805 B1 EP3601805 B1 EP 3601805B1
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EP
European Patent Office
Prior art keywords
hydraulic cylinder
line
pump
hydraulic
collecting
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Application number
EP18705117.2A
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German (de)
English (en)
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EP3601805A1 (fr
Inventor
Thomas Zeller
Rouven Hohage
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Voith Patent GmbH
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Voith Patent GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/022—Installations or systems with accumulators used as an emergency power source, e.g. in case of pump 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—Systems with load-holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • 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
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • 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
    • F15B2211/20538—Type of pump constant 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
    • F15B2211/20—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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—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
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • 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
    • F15B2211/27—Directional control by means of the pressure source
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B2211/3057—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 having two valves, one for each port of a double-acting output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3138—Directional control characterised by the positions of the valve element the positions being discrete
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/31523—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member
    • F15B2211/31535—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member having multiple pressure sources and a single output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/321—Directional control characterised by the type of actuation mechanically
    • F15B2211/322—Directional control characterised by the type of actuation mechanically actuated by biasing means, e.g. spring-actuated
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41572—Flow control characterised by the connections of the flow 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators
    • 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
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • 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
    • F15B2211/705—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
    • F15B2211/7054—Having equal piston areas
    • 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
    • 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
    • F15B2211/8755—Emergency shut-down

