[go: up one dir, main page]

WO2012104047A1 - Dispositif de réglage hydraulique - Google Patents

Dispositif de réglage hydraulique Download PDF

Info

Publication number
WO2012104047A1
WO2012104047A1 PCT/EP2012/000383 EP2012000383W WO2012104047A1 WO 2012104047 A1 WO2012104047 A1 WO 2012104047A1 EP 2012000383 W EP2012000383 W EP 2012000383W WO 2012104047 A1 WO2012104047 A1 WO 2012104047A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
control
pressure
switching
relief
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.)
Ceased
Application number
PCT/EP2012/000383
Other languages
German (de)
English (en)
Inventor
Richard Tauber
Udo FRÖHLICH
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.)
Robert Bosch GmbH
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 WO2012104047A1 publication Critical patent/WO2012104047A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/122—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston
    • F16K31/1225—Actuating devices; Operating means; Releasing devices actuated by fluid the fluid acting on a piston with a plurality of pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/44—Mechanical actuating means
    • F16K31/56—Mechanical actuating means without stable intermediate position, e.g. with snap action
    • 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

Definitions

  • the invention relates to an actuating arrangement for valves.
  • EP 1 413 810 A1 discloses a generic actuating arrangement for a turbine valve for controlling the gas or steam supply of a turbine or for a process fitting for controlling a process flow in process engineering. Such adjusting arrangements usually have an actuator which is embodied in the subject matter of EP 1 413 810 A1 as an electric spindle drive. In a gas turbine can be
  • Such a toggle mechanism requires a considerable device complexity and also takes up a relatively large amount of space to complete.
  • DE 10 2009 021 668 A1 of the applicant discloses an actuating arrangement in which a valve is actuated via a control drive and a switching fitting arranged in series via a switching drive.
  • the invention has the object to perform a hydraulic actuator with improved reliability. This object is achieved by a hydraulic actuator assembly with the features of
  • the hydraulic actuator assembly for valves for controlling process fluid streams, such as gas or vapor streams, is designed with a control valve whose
  • Opening cross section is adjustable by means of a variable speed drive.
  • This control valve is executed with an emergency operation to the control valve in case of a fault in a
  • a hydraulically actuated emergency function valve is provided according to the invention parallel to the fitting valve, which is hydraulically adjustable via a control pressure for triggering the emergency operation in the direction of an open position.
  • the discharge flow path to the low pressure can be controlled regardless of the function of the valve fitting, so that a rapid closing of the Faucet is guaranteed. Since two parallel discharge paths are controlled with proper operation of the valve, this closing process is significantly accelerated compared to the conventional solutions, as these only one
  • the hydraulic actuator assembly for fittings with a variable adjustable via a control drive control valve and a arranged in series switching fitting is executed, which is switchable via a switching drive.
  • This has an effective pressure in the opening direction, which is acted upon via a main line with an opening pressure (high pressure) and the at least two parallel
  • Relief paths with low pressure can be connected to close the switch valve.
  • two relief valves connected in series are arranged, which are each adjustable from a blocking position to a relief position to close the switching valve.
  • the reliability is also significantly improved because with proper function, two parallel discharge paths are opened and so the return of the switching drive can be done very quickly in the closed position. Even in the case in which a valve of a discharge path is not working properly, by turning on the other, parallel
  • the emergency operation is carried out with a hydraulically preloaded energy storage, the stored energy acts for re-dividing in the emergency operation, wherein the energy storage by switching the
  • the emergency function valve is unloaded.
  • the emergency function valve is connected in parallel to the fitting valve, so that the pressure medium can flow out via both discharge flow paths to low pressure.
  • the emergency function valve is designed as a 2/2-way switching valve that locks the discharge flow path of the emergency operation to low pressure / tank in its blocking position and opens when switching.
  • a control valve is arranged in series with the control valve, which is adjustable by means of a hydraulic switching drive from a closed position to an open position, wherein the control pressure for actuating the emergency function valve is tapped on the switching drive.
  • a control switching valve is arranged, which is biased in the direction of a flow position and is adjustable in the direction of a leak-free locking position.
  • An advantageous development of the invention is to perform the switching drive with three discharge paths, each with two relief valves.
  • This design makes it possible to increase the safety level of the system to a high level, since the actuator assembly on the principle of a "2 of 3 control" is operable.
