EP3601806A1 - Dispositif de régulation d'une machine hydraulique - Google Patents

Dispositif de régulation d'une machine hydraulique

Info

Publication number
EP3601806A1
EP3601806A1 EP18705121.4A EP18705121A EP3601806A1 EP 3601806 A1 EP3601806 A1 EP 3601806A1 EP 18705121 A EP18705121 A EP 18705121A EP 3601806 A1 EP3601806 A1 EP 3601806A1
Authority
EP
European Patent Office
Prior art keywords
hydraulic cylinder
pump
memory
hydraulic
line
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.)
Granted
Application number
EP18705121.4A
Other languages
German (de)
English (en)
Other versions
EP3601806B1 (fr
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
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Voith Patent GmbH filed Critical Voith Patent GmbH
Publication of EP3601806A1 publication Critical patent/EP3601806A1/fr
Application granted granted Critical
Publication of EP3601806B1 publication Critical patent/EP3601806B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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 regulating a turbine, a pump or a pump turbine.
  • DE 27 13 867 A1 describes such a device (see FIG. 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 pressure oil source is a reservoir for the pressurized hydraulic medium.
  • the storage tank must be filled with the help of pumps and brought to the required working pressure and kept.
  • the object of the present invention is to provide a device for controlling a hydraulic machine, in which variable speed driven hydraulic constant displacement pumps are used, and which are the requirements for a hydraulic machine, eg in terms of positioning times, Notschlieigenschaftenigenschaften - even with failure of the pump, 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. According to the invention, this object is achieved by a device for controlling a hydraulic machine having the features of claim 1. Further advantageous embodiments of the device according to the invention will become apparent from the dependent therefrom dependent claims.
  • FIG. 1 Schematic structure of a device according to the invention
  • the apparatus comprises a collection and surge tank, designated 1, a pump assembly, designated 2, a variable speed pump drive, designated 3, a reservoir, designated 5, a hydraulic cylinder, designated 6 71, an emergency shut-off solenoid valve, designated 72, two pilot-operated check valves, designated 81 and 82, two pilot valves, designated 91 and 92, three throttles designated 10, 11 and 12, a check valve, designated 14, an optional solenoid valve, designated 20, two optional pressure relief valves, designated 30 and 31, and two optional ports, designated 40 and 50.
  • the arrow below the hydraulic cylinder 6 indicates the closing direction of the same.
  • the hydraulic cylinder 6 may 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 as Synchronous cylinder be made out, as indicated in Figure 1 by the dashed second rod. However, the hydraulic cylinder 6 can also be made as a differential cylinder with different volumes for closing and opening page.
  • the pump assembly 2 comprises two pumps with reversible conveying direction.
  • the two pumps are arranged on a shaft which is driven by the pump drive 3.
  • the pump drive 3 each comprise a motor and a frequency converter for each of the two pumps.
  • the further description relates to the embodiment shown in Figure 1.
  • one connection of a pump is connected to a control line of the hydraulic cylinder so that in one rotational direction of the shaft the one pump delivers hydraulic fluid in the direction of the hydraulic cylinder 6 and the other pump receives hydraulic fluid from the hydraulic cylinder 6.
  • the right port of the lower pump (via the pilot operated check valve 82) is connected to the open side of the hydraulic cylinder 6 and the left port of the upper pump (via the pilot operated check valve 81) to the closing side of the hydraulic cylinder 6.
  • the remaining connections of the pumps are each connected directly to the collection and expansion tank 1. That is, in one rotational direction of the shaft, the lower pump pumps hydraulic fluid from the accumulation and surge 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 to the accumulation and surge tank 1. In the other direction of rotation of the shaft, the volume flows are reversed.
  • the pumps used have designated pressure and suction ports, so preferably always the pressure ports with the hydraulic cylinder 6 and the suction ports are connected to the collection and surge tank 1.
  • the shaft of the pump assembly 2 is driven by the variable-speed pump drive 3, which is operable in both directions of rotation.
  • the pump drive 3 usually comprises an electric servomotor, which is electrically powered by a frequency converter.
  • the pilot-operated check valves 81 and 82 which are arranged in the connecting lines of the hydraulic cylinder 6 to the pump assembly 2 so as to prevent movement of the piston of the hydraulic cylinder in the unlocked state, are each connected to one of the pilot valves 91, 92. These are each connected to the accumulator 5 (via the valves 20 and 72). Opening of a pilot valve 91, 92 thus causes the unlocking of the associated check valve 81, 82.
