WO2010078887A1 - Circuit de commande hydraulique - Google Patents

Circuit de commande hydraulique Download PDF

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Publication number
WO2010078887A1
WO2010078887A1 PCT/EP2009/008415 EP2009008415W WO2010078887A1 WO 2010078887 A1 WO2010078887 A1 WO 2010078887A1 EP 2009008415 W EP2009008415 W EP 2009008415W WO 2010078887 A1 WO2010078887 A1 WO 2010078887A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
valve
control circuit
cylinder
piston
Prior art date
Application number
PCT/EP2009/008415
Other languages
German (de)
English (en)
Inventor
Hans-Peter Janousch
Original Assignee
Robert Bosch 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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2010078887A1 publication Critical patent/WO2010078887A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/002—Electrical failure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D7/00—Controlling wind motors 
    • F03D7/02—Controlling wind motors  the wind motors having rotation axis substantially parallel to the air flow entering the rotor
    • F03D7/022—Adjusting aerodynamic properties of the blades
    • F03D7/0224—Adjusting blade pitch
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/004—Fluid pressure supply failure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2270/00—Control
    • F05B2270/50—Control logic embodiment by
    • F05B2270/506—Control logic embodiment by hydraulic means, e.g. hydraulic valves within a hydraulic circuit
    • 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
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief 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
    • F15B2211/80—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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • the invention relates to a hydraulic control circuit according to the preamble of patent claim 1.
  • EP 1 413 810 A1 an adjusting device for a turbine valve for controlling the gas or steam supply of a turbine or a process fitting for controlling a fluid, a pitch adjustment of a wind turbine or the like is disclosed.
  • Such adjusting devices usually have an actuator which is embodied in the subject matter of EP 1 413 810 A1 as an electric spindle drive.
  • a control device for example, an opening cross-section of a valve for adjusting the steam supply.
  • the valve should be reset - or, in the case of a pinwheel, the pitch angle - to prevent damage to the system.
  • the spindle drive associated with a toggle mechanism which is locked in normal operation, ie with sufficient power supply in an extended position in which a biasing spring is stretched.
  • This toggle acts on a valve body of the valve (on a gas turbine) or on the adjusting mechanism for adjusting the pitch angle of a wind turbine.
  • the locking of the toggle lever takes place only with sufficient power supply; In the event of a power failure, the locking mechanism releases the toggle lever so that it is displaced from its extended position into its bent position via the pretensioning spring, and the valve member or the pitch angle adjustment mechanism is returned to its predetermined basic position in accordance with this adjustment path.
  • the disadvantage of this solution is that the toggle mechanism is quite complex in construction and requires considerable space, so that the device-technical effort is significant.
  • the invention is based on the object to provide a control circuit for a control device that allows an emergency operation with low device complexity and high reliability.
  • a hydraulic control circuit used in particular for wind turbines has a cylinder with a piston which divides the cylinder into a first and second pressure chamber.
  • the cylinder can be controlled via an electrically actuated directional control valve.
  • a valve spool of the directional control valve is spring-loaded in the direction of a fail-safe position. In this position, for moving the piston into a fail-safe position, the first cylinder chamber of the cylinder is relieved via the directional valve to a tank and the piston is acted upon by the system via the second cylinder chamber via the directional control valve.
  • the hydraulic control circuit thus has an apparatus of extremely simple construction emergency operation, which is preferably used in a wind turbine for adjusting rotor blades in a flag position.
  • a pump line with a first check valve is connected to a pressure connection of the directional control valve, wherein a hydraulic accumulator is connected by the pump line between the first check valve and the pressure connection.