Definitions

  • the invention relates to a device for controlling a hydraulic machine, in particular a device for controlling a turbine, a pump or a pump turbine.
  • the DE 27 13 867 A1 such a device (see Figure 3), which comprises a pressure oil source, a hydraulic servomotor (hydraulic cylinder) and control valves for metering the energy for adjusting the hydraulic cylinder.
  • the pressurized oil source is a reservoir for the hydraulic medium which is under overpressure.
  • the storage tank must be filled with the help of pumps and brought to the required working pressure and maintained.
  • the object of the present invention is to provide a device for regulating a hydraulic machine in which variable-speed hydraulic fixed displacement pumps are used, and which meet the requirements of a hydraulic machine, e.g. with regard to setting times, emergency closing properties - even if the pumps fail, suitability for large hydraulic cylinders -Volumes etc., guaranteed.
  • the solution according to the invention is characterized by high energy efficiency, good environmental compatibility, ease of maintenance and low acquisition and operating costs.
  • this object is achieved by a device for controlling a hydraulic machine with the features of claim 1. Further advantageous refinements of the device according to the invention emerge from the dependent claims.
  • the device comprises a collecting and equalizing tank, which is labeled 1, a pump arrangement, which is labeled 2, a variable-speed pump drive, which is labeled 3, a memory, which is labeled 5, a hydraulic cylinder, which is labeled 6 is, an emergency shut-off valve, which is designated with 71, an emergency shut-off solenoid valve, which is designated with 72, two pilot operated check valves, which are designated with 81 and 82, two pilot valves, which are designated with 91 and 92, three throttles, which are designated with 10, 11 and 12, an optional solenoid valve, which is labeled 20, two optional pressure relief valves, which are labeled 30 and 31 and two optional connections, which are labeled 40 and 50.
  • the arrow below the hydraulic cylinder 6 indicates the closing direction of the same.
  • the hydraulic cylinder 6 can be, for example, the stator hydraulic cylinder or the hydraulic cylinder for adjusting the impeller blades of a hydraulic machine. Such hydraulic cylinders often require large volumes of hydraulic fluid to operate.
  • the hydraulic cylinder 6 can be made as a synchronous cylinder, as in Figure 1 by the dashed second Rod is indicated.
  • the hydraulic cylinder 6 can, however, also be designed as a differential cylinder with different volumes for the closing and opening sides.
  • the pump arrangement 2 comprises two pumps with a reversible delivery direction.
  • the two pumps are arranged on a shaft which is driven by the pump drive 3.
  • the pump drive 3 comprises a motor and a frequency converter for each of the two pumps.
  • One connection of a pump is connected to a control line of the hydraulic cylinder, so that one pump conveys hydraulic fluid in the direction of the hydraulic cylinder 6 and the other pump receives hydraulic fluid from the hydraulic cylinder 6 in one direction of rotation of the shaft. In the other direction of rotation of the shaft it is exactly the opposite.
  • the pressure connections are preferably always connected to the hydraulic cylinder 6 and the suction connections to the collecting and compensating tank 1.
  • the shaft of the pump arrangement 2 is driven by the variable-speed pump drive 3, which can be operated in both directions of rotation.
  • the pump drive 3 usually comprises an electric servomotor which is electrically fed by a frequency converter.
  • the releasable check valves 81 and 82 which are arranged in the connecting lines of the hydraulic cylinder 6 with the pump arrangement 2 in such a way that they prevent the piston of the hydraulic cylinder from moving in the unlocked state, are each connected to one of the pilot valves 91, 92. These are each connected to the memory 5 (via the valves 20 and 72). Opening a pilot valve 91, 92 thus unlocks the associated check valve 81, 82.
  • the opening of pilot valves 91, 92 is caused by the (electrical) controller of the hydraulic machine in that they are excited. Each of the pilot valves 91, 92 can be energized separately.
  • the accumulator 5 is connected to the closing side of the hydraulic cylinder 6.
  • the emergency shut-off valve 71 is connected to the opening side of the hydraulic cylinder 6 and the collecting and compensating tank 1 that a volume flow between the opening side of the hydraulic cylinder 6 and the collecting and Equalization tank 1 is only possible when the emergency valve 71 is open.
  • the state of the emergency shut-off valve 71 is controlled via the emergency shut-off solenoid valve 72, which is located in a hydraulic line between the emergency shut-off valve 71 and the accumulator 5.
  • the emergency shut-off solenoid valve 72 is also located in the lines between the pilot valves 91, 92 and the accumulator 5.
