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EP3601806B1 - Apparatus for controlling a hydraulic machine - Google Patents

Apparatus for controlling a hydraulic machine Download PDF

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Publication number
EP3601806B1
EP3601806B1 EP18705121.4A EP18705121A EP3601806B1 EP 3601806 B1 EP3601806 B1 EP 3601806B1 EP 18705121 A EP18705121 A EP 18705121A EP 3601806 B1 EP3601806 B1 EP 3601806B1
Authority
EP
European Patent Office
Prior art keywords
hydraulic cylinder
accumulator
pump
emergency
hydraulic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP18705121.4A
Other languages
German (de)
French (fr)
Other versions
EP3601806A1 (en
Inventor
Thomas Zeller
Rouven Hohage
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Voith Patent GmbH
Original Assignee
Voith Patent GmbH
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Filing date
Publication date
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Publication of EP3601806A1 publication Critical patent/EP3601806A1/en
Application granted granted Critical
Publication of EP3601806B1 publication Critical patent/EP3601806B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/002—Electrical failure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—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
    • F15B2211/20561—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
    • F15B2211/30—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
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—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
    • F15B2211/315—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
    • F15B2211/31582—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 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
    • F15B2211/32—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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/862—Control during or prevention of abnormal conditions the abnormal condition being electric or electronic failure
    • F15B2211/8623—Electric supply failure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/875—Control measures for coping with failures
    • F15B2211/8752—Emergency operation mode, e.g. fail-safe operation mode
    • 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 switching valve, which is labeled 71, an emergency solenoid valve, which is labeled 72, two pilot operated check valves, which are labeled 81 and 82, two pilot valves, which are labeled 91 and 92, three throttles, which are labeled 10, 11 and 12, a check valve, which is indicated with 14, an optional solenoid valve, which is indicated with 20, two optional pressure relief valves, which are indicated with 30 and 31 and two optional connections, which are indicated with 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 used as Synchronous cylinder be made out as in Figure 1 is indicated by the dashed second rod.
  • 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 pumps are driven by the pump drive 3 by means of a gear.
  • 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.
  • the position of the emergency connection changeover slide 71 shown is connected to a connection of a pump with a control line of the hydraulic cylinder, so that in one direction of rotation of the shaft 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.
  • 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 memory 5 is connected to the closing side of the hydraulic cylinder 6.
  • the collecting and equalizing tank 1 is also connected to the opening side of the hydraulic cylinder 6.
  • the state of the emergency switchover slide 71 is controlled via the emergency shutdown solenoid valve 72, which is located in a hydraulic line between the emergency switchover slide 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 continuously excited during operation, so that the emergency shut-off switchover slide 71 is in the position shown in FIG Figure 1 is in the position shown and the pilot valves 91, 92 are supplied with oil pressure by the accumulator 5 (ie the check valves 81, 82 can be unlocked in this state by the pilot valves 91, 92).
  • the emergency switchover slide 71 is designed such that it is in the in Figure 1 The position shown connects the corresponding connections of the pumps of the pump arrangement 2 with the connections of the hydraulic cylinder 6, while the collecting and equalizing tank 1 and the reservoir 5 are decoupled from the hydraulic cylinder, and in its other position, the pumps of the pump arrangement 2 are decoupled from the hydraulic cylinder 6 and the collecting and compensating tank 1 connects to the open side and the reservoir 6 to the close side of the hydraulic cylinder 6.
  • the emergency switchover slide is subjected to the pressure of the accumulator 5 on both sides. The effective area on which this pressure acts is to be selected to be of different sizes on the two sides.
  • the area on the right-hand side is larger, which has the effect that if the emergency shut-off solenoid valve 72 is excited, the emergency shut-off switchover slide 71 is in the position shown in FIG Figure 1 position shown. If the emergency shut-off solenoid valve 72 is de-energized, the memory 5 is separated from the right-hand side of the emergency shut-off changeover slide 71 and the Emergency closing changeover slide 71 is pushed into the other position by the forces acting on the left side.
  • the throttle 10 which is also called the "basic throttle" is located in the line connected to the open side of the hydraulic cylinder 6 before the emergency switchover slide 71, ie in the immediate vicinity of the hydraulic cylinder 6.
  • the throttle 11 is located in the line which connects the memory 5 to the remainder of the device.
  • the throttle 12 is located in the line between the emergency switchover slide 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 shutdown function).
  • a line is also provided which connects one of the lines from the pump arrangement 2 to the hydraulic cylinder 6 with the accumulator 5.
  • the check valve 14 is arranged in this line in such a way that no hydraulic fluid can pass from the reservoir 5.
  • the Figure 1 shows only one of several possible alternatives, ie the case that the line with the check valve 14 connects the corresponding connection of the upper pump to the reservoir 5.
  • the line with the check valve 14 can also be connected to the corresponding connection of the lower pump.
  • the line with the check valve 14 can open out at any points on the lines from the pump arrangement 2 to the hydraulic cylinder 6.
  • the device can also include further emergency shut-off control valves (for example 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 for example an overspeed valve, etc.
  • connection 40 is located in the hydraulic line which connects the reservoir 5 with the rest of the device.
  • the emergency switchover slide 71 is in the position according to FIG Figure 1 , since the emergency closing solenoid valve 72 is energized.
  • the pilot solenoid valves 91, 92 controlled by the controller of the hydraulic machine are in the de-energized state.
  • the unlockable check valves 81, 82 in the control lines to the opening and closing side of the hydraulic cylinder 6 are also closed and the cylinder 6 is held in its position.
  • 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 made 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 delivery volume ratio of the two pumps of the pump arrangement 2 is adapted as precisely as possible to the differential cylinder.
  • 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 pump volume of the upper pump can be designed to be larger than required, since the excess amount of hydraulic fluid is pressed into the reservoir via the check valve 14 when the hydraulic cylinder 6 is closed. In the other direction of rotation of the shaft, the excess amount is made available by the collecting and equalizing container 1 and taken up again.
  • 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.
  • pressure relief valves 30, 31 can optionally be installed, one of which is connected to one of the lines between the releasable check valves (81, 81) and the emergency switchover slide (71)
  • 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 switchover slide 71 switches to the in relation to Figure 1 other position is pushed.
  • the "quasi-closed" hydraulic control circuit thus becomes an open circuit.
  • the memory 5 is connected to the close side of the hydraulic cylinder 6, the open side now being diverted into the collecting and equalizing tank 1.
  • the pressure to the pilot valves 91, 92 is also relieved, so that the releasable check valves 81, 82 close.
  • 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 emergency switchover slide valve 71 and the accumulator 1, 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 throttle 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 opening control side (i.e. the line between basic throttle 10 and the pump arrangement 2).
  • the actuating time would be via the basic throttle 10 can be limited. Only the pressure in the reservoir 5 would slowly increase due to an increased pump delivery rate.
  • 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 via the line with the check valve 14.
  • 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. If the line with the non-return valve 14 is connected to the line from the pump arrangement 2 to the opening side of the hydraulic cylinder 6, charging works in an analogous manner. For this, however, the pump arrangement 2 must be activated in such a way that it delivers in the direction of the opening side of the hydraulic cylinder 6.
  • 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 the opening and closing times of the hydraulic cylinder 6 required for the respective application 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 which is located in the same hydraulic line as the emergency closing solenoid valve 72, is optionally provided. By connecting this valve 20, the storage volume can now be used to close.
  • the quick-closing solenoid valve 20 is energized, causing the emergency closing changeover slide 71 to move into the position shown in FIG Figure 1 other position is pushed.
  • 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 is thus completely decoupled from the hydraulic cylinder 6.
  • the quick-closing valve 20 is de-energized again when a defined opening is reached.
  • the "fine control" is now transferred back to the variable-speed pump drive 3, and the machine can be synchronized again.
  • the memory 5 Since the memory 5 is emptied by a quick-action circuit, the memory 5 should be refilled as quickly as possible in this situation. 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. Thus, flow can flow through the open-side check valve 82, the close-side check valve 81 remains blocked. As a result, the oil displaced during opening is pressed from the hydraulic cylinder 6 via the line with the check valve 14 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.
  • 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 via the pump arrangement 2 is activated by opening the releasable check valves 81 and 82 initiated. 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.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.