  • the hydraulic actuator assembly may be implemented with a bypass valve which is arranged parallel to the valve fitting and in the emergency operation opens a bypass channel to the tank.
  • This bypass channel thus forms an additional flow path for the pressure medium flowing to the low pressure, so that the closing process is further accelerated.
  • the bypass valve may be acted upon in the opening direction by a control pressure difference, which is tapped at a located in a drain to the low pressure diaphragm. This aperture is the switching of the valve from the outflowing pressure medium flows through, so that the control pressure difference for controlling the bypass valve is utilized.
  • the input of the emergency valve is connected to the drain upstream of the orifice.
  • the structure of the actuator assembly is particularly simple when an emergency function valve, a bypass valve and / or relief valve is designed in each case as a logic valve. According to the invention it is preferred if the energy storage of the emergency function is performed by a spring.
  • Such a spring may be hydraulically biased by a clamping cylinder having an effective in the direction of increasing the spring tension pressure chamber, the
  • Clamping is acted upon with pressure medium and is connected to relax with low pressure.
  • Figure 1 is a greatly simplified circuit diagram of an actuating arrangement according to the invention with a control valve and a control valve;
  • Figure 2 is a circuit diagram of a concrete solution of a hydraulic actuator assembly of an industrial steam turbine;
  • Figure 3 is a detail view of a variable speed drive of the actuator according to Figure 2 and
  • FIG. 4 shows an individual representation of a switching drive of the electric actuator according to FIG. 2.
  • the invention is explained below with reference to an embodiment in which the adjusting arrangement according to the invention is used for adjusting a steam volume flow of a steam turbine.
  • the actuator assembly according to the invention generally in valves for controlling process fluids, in pipelines, at
  • These can be linear or rotary movements.
  • FIG. 1 shows a greatly simplified circuit diagram of a steam turbine 1, the steam volume flow of which can be adjusted via an adjusting arrangement 2 according to the invention having a control fitting 4 and a switching fitting 6.
  • the control drive 8 is in
  • Control valve 4 is moved back to its closed position. To an excessive
  • Damping device 16 assigned, via which the movement of the valve is damped in the region of the end position.
  • the switching device 6 is moved via the switching drive 18 in the closed position, so that the steam supply is shut off via the steam line 21.
  • the steam supply via the steam line 21 is shut off by two independently effective devices.
  • the Switching drive 18 substantially from a spring accumulator 20, which is biased by a piston 22. This is in turn of the pressure in a pressure chamber 24 in
  • FIG. 2 shows the detailed circuit diagram of such a positioning arrangement with that of FIG
  • Variable speed control 8 actuated control valve 4 and the arranged in series, not shown switching valve, which is actuated by the switching drive 18.
  • control drive 8 and the switching drive 18 are connected via a control line 26, whose function will be explained in more detail below.
  • Figure 3 shows the variable speed drive 8 for the control valve 4 in a single representation.
  • variable speed drive 8 The basic principle and the individual functions of the variable speed drive 8 are known in the published patent application DE 10 2010 011 516.9, so that in the following only the components and functions required to understand the function of the control drive 8 are described and incidentally to the disclosure of the above Patent application is referenced. The applicant reserves the right to adopt individual passages of this document adapted to the present patent application, if this is necessary to improve the understanding.
  • the actuating cylinder 10 of the control drive 8 has a stationarily arranged cylinder 28, in which a valve piston 30 and a clamping piston 32 are received.
  • the valve piston 30 carries at its protruding from the cylinder 28 end portion a valve body 34 of the control valve 4, which is adjusted to close in the direction of a seat 36.
  • Both pistons 30, 32 each have a flange on which a spring of the spring accumulator 20 is supported.
  • the spring accumulator 20 is preloaded to the maximum extent.
  • the two piston collars 38, 40 define together with a cylinder intermediate bottom two pressure chambers 42, 44, which are designed substantially with identical end faces.
  • the clamping piston 32 is designed as a hollow piston and limited with a cylinder pin 48 and the intermediate bottom 46 two clamping chambers 50, 52, with a smaller
  • Cross-sectional area than the other two pressure chambers 42, 44 are executed and which are respectively connected via clamping lines 54, 56 with working ports A of a control valve 58, 60.
  • Both control valves 58, 60 are designed as electrically operated 2/2-way seat valves and biased by a spring in the illustrated basic position in which the tensioning line 54 is connected to a pressure line 62 and the tensioning line 56 with a supply line 64.
  • the pressure line 62 is connected to a connection of a hydraulic machine 66 and the supply line 64 to the other port of the hydraulic machine 66, so that a closed circuit is formed, through which the opening cross section of the control valves can be adjusted by adjusting the clamping piston 32 via the hydraulic machine 66.
