EP3601805B1 - Apparatus for controlling a hydraulic machine - Google Patents

Apparatus for controlling a hydraulic machine 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
Prior art date
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Active
Application number
EP18705117.2A
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German (de)
French (fr)
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EP3601805A1 (en
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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Description

Die Erfindung betrifft eine Vorrichtung zum Regeln einer hydraulischen Maschine, insbesondere eine Vorrichtung zum Regel einer Turbine, einer Pumpe oder einer Pumpturbine.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.

Konventionelle Vorrichtungen zum Regeln einer hydraulischen Maschine sind aus dem allgemeinen Stand der Technik bekannt. So beschreibt beispielsweise die DE 27 13 867 A1 eine solche Vorrichtung (siehe Figur 3), die eine Druckölquelle, einen hydraulischen Stellmotor (Hydrozylinder) und Regelventile zur Dosierung der Energie zur Verstellung des Hydrozylinders umfasst. In der Regel handelt es sich bei der Druckölquelle um einen Speicher für das unter Überdruck stehende Hydraulikmedium. Der Speicher muss dabei mit Hilfe von Pumpen gefüllt und auf den notwendigen Arbeitsdruck gebracht und gehalten werden.Conventional devices for controlling a hydraulic machine are known from the general prior art. For example, 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. As a rule, 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.

Aus der DE 10 2013 212 937 A1 ist ferner eine Vorrichtung zum Öffnen und Schließen der Leitschaufeln einer hydraulischen Maschine bekannt, bei welcher drehzahlvariabel angetriebenen hydraulische Konstantpumpen verwendet werden. In dieser Schrift wird lediglich die prinzipielle Wirkweise einer solchen Vorrichtung offenbart. Eine weitere Vorrichtung ist aus der DE 10 2013 008047 A1 bekannt.From the DE 10 2013 212 937 A1 Furthermore, a device for opening and closing the guide vanes of a hydraulic machine is known, in which variable-speed hydraulic fixed displacement pumps are used. In this document, only the principle mode of operation of such a device is disclosed. Another device is from the DE 10 2013 008047 A1 known.

Die Aufgabe der vorliegenden Erfindung besteht darin eine Vorrichtung zum Regeln einer hydraulischen Maschine anzugeben, bei welcher drehzahlvariabel angetriebene hydraulische Konstantpumpen verwendet werden, und welche die Anforderungen bei einer hydraulischen Maschine, z.B. hinsichtlich Stellzeiten, Notschließeigenschaften - auch bei Versagen der Pumpen, Eignung für große Hydraulikzylinder-Volumina etc., gewährleistet. Im Vergleich mit konventionellen Vorrichtungen zeichnet sich die erfindungsgemäße Lösung durch eine hohe Energieeffizienz, gute Umweltverträglichkeit, Wartungsfreundlichkeit und geringen Anschaffungs- und Betriebskosten aus.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. In comparison with conventional devices, the solution according to the invention is characterized by high energy efficiency, good environmental compatibility, ease of maintenance and low acquisition and operating costs.

Erfindungsgemäß wird diese Aufgabe durch eine Vorrichtung zum Regeln einer hydraulischen Maschine mit den Merkmalen des Anspruchs 1 gelöst. Weitere vorteilhafte Ausgestaltungen der erfindungsgemäßen Vorrichtung ergeben sich aus den hiervon abhängigen Unteransprüchen.According to the invention, 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.

Die erfindungsgemäße Lösung wird nachfolgend anhand von Figuren erläutert. Darin ist im Einzelnen folgendes dargestellt:

Figur 1
Schematischer Aufbau einer erfindungsgemäßen Vorrichtung
The solution according to the invention is explained below with reference to figures. The following is shown in detail:
Figure 1
Schematic structure of a device according to the invention

In der Darstellung der Figur 1 ist der Aufbau einer erfindungsgemäßen Vorrichtung zum Regeln einer hydraulischen Maschine in schematisierter Weise gezeigt. Die Vorrichtung umfasst einen Sammel- und Ausgleichsbehälter, welcher mit 1 bezeichnet ist, eine Pumpenanordnung, welche mit 2 bezeichnet ist, einen drehzahlvariablen Pumpenantrieb, welcher mit 3 bezeichnet ist, einen Speicher, welcher mit 5 bezeichnet ist, einen Hydraulikzylinder, welcher mit 6 bezeichnet ist, ein Notschlussventil, welches mit 71 bezeichnet ist, ein Notschlussmagnetventil, welches mit 72 bezeichnet ist, zwei entsperrbare Rückschlagventile, welche mit 81 und 82 bezeichnet sind, zwei Vorsteuerventile, welche mit 91 und 92 bezeichnet sind, drei Drosseln, welche mit 10, 11 und 12 bezeichnet sind, ein optionales Magnetventil, welches mit 20 bezeichnet ist, zwei optionale Druckbegrenzungsventile, welche mit 30 und 31 bezeichnet sind und zwei optionale Anschlüsse, welche mit 40 und 50 bezeichnet sind. Der Pfeil unterhalb des Hydraulikzylinders 6 deutet die Schließrichtung desselben an.In the representation of the Figure 1 the structure of a device according to the invention for controlling a hydraulic machine is shown in a schematic manner. 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.