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, einen Notschlussumstellschieber, welcher 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 Rückschlagventil, welches mit 14 bezeichnet ist, 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 switching valve, which is labeled 71, an emergency solenoid valve, which is labeled 72, two pilot operated check valves, which are labeled 81 and 82, two pilot valves, which are labeled 91 and 92, three throttles, which are labeled 10, 11 and 12, a check valve, which is indicated with 14, an optional solenoid valve, which is indicated with 20, two optional pressure relief valves, which are indicated with 30 and 31 and two optional connections, which are indicated with 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 used as Synchronous cylinder be made out as in Figure 1 is indicated by the dashed second rod. 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. In der in Figur 1 gezeigten Stellung des Notschlussumstellschiebers 71 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 Öffnen-Seite des Hydraulikzylinders 6 und der linke Anschluss der oberen Pumpe (über das entsperrbare Rückschlagventil 81) mit der Schließen-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 Öffnen-Seite des Hydraulikzylinders 6 und gleichzeitig pumpt die obere Pumpe Hydraulikflüssigkeit von der Schließen-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 are 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. In the in Figure 1 The position of the emergency connection changeover slide 71 shown is connected to a connection of a pump with a control line of the hydraulic cylinder, so that in one direction of rotation of the shaft 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 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 opening side of the hydraulic cylinder 6 and the left connection of the upper pump (via the releasable check valve 81) is connected to the closing side of the hydraulic cylinder 6. The other connections of the pumps are each connected directly 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 opening side of the hydraulic cylinder 6 and at the same time the upper pump pumps hydraulic fluid from the closing 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 none Hydraulic fluid flows into the collecting and equalizing tank 1 or is withdrawn from it (see below on synchronous cylinder). In the other case, only the differential delivery rate of the pumps is discharged 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.