  • the opening of the pilot valves 91, 92 is effected by the (electric) controller of the hydraulic machine in that they are energized. Each of the pilot valves 91, 92 can be separately energized.
  • the (spring-loaded) Not gleichmagnetventil 72 is always permanently energized during operation, whereby the Notschlußumstellschieber 71 is in the position shown in Figure 1 and the pilot valves 91, 92 are supplied by the accumulator 5 with oil pressure (ie, the check valves 81, 82 can be unlocked in this state by the pilot valves 91, 92).
  • the emergency shut-off valve 71 is designed such that in the position shown in FIG.
  • the throttle 10 which is also called “basic throttle” is located in the connected to the open side of the hydraulic cylinder 6 line before the emergency shut-off valve 71, ie in the immediate vicinity of the hydraulic cylinder 6.
  • the throttle 11 is located in the line
  • the The throttle 12 is located in the line between the Not gleichumstellschieber 71 and the collecting and surge tank 1.
  • one of the two chokes 11 or 12 is to be regarded as optional (see the comments on the emergency function ).
  • a line is provided which connects one of the lines from the pump arrangement 2 to the hydraulic cylinder 6 to the store 5.
  • the check valve 14 is arranged so that no hydraulic fluid can pass from the memory 5 ago.
  • Figure 1 shows only one of several possible alternatives, i. the case that the line with the check valve 14 connects the corresponding port of the upper pump with the memory 5.
  • the line with the check valve 14 may also be connected to the corresponding port of the lower pump.
  • the line with the check valve 14 can open at any point of the lines of the pump assembly 2 to the hydraulic cylinder 6.
  • the device may include other emergency shut-off control valves (eg, an overspeed valve, etc.). These can be connected via the port 50, which is located in the same hydraulic line as the emergency shut-off solenoid valve 72.
  • further consumers can be connected to the memory 5 via the connection 40.
  • the port 40 is located in the hydraulic line connecting the accumulator 5 to the rest of the device.
  • the emergency shut-off valve 71 is in the position according to FIG. 1, since the emergency closing solenoid valve 72 is energized.
  • the pilot valves 91 and 92 are energized via the controller, which leads to the opening of the pilot-operated check valves.
  • the hydraulic cylinder can be positioned directly over the variable speed pump drive 3. If the Hydraulic cylinder 6 is made as a synchronous cylinder is swallowed by the pump assembly 2, the same amount of oil suction side as the pressure side introduced into the cylinder. In this case, the two pumps of the pump assembly 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 assembly 2 is adapted as accurately as possible to the differential cylinder.
  • the resulting during the process of the hydraulic cylinder 6 differential oil quantity can be compensated via the corresponding suction pipes connected to the collection and expansion tank 1 and a small pendulum volume on the memory 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 provided by the collecting and surge tank 1 and resumed. It is clear that in this way with each movement of the hydraulic cylinder 6 in the closing direction of the memory 5 is slightly charged. By means of an overpressure valve (not shown in FIG. 1) or via optional additional consumers (connection 40), overcharging of the accumulator 5 can be prevented.
  • the pilot valves 91, 92 are de-energized, whereby the cylinder 6 can be held in its position again without applying energy.
  • the storage volume is no longer used in comparison with conventional systems for control purposes, since this task is completely taken over by the pump assembly 2.
  • the storage volume and thus the memory size can be drastically reduced. This also leads to a smaller collection and expansion tank 1, which in total the cost can be reduced.
  • optional pressure limiting valves 30, 31 may be installed, one of which is connected to one of the lines between the pilot-operated check valves (81, 81) and the Not gleichumstellschieber (71)
  • an emergency shutdown function is implemented, which makes it possible to shut down the system without power supply (or in the event of a defect in the variable-speed drive 3).
  • the permanently energized in operation Not gleichmagnetventil 72 is de-energized, whereupon the Notschlußumstellschieber 71 is pushed into the other in relation to Figure 1 position.
  • the "quasi-closed" hydraulic control circuit becomes an open circuit, and the accumulator 5 is connected to the closing side of the hydraulic cylinder 6, with the open side now being diverted into the accumulation and equalizing tank 1.
  • the pressure also becomes high relieved to the pilot valves 91, 92, so that the pilot-operated check valves 81, 82 close.