Bei dem Hydraulikzylinder 6 kann es sich z.B. um den Leitrad- Hydraulikzylinder oder um den Hydraulikzylinder zur Verstellung der Laufradschaufeln einer hydraulischen Maschine handeln. Solche Hydraulikzylinder erfordern zum Betrieb oft große Volumina an Hydraulikflüssigkeit. Der Hydraulikzylinder 6 kann als Gleichgangzylinder ausgefertigt sein, wie in Figur 1 durch die gestrichelte zweite Stange angedeutet ist. Der Hydraulikzylinder 6 kann jedoch auch als Differentialzylinder mit unterschiedlichen Volumen für Schließen- und Öffnen-Seite ausgefertigt sein.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.

Die Pumpenanordnung 2 umfasst zwei Pumpen mit umkehrbarer Förderrichtung. In Figur 1 sind die zwei Pumpen auf einer Welle angeordnet, welche durch den Pumpenantrieb 3 angetrieben wird. Es sind jedoch auch andere konstruktive Ausgestaltungen möglich, z.B. dass die Pumpen mittels eines Getriebes durch den Pumpenantrieb 3 angetrieben werden. Es ist sogar denkbar, dass der Pumpenantrieb 3 jeweils einen Motor und einen Frequenzumrichter für jede der beiden Pumpen umfasst. Die weitere Beschreibung bezieht sich auf die in Figur 1 dargestellte Ausführungsform. Dabei ist jeweils ein Anschluss einer Pumpe mit einer Steuerleitung des Hydraulikzylinders verbunden, so dass in einer Drehrichtung der Welle die eine Pumpe Hydraulikflüssigkeit in Richtung des Hydraulikzylinders 6 fördert und die andere Pumpe Hydraulikflüssigkeit vom Hydraulikzylinder 6 aufnimmt. In der anderen Drehrichtung der Welle ist es gerade umgekehrt. So sind in Figur 1 der rechte Anschluss der unteren Pumpe (über das entsperrbare Rückschlagventil 82) mit der Schließen-Seite des Hydraulikzylinders 6 und der linke Anschluss der oberen Pumpe (über das entsperrbare Rückschlagventil 81) mit der Öffnen-Seite des Hydraulikzylinders 6 verbunden. Die übrigen Anschlüsse der Pumpen sind jeweils direkt mit dem Sammel- und Ausgleichsbehälter 1 verbunden. D.h. in der einen Drehrichtung der Welle pumpt die untere Pumpe Hydraulikflüssigkeit aus dem Sammel- und Ausgleichsbehälter 1 in die Schließen-Seite des Hydraulikzylinders 6 und gleichzeitig pumpt die obere Pumpe Hydraulikflüssigkeit von der Öffnen-Seite des Hydraulikzylinders 6 in den Sammel-und Ausgleichsbehälter 1. In der anderen Drehrichtung der Welle verlaufen die Volumenströme umgekehrt. Im Falle, dass die Fördervolumina der beiden Pumpen gleich groß sind, bedeutet das, dass letztendlich keine Hydraulikflüssigkeit in den Sammel- und Ausgleichsbehälter 1 fließt bzw. aus ihm entnommen wird (vgl. unten zu Gleichgangzylinder). Im anderen Fall wird nur die Differenzfördermenge der Pumpen in den Sammel- und Ausgleichbehälter 1 abgegeben bzw. ihm entnommen (vgl. unten zu Differentialzylinder). Dabei ist jeweils vorausgesetzt, dass die Rückschlagventile 81 und 82 entsperrt sind (siehe unten in der Beschreibung der Betriebszustände).The pump arrangement 2 comprises two pumps with a reversible delivery direction. In Figure 1 the two pumps are arranged on a shaft which is driven by the pump drive 3. However, other constructional configurations are also possible, for example the pumps being driven by the pump drive 3 by means of a gear. It is even conceivable that the pump drive 3 comprises a motor and a frequency converter for each of the two pumps. The further description refers to the in Figure 1 illustrated embodiment. 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. So are in Figure 1 the right connection of the lower pump (via the releasable check valve 82) is connected to the closing side of the hydraulic cylinder 6 and the left connection of the upper pump (via the releasable check valve 81) is connected to the opening side of the hydraulic cylinder 6. The other connections of the pumps are each directly connected to the collecting and equalizing tank 1. That is, in one direction of rotation of the shaft, the lower pump pumps hydraulic fluid from the collecting and equalizing tank 1 into the closing side of the hydraulic cylinder 6 and at the same time the upper pump pumps hydraulic fluid from the opening side of the hydraulic cylinder 6 into the collecting and equalizing tank 1. In the other direction of rotation of the shaft, the volume flows are reversed. In the event that the delivery volumes of the two pumps are the same, this means that ultimately no hydraulic fluid flows into the collecting and equalizing tank 1 or is removed from it (see below on synchronous cylinder). Otherwise only the Differential delivery rate of the pumps delivered into the collecting and equalizing tank 1 or taken from it (see below on differential cylinder). It is assumed that the check valves 81 and 82 are unlocked (see below in the description of the operating states).