  • the hydraulic accumulator can advantageously be charged during the normal use of the control circuit by the pump and, for example, a failure of the pump or a pump to the driving motor; ensure the pressure medium supply of the cylinder for moving into the fail-safe position.
  • a pressure switch is provided in the control circuit, which interrupts a power supply of the directional control valve at a system pressure drop, whereby the directional control valve switches to the fail-safe position.
  • the piston of the cylinder with a locking device can be locked to prevent the procedure of the piston from the fail-safe position at a system pressure loss.
  • the locking device is a hydraulically operated check valve. This is arranged in the pressure medium path between the second cylinder chamber and a working port of the directional control valve and prevents a pressure relief of the second cylinder chamber in a fail-safe position of the directional control valve to a tank.
  • the control line for unlocking the check valve advantageously branches off between the first check valve and the directional control valve from the pump line. Such a check valve can be easily and inexpensively integrated into the hydraulic control circuit.
  • the locking device is designed as a rod clamping device for mechanically clamping a piston rod of the cylinder, which has a high degree of robustness.
  • the bar clamping device advantageously has a cone-shaped, the
  • Piston embracing clamping bush which in turn is encompassed by an annular piston.
  • the annular piston is then acted upon by a spring force of springs for locking the piston rod in the rising direction of the diameter of the cone-shaped clamping bush and for unlocking the piston rod with a control pressure against the spring force.
  • the control pressure is tapped via a control line between the first check valve and the directional control valve from the pump line.
  • the directional control valve can be designed as a conventional 4-way valve which, in addition to the fail-safe position, has two further positions counter to the spring-loaded position. clamped direction of the valve slide for retracting and extending the piston rod of the cylinder and has a blocking position.
  • a standard product can be used inexpensively for the directional control valve.
  • the pressure switch is connected via a pressure line between the first non-return and the directional control valve with the pump line, wherein a piston of the pressure switch is acted upon by an adjustable spring against the pressure force of the system pressure. It is thus a conventional pressure switch for the control circuit can be used.
  • the pressure switch is advantageously connected to the power supply of the directional control valve with a control circuit.
  • a switching relay is arranged in series with the pressure switch, which interrupts the power supply of the directional control valve in case of interruption of the control circuit by the pressure switch due to a system pressure drop.
  • a pressure limiting valve which limits the system pressure in the pump line between the first non-return valve and the directional control valve. Furthermore, an adjustable throttle valve and an electrically actuated shut-off valve are provided for controlled system pressure relief, which are each arranged parallel to the pressure relief valve.
  • the hydraulic control circuit is used for example in wind turbines, wherein the cylinder can be used for hydraulic adjustment of rotor blades of the wind turbine.
  • FIG. 1 shows a hydraulic circuit diagram of a hydraulic control circuit according to a first embodiment
  • FIG. 2 shows a hydraulic circuit diagram of the hydraulic control circuit according to a second embodiment.
  • FIG. 1 shows a hydraulic circuit diagram with a hydraulic control circuit 1 according to a first embodiment.
  • the control circuit 1 is used to drive an adjusting device in the form of an actuating cylinder or cylinder 2.
  • Such a control circuit 1 is used for example for the hydraulic pitch of rotor blades in a wind turbine. In wind turbines, the flow energy of the wind is converted into usable rotational energy.
  • the angle of attack (pitch angle) of the rotor blades is set as a function of the wind force to the wind via the cylinder 2 of the control circuit 1 in order to make optimal use of the wind power.
  • control circuit 1 In the event of a defect of the control circuit 1, for example due to interruption of a power supply or due to the failure of a hydraulic pump, it is necessary for safe operation of the wind power plant that the rotor blades are adjusted to their feathered position in which the system is aerodynamically decelerated.
  • the cylinder 2 is moved in this case in a fail-safe position.