  • the hydraulic machine 66 can be operated as a pump or hydraulic motor and is designed to reverse the direction of rotation and is driven by a drive, for example an electric motor 68.
  • the pressure line 62 and the supply line 64 are each a in the direction of
  • a check valve 76 is arranged, which blocks in the direction of the supply line 64.
  • the other pressure chamber 44 is connected via a discharge line 78 to the working port of a valve fitting 80. This is executed in the illustrated embodiment as a 3/2-way seat valve and an electromagnet in an illustrated
  • Biased switching position in which the discharge line 78 is connected to a channel 82 which is connected on the one hand to a pressure port P of the valve 80 and on the other hand opens into the pressure line 62, wherein, however, prevents a backflow from the channel 82 to the pressure line 62 through a further suction valve 84 is.
  • the channel 82 is also in fluid communication with the pressure line 74, so that in the illustrated switching position of the valve 80, the two pressure chambers 42, 44 are interconnected.
  • a pilot-operated check valve 86 Parallel to the valve valve 80, a pilot-operated check valve 86 is formed, which is arranged in a bypass channel 88, which opens on the one hand in the discharge line 78 and on the other hand into the channel 82.
  • the check valve 86 can by the pressure downstream of a nozzle 90 (seen in the relief direction) in the discharge line 78 are unlocked.
  • a tank port T of the valve fitting 80 is connected in the illustrated switching position with a storage channel 81, which opens between the Nachsaugventilen 72, 73 in the connected to the low-pressure accumulator 70 line section.
  • valve valve 80 When the valve valve 80 is switched off, this is biased by the force of a spring in a basic position in which the pressure port P is shut off and the
  • Working port A is connected to the storage channel 81 - according to the pressure chamber 44 is then relieved via the nozzle 90 to the low pressure.
  • Downstream (in the unloading direction) of the nozzle 90 branches off a control channel 96 from the discharge line 78, which runs in the control chamber of a logic valve as executed
  • Bypass valve 98 opens, so that this is biased by the pressure in the discharge line 78 in the closing direction.
  • a front-side port A of the bypass valve 98 is connected via a further nozzle 100 to the storage channel 81 and a radial port B of the bypass valve 98 is connected via a further control channel 102 upstream of the nozzle 90 with the discharge line 78.
  • the pressure medium flows in the spring-biased basic position of the valve valve 80 from the pressure chamber 44, so that above the nozzle 90, a pressure difference arises, the in
  • Opening direction acts on the bypass valve 98, so that it is opened against the force of a biasing spring and thus a parallel discharge flow path via the two control channels 102, 100 is controlled, which does not lead through the nozzle 90, so that the closing movement faster than during an outflow takes place via the nozzle 90.
  • the structure of the variable speed drive 8 substantially corresponds to that described in the abovementioned published patent application.
  • a special feature of the variable speed drive according to FIG. 3 is that parallel to
  • Valve valve 80 an emergency function valve 104 is provided, which also serves as a logic valve is executed and biased by a weak spring in its illustrated basic position in which a port A is shut off from a radial port B.
  • the port A is connected via a low pressure passage 106 and a nozzle 108 to the memory channel.
  • the radial port B of the emergency valve 104 is via a line 110 and the control channel 102 upstream (discharge direction) of the nozzle 90 with the
  • Relief line 78 connected.
  • An effective in the closing direction control chamber is connected to the above-mentioned control line 26, in which a designed as a 2/2-way seat valve control switching valve 1 12 is arranged, which via a spring in the illustrated
  • the control switching valve 1 12 can be electrically switched to a blocking position in which the control line 26 is shut off leak-free relative to the emergency function valve 104.
  • the pressurization of the aforementioned pressure chambers of the actuating cylinder 10 can be done in principle as described in the aforementioned patent application via the hydraulic machine 66 by multiple pumping and suction of pressure medium from the low pressure accumulator 70.
  • pressure medium is conveyed into the clamping space 50 and pushed out of the other clamping space 52.
  • the valve valve 80 is shown in its
  • valves In the event of a fault, for example a power failure, the said valves are de-energized, so that the valve valve 80 is switched to its spring-biased position, in which the terminals A and T are connected to each other.
  • the pressure medium then flows out of the pressure chamber 44 to the low-pressure accumulator 70, the movement of the
  • Armaturkolbens 30 is supported by the force of the spring accumulator 20.
  • pressure medium flows via the nozzle 90, so that the above-described pressure difference opens the bypass valve 98 and the further discharge flow path to the low-pressure accumulator 70 is opened.
  • the valve body 34 rests on the seat 36, so that the steam line 21 is shut off.
  • the control switching valve 112 is in its passage position
  • Relief flow path via the line 110 and the low pressure channel 106 is opened.