  • the (spring-loaded) emergency shut-off solenoid valve 72 is always excited during operation, whereby the emergency shut-off valve 71 is closed and the pilot valves 91, 92 through the accumulator 5 with oil pressure are supplied (ie the check valves 81, 82 can be unlocked in this state by the pilot valves 91, 92).
  • the throttle 10 which is also called the “basic throttle" is located in the line between the opening side of the hydraulic cylinder 8 and the check valve 81, but before the branch in this line to the emergency valve 71, ie in the immediate vicinity of the hydraulic cylinder 6
  • Throttle 11 is located in the line that connects the memory 5 with the rest of the device.
  • the throttle 12 is located in the line between the emergency shut-off valve 71 and the collecting and equalizing tank 1.
  • One of the two throttles 11 or 12 is to be regarded as optional (see the remarks on the emergency shut-off function).
  • the device can also include further emergency shut-off control valves (e.g. an overspeed valve, etc.). These can be connected via the connection 50, which is located in the same hydraulic line as the emergency shut-off solenoid valve 72.
  • further emergency shut-off control valves e.g. an overspeed valve, etc.
  • connection 40 is located in the hydraulic line which connects the reservoir 5 with the rest of the device.
  • the pilot solenoid valves 91, 92 controlled by the controller of the hydraulic machine are in the de-energized state.
  • the releasable check valves 81, 82 in the control lines to the opening or closing side of the hydraulic cylinder 6 are also closed and the cylinder 6 is held in its position without leakage.
  • the variable-speed drive 3 is switched off so that no energy loss (heat) is introduced into the system.
  • oil cooling can in principle be dispensed with, which offers the advantage of significantly better energy efficiency.
  • the pilot valves 91 and 92 are excited via the controller, which leads to the opening of the releasable check valves.
  • the hydraulic cylinder can now be positioned directly via the variable-speed pump drive 3. If the hydraulic cylinder 6 is designed as a synchronous cylinder, the same amount of oil is swallowed by the pump arrangement 2 on the suction side as is introduced into the cylinder on the pressure side. In this case, the two pumps of the pump arrangement 2 have identical delivery volumes.
  • the hydraulic cylinder 6 is made as a differential cylinder, the delivery volume ratio of the two pumps of the pump arrangement 2 is as accurate as possible to the Differential cylinder adapted.
  • the difference in oil quantity that occurs during the movement of the hydraulic cylinder 6 can be compensated for via the corresponding suction lines connected to the collecting and compensating container 1 or a small pendulum volume at the reservoir 5.
  • the oil volume and thus the pressure in the reservoir 5 remains largely constant and ensures that the entire system is preloaded.
  • the permanent pressure bias of the hydraulic cylinder 6 by the accumulator 5 has the advantage that the hydraulic cylinder 6 always remains firmly clamped in the defined position, regardless of e.g. a change in the direction of force of the external forces acting on the cylinder 6.
  • the pilot valves 91, 92 are de-energized, whereby the cylinder 6 can be held in its position again without applying energy. It should be mentioned that, in comparison with conventional systems, the storage volume is no longer used for control purposes, since this task is completely taken over by the pump arrangement 2. Thus the storage volume and thus the storage size can be drastically reduced. This also leads to a smaller collecting and equalizing container 1, which means that costs can be reduced overall.
  • an emergency shutdown function is implemented which allows the system to be shut down without a power supply (or in the event of a defect in the variable-speed drive 3).
  • the emergency shut-off solenoid valve 72 which is permanently excited during operation, is de-energized, whereupon the emergency shut-off valve 71 opens.
  • the "quasi-closed" hydraulic control circuit thus becomes an open circuit.
  • the memory 5 is with the The closing side of the hydraulic cylinder 6 is connected, the opening side now being diverted into the collecting and equalizing tank 1.
  • the memory 5 delivers a defined volume within defined pressure limits. Therefore, with the aid of the basic throttle 10 and an additional throttle 11 or 12 connected in series, a defined closing time can be reliably set. If two throttles 11 and 12 additionally connected in series are actually used, this results in greater flexibility and greater robustness against, for example, a line break in the line between the basic throttle 10 and the quick-acting valve 71, since the additional throttling effect is distributed over two throttles of which only one (12) fails due to the line break.
  • the basic throttle When the hydraulic cylinder 6 is moved, the basic throttle creates a dynamic pressure against which the pump arrangement 2 acts and which must therefore be kept within certain limits (nominal pressures of the lines and components to be maintained, output of the pump drive 3, etc.). An individual design of the individual throttles 10, 11, 12 is therefore necessary. It must be in the foreground that the greatest possible proportion of the total throttling effect and thus the closing time must always be implemented via the basic throttle 10.