Falls die verwendeten Pumpen ausgewiesene Druck- und Sauganschlüsse aufweisen, so werden vorzugsweise immer die Druckanschlüsse mit dem Hydraulikzylinder 6 und die Sauganschlüsse mit dem Sammel- und Ausgleichsbehälter 1 verbunden.If the pumps used have designated pressure and suction connections, the pressure connections are preferably always connected to the hydraulic cylinder 6 and the suction connections to the collecting and compensating tank 1.

Die Welle der Pumpenanordnung 2 wird von dem drehzahlvariablen Pumpenantrieb 3, welcher in beiden Drehrichtungen betreibbar ist, angetrieben. Der Pumpenantrieb 3 umfasst in der Regel einen elektrischen Servomotor, der von einem Frequenzumrichter elektrisch gespeist wird.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.

Die entsperrbaren Rückschlagventile 81 und 82, welche in den Verbindungsleitungen des Hydraulikzylinders 6 mit der Pumpenanordnung 2 so angeordnet sind, dass sie im nicht entsperrten Zustand eine Bewegung des Kolbens des Hydraulikzylinders verhindern, sind jeweils mit einem der Vorsteuerventile 91, 92 verbunden. Diese sind jeweils (über die Ventile 20 und 72) mit dem Speicher 5 verbunden. Ein Öffnen eines Vorsteuerventils 91, 92 bewirkt so die Entsperrung des zugehörigen Rückschlagventils 81, 82. Das Öffnen der Vorsteuerventile 91, 92 wird durch den (elektrischen) Regler der hydraulischen Maschine dadurch bewirkt, dass diese erregt werden. Jedes der Vorsteuerventile 91, 92 kann separat erregt werden.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.

Der Speicher 5 ist mit der Schließen-Seite des Hydraulikzylinders 6 verbunden. Das Notschlussventil 71 ist so mit der Öffnen-Seite des Hydraulikzylinders 6 und dem Sammel- und Ausgleichsbehälter 1 verbunden, dass ein Volumenstrom zwischen der Öffnen-Seite des Hydraulikzylinders 6 und dem Sammel- und Ausgleichsbehälter 1 nur möglich ist, wenn das Notschlussventil 71 geöffnet ist. Die Steuerung des Zustands des Notschlussventils 71 erfolgt über das Notschlussmagnetventil 72, welches sich in einer hydraulischen Leitung zwischen Notschlussventil 71 und dem Speicher 5 befindet. Das Notschlussmagnetventil 72 befindet sich auch in den Leitungen zwischen den Vorsteuerventilen 91, 92 und dem Speicher 5. Das (federbelastete) Notschlussmagnetventil 72 wird im Betrieb immer dauererregt, wodurch das Notschlussventil 71 geschlossen ist und die Vorsteuerventile 91, 92 durch den Speicher 5 mit Öldruck versorgt werden (d.h. die Rückschlagventile 81, 82 können in diesem Zustand durch die Vorsteuerventile 91, 92 entsperrt werden).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).

Die Drossel 10, die auch "Grunddrossel" genannt wird, befindet sich in der Leitung zwischen der Öffnen-Seite des Hydraulikzylinders 8 und dem Rückschlagventil 81 jedoch noch vor der Abzweigung in dieser Leitung zum Notschlussventil 71, d.h. in unmittelbarer Nachbarschaft zum Hydraulikzylinder 6. Die Drossel 11 befindet sich in der Leitung, die den Speicher 5 mit dem restlichen Teil der Vorrichtung verbindet. Die Drossel 12 befindet sich in der Leitung zwischen dem Notschlussventil 71 und dem Sammel- und Ausgleichsbehälter 1. Dabei ist eine der beiden Drosseln 11 oder 12 als optional zu betrachten (siehe die Ausführungen zur Notschlussfunktion).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).

Optional kann die Vorrichtung noch weitere Notschlusssteuerventile umfassen (z.B. ein Überdrehzahlventil etc.). Diese können über den Anschluss 50 angeschlossen werden, welcher sich in derselben hydraulischen Leitung wie das Notschlussmagnetventil 72 befindet.Optionally, 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.

Optional können weitere Verbraucher über den Anschluss 40 an den Speicher 5 angeschlossen werden. Der Anschluss 40 befindet sich in der hydraulischen Leitung, welche den Speicher 5 mit der restlichen Vorrichtung verbindet.Optionally, further consumers can be connected to the memory 5 via the connection 40. The connection 40 is located in the hydraulic line which connects the reservoir 5 with the rest of the device.