  • the switching drive 18 has a switching cylinder 1 14, the switch housing 1 16 actuates a valve body, not shown, of the control valve.
  • the stationary switching piston 22 of the switching cylinder 114 is acted upon via a switching spring 1 18 in the direction of a closed position of the switching device.
  • the switch housing 1 16 limits a switching pressure chamber 120, which acts on the switch housing 116 in the direction of opening the switch fitting 6 and thus acts counter to the spring force.
  • a main line 122 which on the other hand opens into a supply line 124, wherein in the main line 122, a check valve 126 is provided which allows a flow of pressure medium in the direction of the switching cylinder 1 14 and a flow of pressure medium from this in the direction of the supply line 124 blocks.
  • the supply line is arranged over another in the same sense
  • Check valve 128 connected to the pressure port of a switching pump 130, which is for example electrically operated and the suction port is connected via a suction line 132 to a low-pressure accumulator 134.
  • the supply line 124 branches off to a port A of a low-pressure valve 136, which in a spring-biased basic position ( Figure 4) the working port A with a
  • Tank connection T connects, which in turn is connected to a tank line 138.
  • the pressure in the supply line 122 is limited by a pressure limiting valve 140, which opens a pressure medium connection to the tank line 138 when a preset maximum pressure is exceeded.
  • the low pressure valve 136 can be electrically in a
  • the low-pressure valve 136 is designed as a directional seat valve in the illustrated embodiment.
  • a special feature of the circuit according to FIG. 4 is that the pressure chamber 120 can be connected to the low-pressure accumulator 134 via a total of three relief paths 142, 144, 146, in order to close the switching fitting 6.
  • Arranged in each of the relief paths 142, 144, 146 are two in series relief valves 148, 150, 152, 154, 156, 158 via which a pressure medium connection from the main conduit 122 and the respective relief path 142, 144, 146 to one to the low pressure accumulator 134 connected drain line 160 is connected, which is connected to the suction line 132.
  • Each of the relief valves 148-158 is designed as a logic valve. The three
  • Relief valves 150, 154, 158 are connected with their connections A via a respective aperture 162, 164, 166 to the main line 122. Radial connections B this
  • Relief valves 150, 154, 158 are associated with the terminals A of
  • Relief valves 148, 152 and 156 connected. Their radial ports B are then in turn connected to the drain line 160.
  • the relief valves 148 ... 158 are biased by a comparatively weak spring in the direction of its closed position.
  • a control pressure in a control chamber 168, 170, 172, 174, 176, 180 acts.
  • the control pressure in said control chambers 168-180 is over each one
  • the control port A of the relief control valve 184 is connected to the control spaces 172 and 180 via a control line, and the control port A of the third relief control valve 186 is then connected to the remaining control spaces 170 and 176, respectively.
  • control spaces of relief valves located in different relief paths are applied with low pressure or high pressure (pump pressure).
  • pump pressure low pressure or high pressure
  • the relief control valves 182, 184, 186 are adjusted to their home position by the force of their respective shift springs, in which the relief flow path is directed toward the low-pressure accumulator 134, so that the pressure fluid from the switching pressure chamber 120 via the three above-described relief paths 142 , 144, 146 for switching the pressure accumulator flows, so that the switching valve is switched by the force of the switching spring 118 in its blocking position.
  • This switching process takes place relatively quickly, wherein both the switching fitting 6 and the control valve 4 can be designed with a cushioning to avoid hard switching shocks. According to FIG.
  • the control line 26 is connected to the main line 122 via a pickup line 188, so that the pump pressure (high pressure) or the low pressure is effective in the control chamber of the emergency function valve 104 when the control switching valve 112 is open. Accordingly, at a pressure relief of the switching pressure chamber 120 and the emergency function valve 104 is opened, so that regardless of the control of the valve valve 80, the control valve 4 is moved in the direction of its closed position.
  • the temporal succession of the closing operation of the switching valve and the control valve can be determined for example via the control switching valve 112.
  • the volume of oil within the control line 26 is practically closed to the control drive, since it extends only to the control chamber of the emergency function valve 104.
  • the opening order can be determined by suitable design of the above
  • Controls are set, for example, by the use of Cardrige valves with damping pins, the response can be adjusted so that the control valve 4 is opened in front of the switch valve.
  • a hydraulic actuator assembly with a control valve which is designed with an emergency operation. The emergency operation can be triggered electrically and hydraulically. Further disclosed is an actuator assembly for fittings in which a
  • Control valve and a switch valve is provided, the switch valve over at least two parallel unloading paths are closed during the emergency operation