  • the control circuit 1 has an emergency operation or a fail-safe function in which, independently of, for example, the power supply or the pump, the cylinder 2 and thus the rotor blades can be moved into the fail-safe position or flag position.
  • the control circuit 1 in FIG. 1 has a pump connection P connected to a pump and a tank connection T connected to a tank.
  • the pump connection P is via a pump line 3 with a pressure connection PW
  • the tank connection T is via a tank line 4 a tank connection TW of an electrically actuated 4-way valve 6 in pressure medium connection.
  • a piston 19 with a piston rod 20 divides the cylinder 2 into a piston rod-side first pressure chamber or annular space 21 and a bottom-side two th pressure chamber or cylinder chamber 22, wherein the first and on the cylinder chamber 22, the second working line 16 and 18 is connected to the annular space 21.
  • the directional control valve 6 is a conventional 4-way valve, which is known for example from the data sheet RD 29035 of the applicant.
  • This is a continuously adjustable directional control valve with four positions c, a, 0 and b, wherein the switching position c is a basic position in which a biased by a spring 26 with a spring valve spool is biased.
  • the basic position serves as a fail-safe position of the directional control valve 6, in which the pump line 3 with the cylinder space 22 and the tank line 4 with the annular space 20 of the cylinder 2 are in fluid communication and the piston 19 of the cylinder 2 to the left in the figure 1 is moved.
  • the feathering position of the rotor blades is approached.
  • valve spool of the directional control valve 6 is continuously displaceable in the direction of the positions a, 0 and b via an electric magnet 28.
  • the valve spool of the directional control valve 6 is continuously displaceable in the direction of the positions a, 0 and b via an electric magnet 28.
  • the positions a of the annular space 21 of the cylinder 2 is connected via the working line 16 with the tank line 4 and the cylinder chamber 22 via the working line 18 to the pump line 3, whereby the piston 19 is acted upon by the cylinder chamber 22 with working pressure and in ' the figure 1 is moved to the left.
  • the cylinder chamber 22 is relieved via the directional control valve 6 to the tank and the annular space 21 with the pump line 3 in pressure medium connection, whereby the working pressure on the piston 19 acts from the annulus and this moves in the figure 1 to the right becomes.
  • the position 0 is a blocking position in which the connection between the working ports 16, 18 and the pump and tank line 3, 4 is locked.
  • the electric magnet 28 is controlled by a control electronics 30.
  • This has a power supply 32, 34, to which a control circuit 36 of a pressure switch 37 is connected.
  • a switching relay 38 is arranged in series with the pressure switch 37, which interrupts the power supply 32 of the directional control valve 6 in an interruption of the control circuit 36 by the pressure switch 37, which is indicated by a switching symbol in the power supply 32, 34.
  • the pressure switch 37 is connected via a pressure line 40 to the pump line 3 in pressure medium connection.
  • a piston of the pressure switch 37 is over a adjustable spring 42 is acted upon against a pressure force of the system pressure with a spring force, the pressure switch 37 interrupts the control circuit 36 at a spring-biased position of the piston.
  • a check valve 44 is arranged, which prevents, for example, in the case of failure of the pump pressure fluid return to the pump.
  • a hydraulic accumulator 45 is connected between the check valve 44 and the pressure port P of the directional control valve 6, which can be designed as a bladder accumulator. This is charged by the pump via the pump line 3.
  • a pressure limiting valve 46 is provided, which is arranged between the pump line 3 and the tank line 4. Parallel to the pressure limiting valve 46, an adjustable throttle valve 48 and a check valve 50 are provided, which can serve for example for maintenance of externally controlled system pressure relief of the control assembly 1.
  • a hydraulically releasable check valve 52 is arranged in the second working line 18 to the cylinder chamber 22 of the cylinder 2. This prevents a pressure relief of the cylinder chamber 22 in a fail-safe position of the directional control valve 6, which is explained in more detail below.
  • a control line 54 for unlocking the check valve 52 branches off between the check valve 44 and the directional control valve 6 from the pump line 3.
  • the directional control valve 6 In order to move the piston rod 20 in FIG. 1 to the left in order, for example, to bring the rotor blades of the wind power plant into the feathering position, the directional control valve 6, as already described above, is switched into the positions a against the spring force of the spring 26.