Im Folgenden werden die Wirkweisen der erfindungsgemäßen Vorrichtung in den einzelnen Betriebszuständen der hydraulischen Maschine näher beschrieben und die Vorteile der Vorrichtung erläutert. Hierbei wird als Anfangszustand angenommen, dass der mit der Schließen-Seite des Hydraulikzylinders 6 direkt verbundene Speicher 5 mit einem definierten Druck geladen ist und sich der Hydraulikzylinder 6 in einer beliebigen Zwischenstellung befindet.The modes of operation of the device according to the invention in the individual operating states of the hydraulic machine are described in more detail below and the advantages of the device are explained. Here, it is assumed as the initial state that the accumulator 5, which is directly connected to the closing side of the hydraulic cylinder 6, is charged with a defined pressure and the hydraulic cylinder 6 is in any intermediate position.

Regelbetrieb der hydraulischen Maschine:Normal operation of the hydraulic machine:

So lange die Position des Hydraulikzylinders 6 gehalten werden soll, befinden sich die vom Regler der hydraulischen Maschine angesteuerten Vorsteuermagnetventile 91, 92 im entregten Zustand. Dadurch sind die entsperrbaren Rückschlagventile 81, 82 in den Steuerleitungen zur Öffnen- bzw. Schließen-Seite des Hydraulikzylinders 6 ebenfalls geschlossen und der Zylinder 6 wird leckagefrei in seiner Position gehalten. In diesem Zustand wird der drehzahlvariable Antrieb 3 abgeschaltet, so dass keine Verlustenergie (Wärme) in das System eingebracht wird. Dadurch kann prinzipiell auf eine Ölkühlung verzichtet werden, was den Vorteil einer deutlich besseren Energieeffizienz bietet.As long as the position of the hydraulic cylinder 6 is to be maintained, the pilot solenoid valves 91, 92 controlled by the controller of the hydraulic machine are in the de-energized state. As a result, 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. In this state, the variable-speed drive 3 is switched off so that no energy loss (heat) is introduced into the system. As a result, oil cooling can in principle be dispensed with, which offers the advantage of significantly better energy efficiency.

Wird nun ein Regelvorgang notwendig (z.B. Sollwertänderung oder die Regelabweichung überschreitet einen bestimmten Wert (Totband)), werden die Vorsteuerventile 91 und 92 über den Regler erregt, was zum Öffnen der entsperrbaren Rückschlagventile führt. Jetzt kann der Hydraulikzylinder direkt über den drehzahlvariablen Pumpenantrieb 3 positioniert werden. Falls der Hydraulikzylinder 6 als Gleichgangzylinder ausgefertigt ist, wird durch die Pumpenanordnung 2 die gleiche Ölmenge saugseitig geschluckt wie druckseitig in den Zylinder eingebracht. In diesem Fall haben die beiden Pumpen der Pumpenanordnung 2 identische Fördervolumina. Falls der Hydraulikzylinder 6 als Differentialzylinder ausgefertigt ist, wird das Fördervolumen-Verhältnis der beiden Pumpen der Pumpenanordnung 2 so genau wie möglich an den Differentialzylinder angepasst. Die während des Verfahrens des Hydraulikzylinders 6 entstehende Differenz-Ölmenge kann über die entsprechenden am Sammel- und Ausgleichsbehälter 1 angeschlossenen Saugleitungen bzw. ein geringes Pendelvolumen am Speicher 5 ausgeglichen werden.If a control process is now necessary (e.g. a change in the setpoint or the control deviation exceeds a certain value (dead band)), 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. If 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.

Das Ölvolumen und somit der Druck im Speicher 5 bleibt weitestgehend konstant und sorgt dafür, dass das ganze System vorgespannt ist. Die permanente Druckvorspannung des Hydraulikzylinders 6 durch den Speicher 5 hat den Vorteil, dass der Hydraulikzylinder 6 immer fest in der definierten Position eingespannt bleibt unabhängig z.B. von einem Wechsel der Kraftrichtung der am Zylinder 6 angreifenden äußeren Kräfte.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.

Nach Erreichen der gewünschten Position werden die Vorsteuerventile 91, 92 entregt, wodurch der Zylinder 6 wieder ohne Aufbringung von Energie in seiner Position gehalten werden kann. Es ist zu erwähnen, dass das Speichervolumen im Vergleich mit konventionellen Systemen nicht mehr zu Regelzwecken verwendet wird, da diese Aufgabe komplett von der Pumpenanordnung 2 übernommen wird. Somit kann das Speichervolumen und so die Speichergröße drastisch reduziert werden. Dieses führt zusätzlich auch zu einem kleineren Sammel- und Ausgleichsbehälter 1, wodurch insgesamt die Kosten reduziert werden können.After reaching the desired position, 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.