Landscapes

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

Abstract

Dispositif de réglage hydraulique qui comporte une vanne de réglage équipée d'un système d'actionnement d'urgence. Le système d'actionnement d'urgence peut être déclenché électriquement ou hydrauliquement. La présente invention concerne en outre un dispositif de réglage pour des vannes, comprenant une vanne de réglage et une vanne de commutation, la vanne de commutation pouvant être fermée par l'intermédiaire d'au moins deux chemins de délestage parallèles du système d'actionnement d'urgence.
PCT/EP2012/000383 2011-02-04 2012-01-27 Dispositif de réglage hydraulique Ceased WO2012104047A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102011010399 2011-02-04
DE102011010399.6 2011-02-04
DE102011012305.9 2011-02-25
DE102011012305.9A DE102011012305B4 (de) 2011-02-04 2011-02-25 Hydraulische Stellanordnung

Publications (1)

Publication Number Publication Date
WO2012104047A1 true WO2012104047A1 (fr) 2012-08-09

Family

ID=46547091

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2012/000383 Ceased WO2012104047A1 (fr) 2011-02-04 2012-01-27 Dispositif de réglage hydraulique

Country Status (2)

Country Link
DE (1) DE102011012305B4 (fr)
WO (1) WO2012104047A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014012694B3 (de) 2014-09-01 2016-02-25 Böhner-EH GmbH Hydraulische Vorrichtung
US10900504B2 (en) 2015-12-31 2021-01-26 Westinghouse Electric Company Llc Hydraulic apparatus and hydraulic appliance usable therein