Im Betriebszustand "Notschluss" oder "Schnellschluss", d.h. wenn sich der Notschlussumstellschieber 71 in der anderen Stellung als der in Figur 1 gezeigten befindet, ist der Speicher 5 mit der Schließen-Seite des Hydraulikzylinders 6 verbunden. In diesen Beiden Betriebszuständen ist ferner der Sammel- und Ausgleichsbehälter 1 der Öffnen-Seite des Hydraulikzylinders 6 verbunden. Die Steuerung des Zustands des Notschlussumstellschiebers 71 erfolgt über das Notschlussmagnetventil 72, welches sich in einer hydraulischen Leitung zwischen dem Notschlussumstellschieber 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 sich der Notschlussumstellschieber 71 in der in Figur 1 gezeigten Stellung befindet 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).In the "emergency closing" or "quick closing" operating state, ie when the emergency closing changeover slide 71 is in the position other than that in Figure 1 shown is located, the memory 5 is connected to the closing side of the hydraulic cylinder 6. In these two operating states, the collecting and equalizing tank 1 is also connected to the opening side of the hydraulic cylinder 6. The state of the emergency switchover slide 71 is controlled via the emergency shutdown solenoid valve 72, which is located in a hydraulic line between the emergency switchover slide 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 continuously excited during operation, so that the emergency shut-off switchover slide 71 is in the position shown in FIG Figure 1 is in the position shown and the pilot valves 91, 92 are supplied with oil pressure by the accumulator 5 (ie the check valves 81, 82 can be unlocked in this state by the pilot valves 91, 92).

Der Notschlussumstellschieber 71 ist so ausgebildet, dass er in der in Figur 1 gezeigten Stellung die entsprechenden Anschlüsse der Pumpen der Pumpenanordnung 2 mit den Anschlüssen des Hydraulikzylinders 6 verbindet, während der Sammel- und Ausgleichsbehälter 1 und der Speicher 5 vom Hydraulikzylinder entkoppelt sind, und in seiner anderen Stellung, die Pumpen der Pumpenanordnung 2 vom Hydraulikzylinder 6 entkoppelt und den Sammel- und Ausgleichsbehälter 1 mit der Öffnen-Seite und den Speicher 6 mit der Schließen-Seite des Hydraulikzylinders 6 verbindet. In Figur 1 ist erkennbar, dass der Notschlussumstellschieber auf beiden Seiten mit dem Druck des Speichers 5 beaufschlagt ist. Dabei ist die wirksame Fläche, auf die dieser Druck wirkt, auf den beiden Seiten unterschiedlich groß zu wählen. Die Fläche auf der rechten Seite ist größer, was bewirkt, dass sich falls das Notschlussmagnetventil 72 erregt ist, der Notschlussumstellschieber 71 in der in Figur 1 gezeigten Stellung befindet. Wird das Notschlussmagnetventil 72 entregt, so wird der Speicher 5 von der rechten Seite des Notschlussumstellschiebers 71 getrennt und der Notschlussumstellschieber 71 wird durch die Kräfte, die auf die linke Seite einwirken, in die andere Stellung geschoben.The emergency switchover slide 71 is designed such that it is in the in Figure 1 The position shown connects the corresponding connections of the pumps of the pump arrangement 2 with the connections of the hydraulic cylinder 6, while the collecting and equalizing tank 1 and the reservoir 5 are decoupled from the hydraulic cylinder, and in its other position, the pumps of the pump arrangement 2 are decoupled from the hydraulic cylinder 6 and the collecting and compensating tank 1 connects to the open side and the reservoir 6 to the close side of the hydraulic cylinder 6. In Figure 1 it can be seen that the emergency switchover slide is subjected to the pressure of the accumulator 5 on both sides. The effective area on which this pressure acts is to be selected to be of different sizes on the two sides. The area on the right-hand side is larger, which has the effect that if the emergency shut-off solenoid valve 72 is excited, the emergency shut-off switchover slide 71 is in the position shown in FIG Figure 1 position shown. If the emergency shut-off solenoid valve 72 is de-energized, the memory 5 is separated from the right-hand side of the emergency shut-off changeover slide 71 and the Emergency closing changeover slide 71 is pushed into the other position by the forces acting on the left side.