Notschluss:Emergency stop:

Um in einem Fehlerfall ein sicheres Stilllegen der hydraulischen Maschine gewährleisten zu können, ist eine Notschlussfunktion implementiert, die es erlaubt, die Anlage ohne Stromversorgung (oder bei einem Defekt des drehzahlvariablen Antriebs 3) herunterzufahren. Im Notschlussfall wird das im Betrieb dauererregte Notschlussmagnetventil 72 entregt, worauf das Notschlussventil 71 öffnet. Somit wird aus dem "quasi-geschlossenen" hydraulischen Regelkreislauf ein offener Kreislauf. Der Speicher 5 ist mit der Schließen-Seite des Hydraulikzylinders 6 verbunden, wobei die Öffnen-Seite jetzt in den Sammel- und Ausgleichsbehälter 1 abgesteuert wird. Gleichzeitig wird auch der Druck zu den Vorsteuerventilen 91, 92 entlastet, so dass die entsperrbaren Rückschlagventile 81, 82 schließen. Somit wird sicher verhindert, dass sich z.B. aufgrund eines Defektes oder einer Leckage in der Pumpenanordnung 2 das Speichervolumen fälschlicherweise hierüber entleeren könnte und somit nicht mehr zum Schließen zur Verfügung stehen würde.In order to be able to guarantee safe shutdown of the hydraulic machine in the event of a fault, 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). In the event of an emergency, 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. At the same time, the pressure to the pilot valves 91, 92 is also relieved, so that the releasable check valves 81, 82 close. This reliably prevents, for example, due to a defect or a leak in the pump arrangement 2 from being able to falsely empty the storage volume and thus no longer be available for closing.

In diesem offenen Kreislauf liefert der Speicher 5 ein definiertes Volumen innerhalb definierter Druckgrenzen. Daher lässt sich mit Hilfe der Grunddrossel 10 und einer zusätzlich in Reihe geschalteten Drossel 11 oder 12 sicher eine definierte Schließzeit einstellen. Werden tatsächlich zwei zusätzlich in Reihe geschaltete Drosseln 11 und 12 verwendet, so ergibt sich dadurch eine größere Flexibilität und eine größere Robustheit gegenüber z.B. einem Leitungsbruch in der Leitung zwischen der Grunddrossel 10 und dem Schnellschlussventil 71, da sich die zusätzliche Drosselwirkung auf zwei Drosseln verteilt, von denen nur eine (12) durch den Leitungsbruch ausfällt.In this open circuit, 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.

Durch die Grunddrossel 10 entsteht beim Verfahren des Hydraulikzylinders 6 ein Staudruck, gegen den die Pumpenanordnung 2 wirkt, und der daher in gewissen Grenzen gehalten werden muss (einzuhaltende Nenndrücke der Leitungen und Komponenten, Leistung des Pumpenantriebs 3 etc.). Daher ist eine individuelle Auslegung der einzelnen Drosseln 10, 11, 12 notwendig. Dabei muss im Vordergrund stehen, dass immer der größtmögliche Anteil der Gesamtdrosselwirkung und damit der Schließzeit über die Grunddrossel 10 realisiert werden muss. Das hat u.a. den Grund, dass durch die Anordnung der Grunddrossel 10 direkt in der Öffnen-Seite des Hydraulikzylinders 6 auch bei z.B. Leitungsbruch der Öffnen-Steuerseite (d.h. der Leitung zwischen Grunddrossel 10 und der Pumpenanordnung 2) eine Begrenzung der Schließzeit gewährleistet ist. Dadurch, dass der Speicher 5 direkt in der Schließen-Seite des Zylinders 6 angeordnet ist, und dort förmlich als "Puffer" wirkt, würde sogar in dem Fehlerfall, dass der Pumpenantrieb 3 eine höhere als die definierte maximale Drehzahl Richtung Schließen annähme, die Stellzeit über die Grunddrossel 10 begrenzt werden. Es würde sich lediglich der Druck im Speicher 5 durch eine erhöhte Pumpenfördermenge langsam erhöhen.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. One of the reasons for this is that 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). Due to the fact that the memory 5 is arranged directly in the closing side of the cylinder 6, and there literally acts as a "buffer", the actuating time would even in the event of a fault that the pump drive 3 assumed a higher than the defined maximum speed in the closing direction be limited by the basic throttle 10. Only the pressure in the reservoir 5 would slowly increase due to an increased pump delivery rate.

Um die Vorrichtung gegen einen unzulässig hohen Druck abzusichern, können optional Druckbegrenzungsventile 30, 31 jeweils öffnen- und schließen-seitig bzgl. dem Hydraulikzylinder 6 installiert sein. Es ist klar, dass das Druckbegrenzungsventil 31 auch im Speicher 5 integriert sein kann.In order to secure the device against an impermissibly high pressure, 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.