  • the reservoir 5 delivers a defined volume within defined pressure limits. Therefore, with the help of the basic throttle 10 and an additionally series-connected throttle 11 or 12, a defined closing time can be set reliably. If two throttles 11 and 12, which are additionally connected in series, are actually used, this results in greater flexibility and greater robustness compared to, for example, a line break in the line between the emergency shut-off valve 71 and the store 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 10 is formed during the process of the hydraulic cylinder 6 a dynamic pressure against which the pump assembly 2 acts, and therefore must be kept within certain limits (to be observed nominal pressures of the lines and components, power of the pump drive 3, etc.).
  • the memory 5 is monitored for its filling level or its system pressure by means of corresponding level and pressure sensors.
  • the volume of oil and the pressure in the accumulator 5 are kept at a defined maximum level during operation, regardless of the position of the hydraulic cylinder 6. This level will in the case of a used Gleichgangzylinders (see above), or if no other external consumers are connected to the memory 5 via the optional connection point 40, not or only very little change in operation.
  • the memory can be charged by means of the variable speed drive 3 and the electrically controlled unlockable check valves 81 and 82 regardless of the position of the hydraulic cylinder 6 during operation.
  • the pilot solenoid valves 91 and 92 must be in de-energized state, whereby the pilot-operated check valves 81 and 82 are closed.
  • the pump assembly 2 is now controlled so that it promotes towards the closing side of the hydraulic cylinder 6.
  • the position of the cylinder 6 does not change thereby, since the pilot-operated check valve 81 is closed in the open side of the hydraulic cylinder 6 and thus no oil can escape from the hydraulic cylinder 6.
  • the check valve 82 can be flowed through, whereby the pressure increases and the accumulator 5 is charged via the line with the check valve 14.
  • the necessary difference oil quantity is sucked by the pump assembly 2 via a corresponding line from the collection and expansion tank 1. If the line is connected to the check valve 14 to the line from the pump assembly 2 to the open side of the hydraulic cylinder 6, the loading works analogously.
  • the pump assembly 2 must be controlled so that it promotes toward the open side of the hydraulic cylinder 6.
  • the pump arrangement 2 is designed with respect 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 traversed solely via the pump drive 3.
  • the opening times may be significantly longer, in order to keep the dimension of the pump assembly 2 and the pump drive 3 as small as possible (space, spare parts costs, etc.), so designed be that the hydraulic cylinder 6 can be moved only 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.
  • the quick-closing solenoid valve 20 is energized, whereby the Not gleichumstellschieber 71 is pushed into the other with respect to Figure 1 position. At the same time is hydraulically separated by the pressure supply to the pilot valves 91 and 92, so that close the pilot-operated check valves 81 and 82 in the control lines. The pump assembly 2 is thus completely decoupled from the hydraulic cylinder 6.
  • the quick-closing valve 20 is de-energized once a defined opening has been reached.
  • the "fine control" is now transferred again 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 closing, the memory 5 should be replenished as quickly as possible in this situation. Since the regulator is active during and after completion of the synchronization process and restarting the turbine to the corresponding cylinder position and thereby the pump assembly 2 may not be used to load the memory 5, the procedure may be as follows: While the pump assembly 2, the hydraulic cylinder. 6 ascends to the corresponding opening, the pilot solenoid valves 91 and 92 are in the de-energized state. Thus, the open-side check valve 82 can be flowed through, the close-side check valve 81 remains locked. As a result, the oil displaced during startup is pressed out of the hydraulic cylinder 6 via the line with the check valve 14 back into the accumulator 5.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un dispositif de régulation d'une machine hydraulique, par exemple d'une turbine, d'une pompe ou d'une turbine de pompe, au moyen de pompes à cylindrée constante entraînées avec une vitesse de rotation variable, comprenant un dispositif d'exécution d'une coupure d'urgence, ledit dispositif de régulation se caractérisant par une faible consommation d'énergie et une grande efficacité tout en garantissant toutes les exigences de fonctionnement et de sécurité d'une machine hydraulique.
EP18705121.4A 2017-03-29 2018-02-08 Dispositif de régulation d'une machine hydraulique Active EP3601806B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017106700.0A DE102017106700B3 (de) 2017-03-29 2017-03-29 Vorrichtung zum Regeln einer hydraulischen Maschine
PCT/EP2018/053164 WO2018177641A1 (fr) 2017-03-29 2018-02-08 Dispositif de régulation d'une machine hydraulique