Die Drossel 10, die auch "Grunddrossel" genannt wird, befindet sich in der mit der Öffnen-Seite des Hydraulikzylinders 6 verbundenen Leitung noch vor dem Notschlussumstellschieber 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 Notschlussumstellschieber 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 connected to the open side of the hydraulic cylinder 6 before the emergency switchover slide 71, ie in the immediate vicinity of the hydraulic cylinder 6. The throttle 11 is located in the line which connects the memory 5 to the remainder of the device. The throttle 12 is located in the line between the emergency switchover slide 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 shutdown function).

Es ist ferner eine Leitung vorgesehen, die eine der Leitungen von der Pumpenanordnung 2 zum Hydraulikzylinder 6 mit dem Speicher 5 verbindet. In dieser Leitung ist das Rückschlagventil 14 so angeordnet, dass keine Hydraulikflüssigkeit vom Speicher 5 her passieren kann. Die Figur 1 zeigt nur eine von mehreren möglichen Alternativen, d.h. den Fall, dass die Leitung mit den Rückschlagventil 14 den entsprechenden Anschluss der oberen Pumpe mit dem Speicher 5 verbindet. Die Leitung mit dem Rückschlagventil 14 kann auch mit dem entsprechenden Anschluss der untern Pumpe verbunden sein. Die Leitung mit dem Rückschlagventil 14 kann dazu an beliebigen Punkten der Leitungen von der Pumpenanordnung 2 zum Hydraulikzylinder 6 münden.A line is also provided which connects one of the lines from the pump arrangement 2 to the hydraulic cylinder 6 with the accumulator 5. The check valve 14 is arranged in this line in such a way that no hydraulic fluid can pass from the reservoir 5. The Figure 1 shows only one of several possible alternatives, ie the case that the line with the check valve 14 connects the corresponding connection of the upper pump to the reservoir 5. The line with the check valve 14 can also be connected to the corresponding connection of the lower pump. For this purpose, the line with the check valve 14 can open out at any points on the lines from the pump arrangement 2 to the hydraulic cylinder 6.

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 (for example 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 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. It is assumed here as the initial state that the accumulator 5 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:

Der Notschlussumstellschieber 71 befindet sich in der Stellung gemäß Figur 1, da das Notschlussmagnetventil 72 erregt ist.The emergency switchover slide 71 is in the position according to FIG Figure 1 , since the emergency closing solenoid valve 72 is energized.

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 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 unlockable check valves 81, 82 in the control lines to the opening and closing side of the hydraulic cylinder 6 are also closed and the cylinder 6 is held in its position. 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. In Bezug auf die Konfiguration aus Figur 1 kann dazu das Pumpenvolumen der oberen Pumpe größer als benötigt ausgelegt sein, da die überschüssige Menge an Hydraulikflüssigkeit beim Schließen des Hydraulikzylinders 6 über das Rückschlagventil 14 in den Speicher gedrückt wird. In der Anderen Drehrichtung der Welle wird die überschüssige Menge vom Sammel- und Ausgleichsbehälter 1 bereitgestellt und wieder aufgenommen. Es ist klar, dass auf diese Weise bei jeder Bewegung des Hydraulikzylinders 6 in Schließen-Richtung der Speicher 5 etwas geladen wird. Durch ein (in Figur 1 nicht dargestelltes) Überdrückventil oder über optional vorhandene zusätzliche Verbraucher (Anschluss 40) kann eine Überladung des Speichers 5 verhindert 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 made 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 designed as a differential cylinder, the delivery volume ratio of the two pumps of the pump arrangement 2 is adapted as precisely as possible to the differential cylinder. 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. In terms of configuration Figure 1 For this purpose, the pump volume of the upper pump can be designed to be larger than required, since the excess amount of hydraulic fluid is pressed into the reservoir via the check valve 14 when the hydraulic cylinder 6 is closed. In the other direction of rotation of the shaft, the excess amount is made available by the collecting and equalizing container 1 and taken up again. It is clear that in this way, with each movement of the hydraulic cylinder 6 in the closing direction, the accumulator 5 is charged somewhat. Through a (in Figure 1 Overpressure valve (not shown) or via optionally available additional consumers (connection 40), overcharging of the store 5 can be prevented.

