EP1757817A2 - Arrangement de valve pour contrôler une soupape à fermeture rapide de turbine à gaz ou à vapeur - Google Patents

Arrangement de valve pour contrôler une soupape à fermeture rapide de turbine à gaz ou à vapeur Download PDF

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Publication number
EP1757817A2
EP1757817A2 EP06015961A EP06015961A EP1757817A2 EP 1757817 A2 EP1757817 A2 EP 1757817A2 EP 06015961 A EP06015961 A EP 06015961A EP 06015961 A EP06015961 A EP 06015961A EP 1757817 A2 EP1757817 A2 EP 1757817A2
Authority
EP
European Patent Office
Prior art keywords
valve
switching
valves
control
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
EP06015961A
Other languages
German (de)
English (en)
Other versions
EP1757817A3 (fr
EP1757817B1 (fr
EP1757817B8 (fr
Inventor
Tobias Dipl.-Ing. Hermann
Wolfgang Dipl.-Ing. Warmuth
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.)
ABB Technology AG
Original Assignee
ABB Technology AG
ABB 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 ABB Technology AG, ABB Patent GmbH filed Critical ABB Technology AG
Priority to PL06015961T priority Critical patent/PL1757817T3/pl
Publication of EP1757817A2 publication Critical patent/EP1757817A2/fr
Publication of EP1757817A3 publication Critical patent/EP1757817A3/fr
Publication of EP1757817B1 publication Critical patent/EP1757817B1/fr
Application granted granted Critical
Publication of EP1757817B8 publication Critical patent/EP1757817B8/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • 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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • 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
    • F15B20/008—Valve 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
    • F15B2211/30—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
    • F15B2211/30575—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 in a Wheatstone Bridge arrangement (also half bridges)
    • 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
    • F15B2211/80—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
    • 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
    • F15B2211/863—Control during or prevention of abnormal conditions the abnormal condition being a hydraulic or pneumatic failure
    • F15B2211/8636—Circuit failure, e.g. valve or hose 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
    • F15B2211/8757—Control measures for coping with failures using redundant components or assemblies

Definitions

  • the invention relates to a valve arrangement for controlling a component with three input switching valves, through which a pressurized medium can be conducted, which are connected to the inflow side with supply lines to a pressure supply and which are arranged fluidically parallel to each other, and with a connecting element for the device, which Connecting element is connected by pressure lines with drain sides of all input switching valves.
  • Valve arrangements of this type are well known.
  • such valve arrangements are referred to as trip blocks with a 2 of 3 interconnection, and are known, for example, for the quick release of a quick-closing valve, in particular of gas or steam turbines.
  • the designation 2 of 3 states that of three available signal channels, at least 2 must be actuated in order to trigger the fast-closing signal.
  • arrangements have prevailed on a hydraulic basis, that is, the control medium for triggering the high-speed signal is usually a hydraulic oil.
  • valve arrangement for driving a component with the features specified in claim 1 and with the features specified in claim 11.
  • valve arrangement according to the invention for controlling a component of the type mentioned in that a connected to the medium control line is connected to the pressure supply that three control valve groups are controlled with the control line that each switching valve group are assigned two switching valves and one of the input switching valves, that between a switching valve group and the control line in each case a control valve is interposed, with which control valve the switching operations of the switching valves and the input valve of the corresponding switching valve group allows that between a drainage point for the medium and the connecting element three flow-parallel discharge lines are arranged for the medium, that in each of the drain lines two switching valves are arranged in series, and that the switching valves of each drain line of different Ansteu erventilen are actuated.
  • control valve is designed as a solenoid valve.
  • each solenoid valve is a channel of a drive signal, which is separately controllable.
  • the generally known fail-safe principle can be carried out with the valve assembly according to the invention by, for example, the switching valves, the input valves and / or the control valves have a return element, in particular a return spring, which the valve in the idle state in a predetermined valve position , holds or brings, namely the fail-safe-proper position.
  • the "closed position” is the position in the idle state.
  • the "open position” is the position in the idle state and for the solenoid valves, the electric actuator operates against the return element, so that in the current-free state, the return element of the valve this also in the position of inoperative condition transferred.