  • the arrangement of the basic throttle 10 directly in the opening side of the hydraulic cylinder 6 ensures that the closing time is limited even in the event of a line break on the open control side (ie the line between the basic throttle 10 and the pump arrangement 2).
  • pressure limiting valves 30, 31 can optionally be installed on the opening and closing sides with respect to the hydraulic cylinder 6. It is clear that the pressure limiting valve 31 can also be integrated in the memory 5.
  • the memory 5 is monitored for its degree of filling or its system pressure by means of appropriate level and pressure sensors.
  • the oil volume and the pressure in the reservoir 5 are kept at a defined maximum level during operation, regardless of the position of the hydraulic cylinder 6. In the case of a synchronous cylinder being used (see above), or if no further external consumers are connected to the memory 5 via the optional connection point 40, this level will not change or change only very little during operation.
  • the memory can be charged during operation by means of the variable-speed drive 3 and the electrically controlled, releasable check valves 81 and 82, regardless of the position of the hydraulic cylinder 6.
  • the pilot solenoid valves 91 and 92 must be in the de-energized state, as a result of which the releasable check valves 81 and 82 are also closed.
  • the pump arrangement 2 is now activated in such a way that it conveys in the direction of the closing side of the hydraulic cylinder 6.
  • the position of the cylinder 6 does not change because the releasable check valve 81 in the open side of the hydraulic cylinder 6 is closed and therefore no oil can escape from the hydraulic cylinder 6.
  • flow can flow through the check valve 82, as a result of which the pressure increases and the accumulator 5 is “charged”.
  • the difference in oil quantity required for this is sucked in by the pump arrangement 2 from the collecting and equalizing tank 1 via a corresponding line.
  • the store loading function is active during normal operation and when the hydraulic machine is at a standstill. This ensures that there is always the appropriate safety for a possible emergency shutdown and that it is available as quickly as possible when the hydraulic machine is started.
  • the pump arrangement 2 is designed with regard to the size, speed and power of the pumps in such a way that they are suitable for the respective application Required opening and closing times of the hydraulic cylinder 6 can be moved solely via the pump drive 3.
  • the opening times may be significantly longer, they could be designed in this way in order to keep the dimensions of the pump arrangement 2 and the pump drive 3 as small as possible (space, spare parts costs, etc.) be that the hydraulic cylinder 6 can only be moved with the minimum opening time.
  • the quick-closing solenoid valve 20 is optionally provided, which is located in the same hydraulic line as the emergency closing solenoid valve 72. By connecting this valve 20, the storage volume can now be used to close.
  • the quick-closing solenoid valve 20 is excited, as a result of which the emergency-closing valve 71 opens.
  • the pressure supply to the pilot control valves 91 and 92 is hydraulically disconnected, so that the pilot operated check valves 81 and 82 in the control lines also close.
  • the pump arrangement 2 can now be controlled in the closing direction with the maximum delivery rate during this process.
  • the quick-closing valve 20 is de-energized again when a defined opening is reached. Simultaneously the "fine control" is now transferred back to the variable-speed pump drive 3, and the machine can be synchronized again.
  • the controller Since the controller is active during and after the synchronization process has been completed and the turbine has been restarted to the corresponding cylinder position and the pump arrangement 2 may therefore not be used to charge the accumulator 5, the following procedure can be used in this case: While the pump arrangement 2 moves the hydraulic cylinder 6 to the corresponding opening, the pilot solenoid valves 91 and 92 are in the de-energized state. The flow can thus flow through the open-side check valve 81, the close-side check valve 82 remains blocked. As a result, the oil displaced when opening is pressed from the hydraulic cylinder 6 directly back into the reservoir 5. The amount of oil required for this is sucked in by the pump arrangement 2 from the collecting and compensating tank 1 via the corresponding line. When the accumulator 5 has reached its nominal degree of filling, the corresponding check valves 81 and 82 are opened and the hydraulic cylinder 6 can be moved to its end position without further filling the accumulator 5.
  • the regulation is initiated via the pump arrangement 2 by opening the releasable check valves 81 and 82. This creates heat that is used to heat the system.