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.

Um die Vorrichtung gegen einen unzulässig hohen Druck abzusichern, können optional Druckbegrenzungsventile 30, 31 installiert sein, von denen jeweils eines an eine der Leitungen zwischen den entsperrbaren Rückschlagventilen (81, 81) und dem Notschlussumstellschieber (71) angeschlossen istTo protect the device against impermissibly high pressure, pressure relief valves 30, 31 can optionally be installed, one of which is connected to one of the lines between the releasable check valves (81, 81) and the emergency switchover slide (71)

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 der Notschlussumstellschieber 71 in die in Bezug auf Figur 1 andere Stellung geschoben wird. 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.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 switchover slide 71 switches to the in relation to Figure 1 other position is pushed. The "quasi-closed" hydraulic control circuit thus becomes an open circuit. The memory 5 is connected to the close side of the hydraulic cylinder 6, the open 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.

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 Notschlussumstellschieber 71 und dem Speicher 1, 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 emergency switchover slide valve 71 and the accumulator 1, 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.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 throttle 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 opening control side (i.e. the line between basic throttle 10 and the pump arrangement 2).

Dadurch, dass der Speicher 5 über die Leitung mit dem Rückschlagventil 14 mit der Schließen-Seite des Zylinders 6 verbunden ist, 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.Because the accumulator 5 is connected to the closing side of the cylinder 6 via the line with the non-return valve 14, even in the event of a fault that the pump drive 3 assumes a higher than the defined maximum speed in the closing direction, the actuating time would be via the basic throttle 10 can be limited. Only the pressure in the reservoir 5 would slowly increase due to an increased pump delivery rate.

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 über die Leitung mit dem Rückschlagventil 14 geladen wird. Die dafür nötige Differenz-Ölmenge wird von der Pumpenanordung 2 über eine entsprechende Leitung vom Sammel- und Ausgleichsbehälter 1 angesaugt. Ist die Leitung mit dem Rückschlagventil 14 an die Leitung von der Pumpenanordnung 2 zur Öffnen-Seite des Hydraulikzylinders 6 angeschlossen, so funktioniert das Laden analog. Dazu muss jedoch die Pumpenanordnung 2 so angesteuert werden, dass diese in Richtung Öffnen-Seite des Hydraulikzylinders 6 fördert.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 via the line with the check valve 14. 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. If the line with the non-return valve 14 is connected to the line from the pump arrangement 2 to the opening side of the hydraulic cylinder 6, charging works in an analogous manner. For this, however, the pump arrangement 2 must be activated in such a way that it delivers in the direction of the opening side of the hydraulic cylinder 6.

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 the opening and closing times of the hydraulic cylinder 6 required for the respective application 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 der Notschlussumstellschieber 71 in die in Bezug auf Figur 1 andere Stellung geschoben wird. 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 ist damit vom Hydraulikzylinder 6 vollständig entkoppelt.In order to then achieve a faster closing time (for example in the case of a hydropower regulator in the event of a load shedding), the quick-closing solenoid valve 20, which is located in the same hydraulic line as the emergency closing solenoid valve 72, is optionally provided. By connecting this valve 20, the storage volume can now be used to close. In the process, the quick-closing solenoid valve 20 is energized, causing the emergency closing changeover slide 71 to move into the position shown in FIG Figure 1 other position is pushed. 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 is thus completely decoupled from the hydraulic cylinder 6.

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, e.g. after a load shedding in a water turbine, the quick-closing valve 20 is de-energized again when a defined opening is reached. At the same time, the "fine control" is now transferred back to the variable-speed pump drive 3, and the machine can be synchronized again.