  • valves namely the input valves, the switching valve and the control valves are arranged in a common housing.
  • pressure signals are provided in particular at different points of the valve arrangement according to the invention.
  • throttle bodies such as orifices, Verstellblenden or valves and the like are provided, so that the valve arrangement according to the invention is adjustable in a particularly simple manner.
  • FIG. 1 shows a triggering device 10 in a schematic representation, wherein three signal channels are available in the present example, wherein two of these channels must trigger to actuate the triggering device 10.
  • the valves, sensors and piping shown are essentially realized in a single device, so that the triggering device 10 is designed to be particularly compact and thus space-saving.
  • the triggering device 10 is prepared with a first flange 12 to be connected to a pressure supply, not shown in this figure.
  • the embodiment of the invention shown in the figure is realized by a hydraulic system, so that the pressure supply is ensured for example by a pump for hydraulic oil.
  • the hydraulic oil will supply the triggering device 10 with hydraulic oil through the connection point on the first flange 12 into a first pipeline 14.
  • a first 16, a second 18, and a third input switching valve 20 are fluidly connected in parallel to the first pipe 14.
  • the input switching valves 16, 18, 20 essentially have two switching positions, wherein a first switching position is shown in this figure and should be referred to as "open", so that the hydraulic oil flows through the input switching valves 16, 18, 20.
  • a second switching position may be adjusted by the input switching valves 16, 18, 20 by actuating a hydraulic cylinder 22 provided on each input switching valve 16, 18, 20 and correspondingly changing the valve position.
  • the hydraulic cylinder 22 operates against a spring, not shown in this figure, the failure of the hydraulic system, in particular in a pressure drop at the hydraulic cylinder 22, the input switching valves 16, 18, 20 in the predetermined first position "open" spends.
  • the hydraulic oil now flows from the first flange 12 through the first pipe 14 to and through the first input switching valve 16, which is connected on the output side to a first side of a second pipe 24, while a second side of the second pipe 24, the hydraulic oil into a manifold 26 leads.
  • a first check valve 30 with tubing fittings is disposed between the first manifold and the manifold 26. Branches or junctions of lines are highlighted in the figure with black dots.
  • the first spring-loaded check valve 30 ensures that only from a set minimum pressure hydraulic oil into the manifold 26 passes at corresponding pressure conditions in the pipes a return flow of oil against the planned pressure gradient back into the second pipe 24 is prevented. In this way, a pressure relief of the system is realized.
  • a first adjustable orifice 32 is arranged as a throttle member. With the first orifice 32, a predeterminable pressure in the second pipe 24 is adjusted, and thus also the flow rate. Downstream of the first orifice 32, a first pressure sensor 34 is arranged, which measures the pressure downstream of the first orifice 32.
  • the manifold 26 also has a second pressure sensor 36 which measures the resulting pressure of all three supply systems from the pressure supply via the input switching valve 16, 18, 20.
  • the manifold 26 still has a connection point 38 with a connecting element, not shown, on which quite generally a component can be shot.
  • the component is a quick-acting valve, for example for a gas turbine or a steam turbine, which ultimately receives a control signal via which the connecting element.
  • the quick-closing valve As long as a certain pressure prevails in the manifold 26 and thus at the junction, the quick-closing valve remains open. In the other case, if there is a pressure drop in the manifold 26 below the certain, predetermined, value, the quick-closing valve will close, in particular by a certain biasing force, moved to its "closed" position.
  • the quick-closing valve can accordingly be used as a safety valve.
  • the first pipe 14 also branches at a second pipe branch 40 on the one hand to a pressure relief valve 42 and on the other hand in a control line 44.
  • the control line 44 passes the hydraulic oil, which is now used as control oil, to a first 46, a second 48 and a third control valve 50.
  • These control valves 46, 48, 50 are designed so that they are electromagnetically are controlled, which is symbolized by a corresponding symbol 52 in the figure.
  • the drive operates in each case against a spring 54, which ensures in the case of failure of the drive that the control valves 46, 48, 50 are spent in a design-related situation and held there.
  • first control valve 46 This is designed so that it simultaneously switches two hydraulic lines with a switching movement.