  • a pump delivers pressure medium via the check valve 44, the pump line 3 and the second working line 18 with the check valve 52 which is hydraulically unlocked via the control line 54 to the cylinder block.
  • the piston 19 is acted upon by the cylinder chamber 22 with a working pressure and moves the piston rod 20 to the left, wherein pressure medium from the annular space 20 via the first working line 16, the directional control valve 6 and the tank line 4 to the tank port T. is displaced.
  • the hydraulic accumulator 45 is charged with the prevailing system pressure in the pump line 3, and the piston of the pressure switch 37 is acted upon by the system pressure from the pump line 3, wherein the control circuit 36 is closed.
  • the directional control valve 6 For moving the piston rod 20 in the figure 1 to the right, the directional control valve 6 is switched to the positions b.
  • the piston 19 of the cylinder 2 is acted upon by the annular space 21 with the working pressure and moves the piston rod 20 to the right, wherein pressure fluid from the second pressure chamber 22 via the system pressure from the pump line 3 unlocked check valve 52, via the directional control valve 6 and the tank line 4 to the tank port T.
  • the directional control valve 6 is switched to the blocking position 0.
  • the piston rod 20 is moved into a fail-safe position, ie the rotor blades are adjusted to the flag position.
  • the hydraulic accumulator 45 supplies the control circuit 1 with pressure medium, wherein the system pressure in the pump line 3 drops continuously. From a certain system pressure in the pump line 3, the pressure switch 37 interrupts the control circuit 36. Thus, the switching relay 38 is no longer energized and interrupts the power supply 32, 34 of the directional control valve 6, whereby the valve spool of the directional control valve 6 via the spring force of the spring 26 in the fail-safe position c is shifted.
  • FIG. 2 discloses a second exemplary embodiment of the control circuit 1.
  • the difference from the first exemplary embodiment from FIG. 1 lies in the locking device, which here as a rod clamping device 56 is used for mechanical locking
  • the check valve 52 with the control line 54 of Figure 1 is no longer formed in the control circuit 1.
  • the rod clamping device 56 has a cone-shaped, the piston rod 20 encompassing clamping bush 58.
  • the clamping bush 58 is in turn encompassed by an annular piston 60.
  • the annular piston 60 is displaced with a spring force of a spring assembly 62 in the ascending direction of the diameter of the cone-shaped clamping bush 58.
  • To unlock the annular piston 60 can be acted upon by a control pressure against the spring force, wherein the control pressure is tapped via a control line 64 between the check valve 44 and the directional control valve 6 of the pump line 3.
  • the control circuit 1 is supplied via the hydraulic accumulator 45 charged by the pump with a continuously decreasing system pressure until the pressure switch 37, the power supply 32, 34 of the directional control valve 6 interrupts.
  • the piston 19 with the piston rod 20 of the cylinder 2 is then moved to the left in Figure 2 due to the fail-safe position c of the directional control valve 6 in the fail-safe position.
  • the control pressure acting on the annular piston 60 of the rod clamping device 56 also drops. If the spring forces of the spring assembly 62 on the annular piston 60 predominate over the pressure forces of the control pressure, this is displaced and the piston rod 20 is clamped mechanically via the clamping bush 58.
  • the cylinder 2 is firmly held in the fail-safe position.
  • the control circuit could be designed such that the fail-safe position of the cylinder 2 is the retracted position of the piston rod 20.
  • a hydraulic control circuit having a cylinder having a piston dividing the cylinder into a ring and a cylinder space.
  • the piston is controllable via an electrically actuated directional control valve by a plurality of positions, wherein a valve spool of the directional control valve is spring-loaded in the direction of a fail-safe position.
  • a fail-safe position to move the piston into a fail-safe position, the first pressure chamber of the cylinder is relieved via the directional valve to a tank and the piston is pressurized with a system pressure via the directional valve via the second pressure chamber.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Analytical Chemistry (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Combustion & Propulsion (AREA)
  • Wind Motors (AREA)