Da durch einen Schnellschluss der Speicher 5 entleert wird, 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 82 durchströmt werden, das schließen-seitige Rückschlagventil 81 bleibt gesperrt. Dadurch wird das beim Auffahren verdrängte Öl aus dem Hydraulikzylinder 6 über die Leitung mit dem Rückschlagventil 14 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.Since the memory 5 is emptied by a quick-action circuit, the memory 5 should be refilled as quickly as possible in this situation. 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. Thus, flow can flow through the open-side check valve 82, the close-side check valve 81 remains blocked. As a result, the oil displaced during opening is pressed from the hydraulic cylinder 6 via the line with the check valve 14 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.If the oil temperature falls below a defined value, the regulation via the pump arrangement 2 is activated by opening the releasable check valves 81 and 82 initiated. 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), 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, and the device furthermore comprising a collecting and compensation vessel (1), an emergency closure solenoid valve (72), an emergency closure switching slide (71), a check valve (14) and at least 2 throttles (10, 11, 12), wherein the emergency closure switching slide (71) is configured, and is connected to the pump arrangement (2), the hydraulic cylinder (6), the collecting and compensation vessel (1) and the accumulator (5), in such a way that, in a first position of the emergency closure switching slide (71), 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 the accumulator (5) and the collecting and compensation vessel (1) are decoupled from the hydraulic cylinder (6), and in a second position of the emergency closure switching slide (71), 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 pump arrangement (2) is decoupled from the hydraulic cylinder (6), and wherein furthermore 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 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), and the device furthermore comprising lines which connect the accumulator (5) respectively to the two check valves (81, 82) and the emergency closure switching slide (71), in order for it to be possible to unblock the check valves (81, 82) and to keep the emergency closure switching slide (71) in the first position, 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 emergency closure switching slide (71), or in the line between the accumulator (5) and the emergency closure switching slide (71), and wherein the check valve (14) is arranged in a line, which connects one of the lines from the pump arrangement (2) to the hydraulic cylinder (6) with the accumulator (5), in such a way that no hydraulic fluid from the accumulator (5) can pass through the check valve (14).
  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 emergency closure switching slide (71), or in the line between the accumulator (5) and the emergency closure switching slide (71) .
  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 emergency closure switching slide (71).
  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 push the emergency closure switching slide (71) into the second position 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 emergency closure switching slide (71).
  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.
EP18705121.4A 2017-03-29 2018-02-08 Apparatus for controlling a hydraulic machine Active EP3601806B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017106700.0A DE102017106700B3 (en) 2017-03-29 2017-03-29 Device for controlling a hydraulic machine
PCT/EP2018/053164 WO2018177641A1 (en) 2017-03-29 2018-02-08 Apparatus for controlling a hydraulic machine

Publications (2)

Publication Number Publication Date
EP3601806A1 EP3601806A1 (en) 2020-02-05
EP3601806B1 true EP3601806B1 (en) 2021-01-06

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EP18705121.4A Active EP3601806B1 (en) 2017-03-29 2018-02-08 Apparatus for controlling a hydraulic machine

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US (1) US10962032B2 (en)
EP (1) EP3601806B1 (en)
CN (1) CN110520634B (en)
CA (1) CA3058355C (en)
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WO (1) WO2018177641A1 (en)

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DE102017106693B3 (en) * 2017-03-29 2018-05-30 Voith Patent Gmbh Device for controlling a hydraulic machine
FR3123312B1 (en) * 2021-05-28 2024-01-12 Safran Aircraft Engines Feathering of the electrohydraulic system with pump by valves in the rotating mark
DE102022121962A1 (en) * 2022-08-31 2024-02-29 Bucher Hydraulics Ag Electric-hydraulic actuator

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EP2024647A1 (en) * 2006-06-02 2009-02-18 Brueninghaus Hydromatik Gmbh Hydrostatic drive having volumetric flow compensation
CN101813104A (en) * 2009-12-31 2010-08-25 上海汇益控制系统股份有限公司 Quickly-propelled low-power and energy-saving hydraulic servo-actuator
CN101858094B (en) * 2010-06-10 2016-07-06 中国重汽集团青岛重工有限公司 Hydraulic hybrid power system of excavator
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CN103062166A (en) * 2013-01-24 2013-04-24 中国铁建重工集团有限公司 Compound pumping electro-hydraulic system
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US20200096015A1 (en) 2020-03-26
CN110520634B (en) 2020-09-04
US10962032B2 (en) 2021-03-30
CN110520634A (en) 2019-11-29
CA3058355A1 (en) 2018-10-04
WO2018177641A1 (en) 2018-10-04
DE102017106700B3 (en) 2018-05-17
CA3058355C (en) 2024-05-07
EP3601806A1 (en) 2020-02-05

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