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10152414A1 (de) * 2001-08-29 2003-05-08 Bosch Rexroth Ag Hydraulikzylinder
EP1413810A1 (fr) 2002-10-22 2004-04-28 MOOG GmbH Dispositif de commande
DE102009021668A1 (de) 2009-05-16 2010-11-18 Robert Bosch Gmbh Stellanordnung, Schaltantrieb für eine derartige Stellanordnung und Ventilanordnung für eine derartige Stellanordnung
DE102010011516A1 (de) 2010-03-15 2011-09-15 Robert Bosch Gmbh Antrieb mit Notschließfunktion

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10152414A1 (de) * 2001-08-29 2003-05-08 Bosch Rexroth Ag Hydraulikzylinder
EP1413810A1 (fr) 2002-10-22 2004-04-28 MOOG GmbH Dispositif de commande
DE102009021668A1 (de) 2009-05-16 2010-11-18 Robert Bosch Gmbh Stellanordnung, Schaltantrieb für eine derartige Stellanordnung und Ventilanordnung für eine derartige Stellanordnung
DE102010011516A1 (de) 2010-03-15 2011-09-15 Robert Bosch Gmbh Antrieb mit Notschließfunktion

Also Published As

Publication number Publication date
DE102011012305B4 (de) 2024-01-25
DE102011012305A1 (de) 2012-08-09

Similar Documents

Publication Publication Date Title
DE102011104530A1 (de) Hydraulische Stellanordnung
EP2547935B1 (fr) Système d'entraînement avec une fonction de fermeture d'urgence
EP2840264B1 (fr) Système d'actionnement à sécurité intégrée
DE102017206394A1 (de) Druckhalteventilanordnung für einen Spülkreislauf eines geschlossenen hydraulischen Kreislaufs
WO2017125108A1 (fr) Système de changement de vitesse hydraulique conçu pour un véhicule automobile
DE102016210874A1 (de) Vorrichtung zum Betätigen einer Parksperre eines Automatikgetriebes, sowie Parksperreneinrichtung für ein solches Automatikgetriebe
EP2503161A2 (fr) Dispositif de vanne de commande hydraulique
DE102009021668B4 (de) Stellanordnung, Schaltantrieb für eine derartige Stellanordnung und Ventilanordnung für eine derartige Stellanordnung
EP2597317B1 (fr) groupe moteur-pompe pour une machine-outil
DE102012214408B4 (de) Verstelleinrichtung für eine hydrostatische Maschine und hydrostatische Maschine
EP2647883B1 (fr) Dispositif de commande hydraulique
DE102012012977A1 (de) Hydraulischer Antrieb
DE102015108521A1 (de) Zylindereinheit
DE2063318B2 (de) Hydraulischer Unterbrecher
DE102011012305B4 (de) Hydraulische Stellanordnung
DE102013216790A1 (de) Schaltarmaturanordnung
WO2017167435A1 (fr) Dispositif de commande
DE102010055716A1 (de) Hydraulischer Antrieb
EP3244072B1 (fr) Système de soupapes hydrostatiques et dispositif de levage hydrostatique doté du système de soupapes
EP1757817B1 (fr) Arrangement de valve pour contrôler une soupape à fermeture rapide de turbine à gaz ou à vapeur
EP4038285A1 (fr) Commande hydrostatique à commutation rapide
WO2015185619A2 (fr) Vanne multivoies, en particulier vanne à 6/2 voies, et agencement de vannes multivoies
DE102022208319B3 (de) Ventilschalteinheit mit einem 2-Wege-Einbau-Logikventil mit zuschaltbarer Rückschlagventilfunktion und Servohydraulische-Achse mit Ventilschalteinheit
DE202008012466U1 (de) Steuerblock für einen doppeltwirkenden Hydraulikdrehantrieb zur Steuerung einer Dampfturbine
DE102019122985B4 (de) Steuerventil mit Sicherheitsfunktion

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12702760

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 12702760

Country of ref document: EP

Kind code of ref document: A1