Speicherlade-Funktion:Storage charging function:

Der Speicher 5 wird auf seinen Füllgrad bzw. seinen Systemdruck mittels entsprechender Niveau- und Drucksensoren überwacht. Das Ölvolumen und der Druck im Speicher 5 werden im Betrieb unabhängig von der Stellung des Hydraulikzylinders 6 auf einem definierten maximalen Niveau gehalten. Dieses Niveau wird sich im Falle eines verwendeten Gleichgangzylinders (siehe oben), bzw. wenn keine weiteren externen Verbraucher am Speicher 5 über die optionale Anschlussstelle 40 angeschlossen sind, im Betrieb nicht oder nur sehr wenig ändern.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.

Um aber auch die Verwendung von Differenzialzylindern sowie externen Verbrauchern zu ermöglichen, kann der Speicher mittels des drehzahlvariablen Antriebs 3 und den elektrisch angesteuerten entsperrbaren Rückschlagventilen 81 und 82 unabhängig von der Stellung des Hydraulikzylinders 6 während des Betriebs aufgeladen werden.However, in order to also enable the use of differential cylinders and external consumers, 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.

Dazu müssen sich die Vorsteuermagnetventile 91 und 92 in entregtem Zustand befinden, wodurch auch die entsperrbaren Rückschlagventile 81 und 82 geschlossen sind. Die Pumpenanordnung 2 wird jetzt so angesteuert, dass diese in Richtung Schließen-Seite des Hydraulikzylinders 6 fördert. Die Position des Zylinders 6 ändert sich dadurch nicht, da das entsperrbare Rückschlagventil 81 in der Öffnen-Seite des Hydraulikzylinders 6 geschlossen ist und somit kein Öl aus dem Hydraulikzylinder 6 entweichen kann. In Schließen-Richtung kann das Rückschlagventil 82 aber durchströmt werden, wodurch sich der Druck erhöht und der Speicher 5 "geladen" wird. Die dafür nötige Differenz-Ölmenge wird von der Pumpenanordung 2 über eine entsprechende Leitung vom Sammel- und Ausgleichsbehälter 1 angesaugt.For this purpose, 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. In the closing direction, however, 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.

Sollte während des Ladens ein Regelvorgang notwendig werden, hat dieser Priorität vor dem Ladevorgang. Das ist aus sicherheitstechnischer Sicht kein Problem, da ein entsprechender Schaltpunkt der Niveau- und Drucküberwachung dafür sorgt, dass für einen eventuellen Notschluss immer genügend Volumen bzw. Druck im Speicher vorhanden ist. Durch das Erregen der Vorsteuerventile 91 und 92 und die Ansteuerung des drehzahlvariablen Antriebs 3 ist es sofort wieder möglich Regelbewegungen auszuführen.If a control process becomes necessary during charging, this has priority over the charging process. From a safety point of view, this is not a problem, as a corresponding switching point for level and pressure monitoring ensures that there is always enough volume or pressure in the storage tank for a possible emergency shutdown. By energizing the pilot valves 91 and 92 and activating the variable-speed drive 3, it is immediately possible to carry out control movements again.

Die Speicher-Laden-Funktion ist während des normalen Betriebs und einem Stillstand der hydraulischen Maschine aktiv. So wird gewährleistet, dass immer die entsprechende Sicherheit für einen eventuellen Notschluss gegeben ist, sowie beim Start der hydraulischen Maschine diese schnellstmöglich verfügbar ist.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.

Optionale Schnell-Schließen-Funktion:Optional quick-close function:

Normalerweise wird die Pumpenanordnung 2 bzgl. der Größe, Drehzahl und Leistung der Pumpen so ausgelegt, dass die für den jeweiligen Anwendungsfall geforderten Öffnen- und Schließzeiten des Hydraulikzylinders 6 allein über den Pumpenantrieb 3 verfahren werden können.Normally, 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.

Wenn z.B. große Hydraulikzylinder-Volumina vorhanden sind und im Gegensatz zu den Schließzeiten die Öffnungszeiten deutlich länger sein dürfen, könnten, um die Dimension der Pumpenanordnung 2 und des Pumpenantriebes 3 so klein wie möglich zu halten (Platzverhältnisse, Ersatzteilkosten etc.), diese so ausgelegt werden, dass der Hydraulikzylinder 6 nur mit der minimalen Öffnungszeit verfahren werden kann.If, for example, there are large hydraulic cylinder volumes and, in contrast to the closing times, 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.