Abstract

L'invention concerne un circuit de commande hydraulique comprenant un cylindre (2), muni d'un piston (19) qui divise le cylindre en une première et une seconde chambre de compression (21, 22). Le piston peut être réglé dans une pluralité de positions par l'intermédiaire d'une soupape directionnelle (6), commandée électriquement (6), un tiroir de soupape de la soupape directionnelle pouvant être sollicité par ressort en direction d'une position de sûreté en cas de défaillance. Dans cette position, pour déplacer le piston dans une position de sûreté en cas de défaillance, la première chambre de compression (21) du cylindre est déchargée par l'intermédiaire de la soupape directionnelle dans un réservoir, et le piston est alimenté en pression du système, par la seconde chambre de compression, par l'intermédiaire de la soupape directionnelle.
PCT/EP2009/008415 2009-01-10 2009-11-26 Circuit de commande hydraulique WO2010078887A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009004286A DE102009004286A1 (de) 2009-01-10 2009-01-10 Hydraulische Steuerschaltung
DE102009004286.5 2009-01-10

Publications (1)

Publication Number Publication Date
WO2010078887A1 true WO2010078887A1 (fr) 2010-07-15

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ID=41692918

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PCT/EP2009/008415 WO2010078887A1 (fr) 2009-01-10 2009-11-26 Circuit de commande hydraulique

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DE (1) DE102009004286A1 (fr)
WO (1) WO2010078887A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016139629A1 (fr) * 2015-03-04 2016-09-09 Meccanica Breganzese S.P.A. In Breve Mb S.P.A. Équipement hydraulique pour excavatrices et machines de fonctionnement en général
CN106837945A (zh) * 2017-03-23 2017-06-13 马鞍山工蜂智能科技有限公司 一种液压安全电气控制系统
CN111315999A (zh) * 2017-11-06 2020-06-19 采埃孚股份公司 阀、液压系统和机动车辆变速器
CN111532449A (zh) * 2020-04-30 2020-08-14 中国飞机强度研究所 应急保护装置及高压流体充压试验装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB713666A (en) * 1950-09-20 1954-08-18 Mercier Jean Improvements in or relating to arrangements for the remote control of elements such as fluid-tight doors in ships or for similar applications
DE19510071A1 (de) * 1995-03-20 1996-09-26 Klaus Brugger Vorrichtung zum Treiben eines Kolbens
DE19948997A1 (de) * 1999-10-11 2001-04-19 Aerodyn Eng Gmbh Blatteinzelverstellung für Windenergieanlagen
EP1413810A1 (fr) * 2002-10-22 2004-04-28 MOOG GmbH Dispositif de commande
DE102005052755A1 (de) * 2005-06-14 2006-12-21 Bosch Rexroth Aktiengesellschaft Hydraulisch betätigte Klemmeinheit und damit ausgeführte hydraulische Regelachse

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB713666A (en) * 1950-09-20 1954-08-18 Mercier Jean Improvements in or relating to arrangements for the remote control of elements such as fluid-tight doors in ships or for similar applications
DE19510071A1 (de) * 1995-03-20 1996-09-26 Klaus Brugger Vorrichtung zum Treiben eines Kolbens
DE19948997A1 (de) * 1999-10-11 2001-04-19 Aerodyn Eng Gmbh Blatteinzelverstellung für Windenergieanlagen
EP1413810A1 (fr) * 2002-10-22 2004-04-28 MOOG GmbH Dispositif de commande
DE102005052755A1 (de) * 2005-06-14 2006-12-21 Bosch Rexroth Aktiengesellschaft Hydraulisch betätigte Klemmeinheit und damit ausgeführte hydraulische Regelachse

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016139629A1 (fr) * 2015-03-04 2016-09-09 Meccanica Breganzese S.P.A. In Breve Mb S.P.A. Équipement hydraulique pour excavatrices et machines de fonctionnement en général
US10626577B2 (en) 2015-03-04 2020-04-21 Meccanica Breganzese S.P.A. In Breve Mb S.P.A. Hydraulic equipment for excavators and operating machines in general
CN106837945A (zh) * 2017-03-23 2017-06-13 马鞍山工蜂智能科技有限公司 一种液压安全电气控制系统
CN106837945B (zh) * 2017-03-23 2018-10-02 马鞍山工蜂智能科技有限公司 一种液压安全电气控制系统
CN111315999A (zh) * 2017-11-06 2020-06-19 采埃孚股份公司 阀、液压系统和机动车辆变速器
CN111532449A (zh) * 2020-04-30 2020-08-14 中国飞机强度研究所 应急保护装置及高压流体充压试验装置

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