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

Claims (8)

  1. Dispositif de régulation d'une machine hydraulique, comportant un ensemble de pompage (2), un entraînement de pompe (3) à régime variable, un accumulateur (5), un cylindre hydraulique (6), une soupape de fermeture d'urgence (71), deux soupapes anti-retour (81, 82) pouvant être débloquées et deux soupapes pilotes (91, 92) pour le déblocage des soupapes anti-retour (81, 82), dans lequel l'ensemble de pompage (2) comporte deux pompes à sens de refoulement réversible, lesquelles sont reliées à l'entraînement de pompe (3) à régime variable de telle sorte que les pompes peuvent être entraînées par l'entraînement de pompe (3) dans les deux sens de refoulement, et le dispositif comporte en outre un récipient de collecte et de compensation (1), une électrovanne de fermeture d'urgence (72) et au moins deux étranglements (10, 11, 12), dans lequel un premier raccord de la première pompe est relié au côté d'ouverture du cylindre hydraulique et un premier raccord de la deuxième pompe est relié au côté de fermeture du cylindre hydraulique (6), et dans lequel les raccords restants des pompes sont reliés respectivement au récipient de collecte et de compensation (1), de telle sorte que, dans un sens d'entraînement de l'entraînement de pompe (3), la première pompe peut refouler du fluide hydraulique à partir du récipient de collecte et de compensation (1) en direction du cylindre hydraulique (6) et la deuxième pompe peut refouler du fluide hydraulique à partir de côtés du cylindre hydraulique (6) dans le récipient de collecte et de compensation (1), et dans lequel le récipient de collecte et de compensation (1) est relié au côté d'ouverture et l'accumulateur (5) est relié au côté de fermeture du cylindre hydraulique (6), et la soupape de fermeture d'urgence (71) est disposée dans la conduite entre le cylindre hydraulique (6) et le récipient de collecte et de compensation (1), et une soupape anti-retour (81, 82) pouvant être débloquée se trouve respectivement dans l'une des conduites allant des pompes jusqu'au cylindre hydraulique (6) et est orientée de telle sorte que, dans chaque état des soupapes anti-retour (81, 82), du fluide hydraulique peut passer en direction du cylindre hydraulique (6), et le dispositif comporte en outre des conduites, lesquelles relient l'accumulateur (5) respectivement aux deux soupapes anti-retour (81, 82) et à la soupape de fermeture d'urgence (71), afin de pouvoir débloquer les soupapes anti-retour (81, 82) et de pouvoir fermer la soupape de fermeture d'urgence (71), dans lequel ces conduites forment, au moins sur un tronçon, une conduite unique, tronçon dans lequel l'électrovanne de fermeture d'urgence (72) est disposée, afin d'être excitée en permanence pendant le fonctionnement du système hydraulique et d'être ouverte dans cette position, et dans lequel les soupapes pilotes (91, 92) sont disposées respectivement dans les tronçons, s'étendant séparément, des conduites entre l'accumulateur (5) et les soupapes anti-retour (81, 82) et sont réalisées de manière commandable électriquement, et dans lequel un étranglement (10) se trouve dans la conduite sur le côté d'ouverture du cylindre hydraulique (6), afin d'être traversé par du fluide hydraulique pendant chaque déplacement du cylindre hydraulique (6), et l'autre étranglement (11, 12) se trouve soit dans la conduite entre le récipient de collecte et de compensation (1) et le débouché dans la conduite allant de l'ensemble de pompage (2) jusqu'au côté d'ouverture du cylindre hydraulique (6) soit dans la conduite entre l'accumulateur (5) et le débouché dans la conduite allant de l'ensemble de pompage (2) jusqu'au côté de fermeture du cylindre hydraulique (6).
  2. Dispositif selon la revendication 1, caractérisé en ce que le dispositif comporte un étranglement supplémentaire (11, 12), lequel se trouve soit dans la conduite entre le récipient de collecte et de compensation (1) et le débouché dans la conduite allant de l'ensemble de pompage (2) jusqu'au côté d'ouverture du cylindre hydraulique (6) soit dans la conduite entre l'accumulateur (5) et le débouché dans la conduite allant de l'ensemble de pompage (2) jusqu'au côté de fermeture du cylindre hydraulique (6), de telle sorte qu'un étranglement (11, 12) se trouve dans chacune de ces deux conduites.
  3. Dispositif selon l'une des revendications 1 ou 2, caractérisé en ce que le dispositif comporte deux soupapes de limitation de pression (30, 31), dont l'une est respectivement raccordée à l'une des conduites entre les soupapes anti-retour (81, 82) pouvant être débloquées et le cylindre hydraulique (6).
  4. Dispositif selon l'une des revendications 1 à 3, caractérisé en ce que le dispositif comporte une électrovanne (20) pouvant être commandée électriquement, laquelle est disposée dans la même conduite que l'électrovanne de fermeture d'urgence (72) et est réalisée de telle sorte qu'en cas d'excitation électrique elle peut ouvrir la soupape de fermeture d'urgence (71) et désaccoupler les soupapes pilotes (91, 92) de l'accumulateur (5).
  5. Dispositif selon l'une des revendications 1 à 4, caractérisé en ce que le dispositif comporte un point de raccordement (50) pour des soupapes de fermeture d'urgence supplémentaires, lequel est disposé dans la même conduite que l'électrovanne de fermeture d'urgence (72) .
  6. Dispositif selon l'une des revendications 1 à 5, caractérisé en ce que le dispositif comporte un point de raccordement (40) pour des consommateurs supplémentaires de fluide hydraulique, lequel est disposé dans la conduite allant de l'accumulateur (5) jusqu'au cylindre hydraulique (6).
  7. Dispositif selon l'une des revendications 1 à 6, caractérisé en ce que le cylindre hydraulique (6) est réalisé sous forme de cylindre synchrone, et les pompes de l'ensemble de pompage (2) refoulent la même quantité de fluide hydraulique par révolution.
  8. Dispositif selon l'une des revendications 1 à 6, caractérisé en ce que le cylindre hydraulique (6) est réalisé sous forme de cylindre différentiel, et les pompes de l'ensemble de pompage (2) refoulent différentes quantités de fluide hydraulique par révolution, le rapport de quantités de refoulement étant adapté au rapport de volumes du cylindre hydraulique (6) par rapport aux côtés d'ouverture et de fermeture.
EP18705117.2A 2017-03-29 2018-02-08 Dispositif de régulation d'une machine hydraulique Active EP3601805B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017106693.4A DE102017106693B3 (de) 2017-03-29 2017-03-29 Vorrichtung zum Regeln einer hydraulischen Maschine
PCT/EP2018/053139 WO2018177640A1 (fr) 2017-03-29 2018-02-08 Dispositif de régulation d'une machine hydraulique