Um dann eine schnellere Schließzeit (z.B. im Fall eines Wasserkraftreglers bei einem Lastabwurf) zu erreichen, ist optional das Schnell-Schließen-Magnetventil 20 vorgesehen, welches sich in derselben hydraulischen Leitung wie das Notschlussmagnetventil 72 befindet. Durch Beschalten dieses Ventils 20 kann nun das Speichervolumen genutzt werden, um zu schließen. Dabei wird das Schnell-Schließen-Magnetventil 20 erregt, wodurch das Notschlussventil 71 öffnet. Gleichzeitig wird durch die Druckzufuhr zu den Vorsteuerventilen 91 und 92 hydraulisch getrennt, so dass auch die entsperrbaren Rückschlagventile 81 und 82 in den Steuerleitungen schließen. Die Pumpenanordnung 2 kann nun während dieses Vorgangs mit maximaler Fördermenge in Richtung Schließen gesteuert werden. Durch die Unterstützung durch die Pumpenanordnung 2 wird das Ölvolumen minimiert, welches aus dem Speicher 5 entnommen wird. Dies hat u.a. die Vorteile, dass der Speicher 5 weniger stark entleert wird und die Schließzeit, die über die Grunddrossel 10 direkt am Hydraulikzylinder 6 definiert wird, aufgrund der kleineren Spanne zwischen Anfangs- und Enddruck im Speicher 5 genauer eingestellt werden kann.In order to achieve a faster closing time (e.g. in the case of a hydropower regulator in the event of a load shedding), 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. At the same time, 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. As a result of the support provided by the pump arrangement 2, the oil volume which is taken from the reservoir 5 is minimized. This has the advantages, among other things, that the accumulator 5 is emptied less and the closing time, which is defined by the basic throttle 10 directly on the hydraulic cylinder 6, can be set more precisely due to the smaller range between the initial and final pressure in the accumulator 5.

Um z.B. nach einem Lastabwurf bei einer Wasserturbine die Möglichkeit zu haben, die Maschine wieder zu synchronisieren zu können, wird bei Erreichen einer definierten Öffnung das Schnell-Schließen-Ventil 20 wieder entregt. Gleichzeitig wird die "Fein-Regelung" jetzt wieder an den drehzahlvariablen Pumpenantrieb 3 übergeben, und die Maschine kann wieder synchronisiert werden.In order to be able to synchronize the machine again after a load shedding in a water turbine, for example, 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.

Im jetzigen Zustand ist aufgrund des Schließvorgangs und der Tatsache, dass nicht das ganze Volumen über die Pumpenanordnung 2 bereitgestellt werden konnte, der Speicher um einen Betrag, der kleiner ist als das bis zur entsprechenden Hydraulikzylinder-Position notwendige Ölvolumen, entleert worden. Der Druck und das Ölvolumen im Speicher 5 ist dabei immer noch hoch genug, dass ein etwaig notwendiger Notschluss durchgeführt werden könnte. Trotzdem sollte in dieser Situation der Speicher 5 so schnell wie möglich wieder aufgefüllt werden. Da während und nach Abschluss des Synchronisierungsvorgangs und erneutem Auffahren der Turbine auf die entsprechende Zylinderstellung der Regler aktiv ist und dadurch die Pumpenanordnung 2 nicht zum Laden des Speichers 5 genutzt werden darf, kann in diesem Fall folgendermaßen vorgegangen werden:
Während die Pumpenanordnung 2 den Hydraulikzylinder 6 auf die entsprechende Öffnung auffährt, befinden sich die Vorsteuermagnetventile 91 und 92 im entregten Zustand. Somit kann das öffnen-seitige Rückschlagventil 81 durchströmt werden, das schließen-seitige Rückschlagventil 82 bleibt gesperrt. Dadurch wird das beim Auffahren verdrängte Öl aus dem Hydraulikzylinder 6 direkt zurück in den Speicher 5 gedrückt. Die dafür nötige Ölmenge wird von der Pumpenanordnung 2 über die entsprechende Leitung vom Sammel- und Ausgleichsbehälter 1 angesaugt. Hat der Speicher 5 seinen Nenn-Füllgrad erreicht, werden die entsprechenden Rückschlagventile 81 und 82 geöffnet und der Hydraulikzylinder 6 kann ohne weiteres Füllen des Speichers 5 auf seine Endposition gefahren werden.In the current state, due to the closing process and the fact that the entire volume could not be made available via the pump arrangement 2, the reservoir has been emptied by an amount which is smaller than the oil volume required up to the corresponding hydraulic cylinder position. The pressure and the oil volume in the reservoir 5 are still high enough that any necessary emergency shutdown could be carried out. Nevertheless, in this situation, the memory 5 should be refilled as quickly as possible. 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.

Heizen-Funktion:Heating function:

Bei Unterschreiten eines definierten Öltemperaturwertes wird die Regelung über die Pumpenanordnung 2 durch das Öffnen der entsperrbaren Rückschlagventile 81 und 82 initiiert. Dadurch entsteht Wärme die zum Aufheizen des Systems genutzt wird.When the oil temperature falls below a defined value, 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.