Publications (2)

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

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US (1) US10962032B2 (fr)
EP (1) EP3601806B1 (fr)
CN (1) CN110520634B (fr)
CA (1) CA3058355C (fr)
DE (1) DE102017106700B3 (fr)
WO (1) WO2018177641A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017106693B3 (de) * 2017-03-29 2018-05-30 Voith Patent Gmbh Vorrichtung zum Regeln einer hydraulischen Maschine
FR3123312B1 (fr) * 2021-05-28 2024-01-12 Safran Aircraft Engines Mise en drapeau du système électrohydraulique avec pompe par clapets dans le repère tournant
DE102022121962A1 (de) * 2022-08-31 2024-02-29 Bucher Hydraulics Ag Elektrisch-hydraulischer Aktor
JP2024047729A (ja) * 2022-09-27 2024-04-08 いすゞ自動車株式会社 ポンプシステム及びそれを備えた車両
DE102023134581B3 (de) * 2023-12-11 2024-11-21 Voith Patent Gmbh Vorrichtung zum Regeln einer hydraulischen Maschine vom Typ Kaplan
DE102024117954A1 (de) * 2024-06-26 2025-12-31 Thyssenkrupp Ag Manuelle Notschaltung für ein Hydrauliksystem

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JPS6048634B2 (ja) 1976-03-29 1985-10-28 株式会社東芝 水力機械のガイドベ−ン閉鎖装置
EP2024647A1 (fr) * 2006-06-02 2009-02-18 Brueninghaus Hydromatik Gmbh Mecanisme d'entrainement hydrostatique avec equilibrage des volumes
CN101813104A (zh) * 2009-12-31 2010-08-25 上海汇益控制系统股份有限公司 一种快速推进的低功率节能型液压伺服执行机构
CN101858094B (zh) * 2010-06-10 2016-07-06 中国重汽集团青岛重工有限公司 挖掘机液压混合动力系统
DE102010053811A1 (de) 2010-12-08 2012-06-14 Moog Gmbh Störungssicheres Betätigungssystem
CN102155476B (zh) * 2011-03-28 2013-11-06 上海交通大学 基于pwm无节流损失的阀控调节系统的调节方法
KR101339921B1 (ko) * 2011-09-28 2013-12-10 주재석 유압 실린더용 유압장치
JP5956184B2 (ja) * 2012-02-27 2016-07-27 株式会社小松製作所 油圧駆動システム
CN103062166A (zh) * 2013-01-24 2013-04-24 中国铁建重工集团有限公司 一种复合型泵送电液系统
DE102013008047A1 (de) 2013-05-13 2014-11-13 Robert Bosch Gmbh Drehzahlvariabler Antrieb mit zwei Pumpen und einem Differenzialzylinder
DE102013212937A1 (de) 2013-07-03 2014-07-10 Voith Patent Gmbh Vorrichtung zum Öffnen und Schließen der Leitschaufeln einer hydraulischen Maschine
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US10344784B2 (en) * 2015-05-11 2019-07-09 Caterpillar Inc. Hydraulic system having regeneration and hybrid start

Also Published As

Publication number Publication date
CA3058355C (fr) 2024-05-07
WO2018177641A1 (fr) 2018-10-04
US10962032B2 (en) 2021-03-30
CA3058355A1 (fr) 2018-10-04
CN110520634A (zh) 2019-11-29
DE102017106700B3 (de) 2018-05-17
US20200096015A1 (en) 2020-03-26
EP3601806B1 (fr) 2021-01-06
CN110520634B (zh) 2020-09-04

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