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EP3601805A1 EP3601805A1 (fr) 2020-02-05
EP3601805B1 true EP3601805B1 (fr) 2021-01-06

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EP (1) EP3601805B1 (fr)
CN (1) CN110446859B (fr)
CA (1) CA3058354A1 (fr)
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WO (1) WO2018177640A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022121962A1 (de) 2022-08-31 2024-02-29 Bucher Hydraulics Ag Elektrisch-hydraulischer Aktor

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9062744B2 (en) * 2013-03-13 2015-06-23 American Axle & Manufacturing, Inc. Two-speed drive module
DE102019108476A1 (de) * 2019-04-01 2020-10-01 Moog Gmbh Hydrauliksystem für Stabilisatorantrieb
CN111550459A (zh) * 2020-05-20 2020-08-18 宁波华美达机械制造有限公司 一种伺服泵的安全保护油路系统
DE102021123914A1 (de) * 2021-09-15 2023-03-16 HMS - Hybrid Motion Solutions GmbH Hydraulisches Antriebssystem mit einer 2x2Q Pumpeneinheit
JP7400915B1 (ja) 2022-09-27 2023-12-19 いすゞ自動車株式会社 ポンプシステム及びそれを備えた車両

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6048634B2 (ja) 1976-03-29 1985-10-28 株式会社東芝 水力機械のガイドベ−ン閉鎖装置
FR2811037B1 (fr) * 2000-06-28 2002-10-18 Aerospatiale Matra Airbus Systeme d'actionnement hydraulique a commande electrique
WO2002004820A1 (fr) 2000-07-10 2002-01-17 Kobelco Construction Machinery Co., Ltd. Circuit de verin hydraulique
AT8986U1 (de) * 2005-10-28 2007-03-15 Hoerbiger Automatisierungstech Hydraulische druckversorgungseinheit, sowie elektrohydraulische arbeitseinheit und spannsystem mit einer derartigen druckversorgungseinheit
US7546730B2 (en) * 2006-03-23 2009-06-16 Parker-Hannifin Corporation Hydraulic vehicle stabilizer system with two-stage bi-rotational hydraulic pump system
CN101813104A (zh) * 2009-12-31 2010-08-25 上海汇益控制系统股份有限公司 一种快速推进的低功率节能型液压伺服执行机构
DE102010053811A1 (de) * 2010-12-08 2012-06-14 Moog Gmbh Störungssicheres Betätigungssystem
CN102155476B (zh) * 2011-03-28 2013-11-06 上海交通大学 基于pwm无节流损失的阀控调节系统的调节方法
KR101339921B1 (ko) * 2011-09-28 2013-12-10 주재석 유압 실린더용 유압장치
JP5956184B2 (ja) * 2012-02-27 2016-07-27 株式会社小松製作所 油圧駆動システム
CN103062166A (zh) * 2013-01-24 2013-04-24 中国铁建重工集团有限公司 一种复合型泵送电液系统
DE102013008047A1 (de) * 2013-05-13 2014-11-13 Robert Bosch Gmbh Drehzahlvariabler Antrieb mit zwei Pumpen und einem Differenzialzylinder
DE102013212937A1 (de) 2013-07-03 2014-07-10 Voith Patent Gmbh Vorrichtung zum Öffnen und Schließen der Leitschaufeln einer hydraulischen Maschine
DE102014218884B4 (de) * 2014-09-19 2020-12-10 Voith Patent Gmbh Hydraulischer Antrieb mit Eilhub und Lasthub
DE102017106700B3 (de) * 2017-03-29 2018-05-17 Voith Patent Gmbh Vorrichtung zum Regeln einer hydraulischen Maschine
US11072418B2 (en) * 2018-04-13 2021-07-27 The Boeing Company Hydraulic system for an aircraft

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022121962A1 (de) 2022-08-31 2024-02-29 Bucher Hydraulics Ag Elektrisch-hydraulischer Aktor

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CN110446859B (zh) 2020-08-28
DE102017106693B3 (de) 2018-05-30
CN110446859A (zh) 2019-11-12
EP3601805A1 (fr) 2020-02-05
US20200018329A1 (en) 2020-01-16
US10808734B2 (en) 2020-10-20
CA3058354A1 (fr) 2018-10-04

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