Claims (8)

  1. Device for regulating a hydraulic machine, comprising a pump arrangement (2), a variable-rotational-speed pump drive (3), an accumulator (5), a hydraulic cylinder (6), an emergency closure valve (71), two unblockable check valves (81, 82), and two pilot-control valves (91, 92) for unblocking the check valves (81, 82), wherein the pump arrangement (2) comprises two pumps with reversible delivery direction, which are connected to the variable-rotational-speed pump drive (3) in such a way that the pumps can be driven by the pump drive (3) in both delivery directions, the device furthermore comprising a collecting and compensation vessel (1), an emergency closure solenoid valve (72), and at least two throttles (10, 11, 12), wherein a first connection of the first pump is connected to the opening side, and a first connection of the second pump is connected to the closure side, of the hydraulic cylinder (6), and wherein the remaining connections of the pumps are respectively connected to the collecting and compensation vessel (1) such that, in a drive direction of the pump drive (3), the first pump can deliver hydraulic fluid in the direction of the hydraulic cylinder (6) from the collecting and compensation vessel (1) and the second pump can deliver hydraulic fluid into the collecting and compensation vessel (1) from the sides of the hydraulic cylinder (6), and wherein the collecting and compensation vessel (1) is connected to the opening side, and the accumulator (5) is connected to the closure side, of the hydraulic cylinder (6), and the emergency closure valve (71) is arranged in the line between the hydraulic cylinder (6) and the collecting and compensation vessel (1), and respectively one unblockable check valve (81, 82) is situated in one of the lines from the pumps to the hydraulic cylinder (6) and is oriented in such a way that, in each state of the check valves (81, 82), hydraulic fluid can be passed through in the direction of the hydraulic cylinder (6), the device furthermore having lines which connect the accumulator (5) respectively to the two check valves (81, 82) and the emergency closure valve (71), in order for it to be possible to unblock the check valves (81, 82) and close the emergency closure valve (71), wherein said lines form, at least over a section, a single line, in which section the emergency closure solenoid valve (72) is arranged in order, during the operation of the hydraulic system, to be permanently excited and to be open in this position, and wherein the pilot-control valves (91, 92) are respectively arranged in the separately running sections of the lines between the accumulator (5) and the check valves (81, 82) and are designed to be electrically actuatable, and wherein one throttle (10) is situated in the line to the opening side of the hydraulic cylinder (6) in order, during each movement of the hydraulic cylinder (6), to be flowed through by hydraulic fluid, and the other throttle (11, 12) is situated either in the line between the collecting and compensation vessel (1) and the opening into the line from the pump arrangement (2) to the opening side of the hydraulic cylinder (6), or in the line between the accumulator (5) and the opening into the line from the pump arrangement (2) to the closure side of the hydraulic cylinder (6).
  2. Device according to Claim 1, characterized in that the device comprises a further throttle (11, 12) which is situated either in the line between the collecting and compensation vessel (1) and the opening into the line from the pump arrangement (2) to the opening side of the hydraulic cylinder (6), or in the line between the accumulator (5) and the opening into the line from the pump arrangement (2) to the closure side of the hydraulic cylinder (6), such that a throttle (11, 12) is situated in each of these two lines.
  3. Device according to either of Claims 1 and 2, characterized in that the device comprises two pressure-limiting valves (30, 31), of which respectively one is connected to one of the lines between the unblockable check valves (81, 82) and the hydraulic cylinder (6).
  4. Device according to one of Claims 1 to 3, characterized in that the device comprises an electrically actuatable solenoid valve (20), which is arranged in the same line as the emergency closure solenoid valve (72) and is designed in such a way that, in the event of electrical excitation, it can open the emergency closure valve (71) and can decouple the pilot-control valves (91, 92) from the accumulator (5).
  5. Device according to one of Claims 1 to 4, characterized in that the device comprises a connection point (50) for further emergency closure valves, which is arranged in the same line as the emergency closure solenoid valve (72).
  6. Device according to one of Claims 1 to 5, characterized in that the device comprises a connection point (40) for further consumers of hydraulic fluid, which is arranged in the line from the accumulator (5) to the hydraulic cylinder (6).
  7. Device according to one of Claims 1 to 6, characterized in that the hydraulic cylinder (6) is in the form of a synchronous cylinder, and the pumps of the pump arrangement (2) deliver the same amount of hydraulic fluid per revolution.
  8. Device according to one of Claims 1 to 6, characterized in that the hydraulic cylinder (6) is in the form of a differential cylinder, and the pumps of the pump arrangement (2) deliver different amounts of hydraulic fluid per revolution, wherein the delivery amount ratio is matched to the volume ratio of the hydraulic cylinder (6) in relation to the closure and opening sides.
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DE102022121962A1 (en) 2022-08-31 2024-02-29 Bucher Hydraulics Ag Electric-hydraulic actuator

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CN110446859A (en) 2019-11-12
WO2018177640A1 (en) 2018-10-04
CA3058354A1 (en) 2018-10-04
US10808734B2 (en) 2020-10-20
US20200018329A1 (en) 2020-01-16
EP3601805A1 (en) 2020-02-05
DE102017106693B3 (en) 2018-05-30
CN110446859B (en) 2020-08-28

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