  • first control valve 46 This is designed so that it simultaneously switches two hydraulic lines with a switching movement.
  • first supply line 56 which ensures that the pressure, by means of hydraulic oil, to a first control cylinder 58 of a first switching valve 60 and a second control cylinder 62 of a second switching valve 64 is supplied.
  • each of the switching valves 60,64 operates against a spring, so that the switching position of the switching valves 60, 64 is only achieved as long as a pressure in front of the control cylinders 58, 62 is present. Should a pressure drop in this system be caused for any reason, the relevant switching valve 60,64 is automatically transferred by the error in its second switching position, which releases the hydraulic path through the valve.
  • a second pressure relief valve between the first switching valve 60 and the first control valve 46 is interposed in the first supply line 56. In particular, it fulfills a safety function.
  • the hydraulic cylinder 22 of the first input switching valve 16 is connected via the second supply line 57 and the first control valve 46 with a drainage pipe 68, which ultimately leads to a substantially unpressurized outflow point 70, which returns the incoming there hydraulic oil in an oil system.
  • This is usually in turn connected to the pressure supply, so that overall results in a non-illustrated closed circuit for the hydraulic oil.
  • the second supply line 57 is also ensured that in the illustrated first switching position of the first control valve 46 whose hydraulic cylinder 22 is not driven and accordingly, the return spring, not shown, the first input switching valve 16 has spent in the switching position shown.
  • the manifold 26 is connected by a first 72, a second 74 and a third drainage line 76 to the drainage pipe 68.
  • the second switching valve 64 and a further switching valve which is switched by the second control valve 48, installed in the pipeline in series.
  • the flow of hydraulic oil from the manifold 26 can flow at a relatively high pressure level in the drainage pipe 68 with a comparatively low pressure level. Only when both switching valves are depressurized on their control cylinder and thus open, the drainage of the hydraulic oil through the first drainage pipe 72 is ensured.
  • two switching valves are also arranged in the second drainage line 74, of which a first via the second control valve 48 and a second via the third control valve 50 is driven.
  • the corresponding two switching valves in the third drainage line 76 are actuated by the third control valve 50 or by the first control valve 46.
  • each different drainage line 72, 74, 76 are installed in each different drainage line 72, 74, 76, so that a pressure drop, for example in the first supply line 56 only causes the first switching valve 60 in the third drainage line 76 is switched to passage, and the second switching valve 64 in the first drainage line 72 is switched to passage.
  • both drainage line 72, 76 there are but still another switching valve that ensures that the drainage line 72, 76 remain closed and no pressure drop in the manifold 26 is effected. In this way, a mechanical interconnection of the two of three principle is ensured according to the invention.
  • the first pipe 14 is also still connected by means of a first 78, a second 80 and a third bypass line 82 to the drainage pipe 68.
  • throttle bodies 84 for example throttle orifices, are installed in the bypass lines 78, 80, 82 at points marked "D".
  • the pressure conditions upstream of these throttle bodies can thereby be adjusted in a particularly simple manner.
  • the first bypass line 78 is connected to the first drainage line 72 and in the pipe section between the two switching valves, wherein the two throttle bodies "D", which are installed in the first bypass line 78, upstream and downstream of the connection point are arranged.
  • a third pressure sensor 86 is also arranged, which measures according to the pressure between the two throttle points and also on the principle of the connected tubes and the pressure between the two switching valves of the first drainage line 72. It can be determined via the pressure level which is established there, whether one of the two switching valves is open and from this the inference to appropriate errors or damages in the system or the switching valves or also the control valves to draw.
  • the necessary evaluation devices for the measurements and possibly further measuring and control technology are not shown in the figure.
  • the second bypass line 80 is connected to the second drainage line 74 and the third bypass line 82 to the third drainage line 76.
  • the corresponding reference numerals are not included for reasons of simplicity.
  • FIG 2 shows the triggering device 10 in which by appropriate control of the control valves 46, 48, 50, the system has been depressurized at the junction to reach, so that a quick-acting valve connected thereto exerts its quick-closing function. Since this figure is the same triggering device 10 as in Figure 1, the previously used reference numerals the same components are also used in this figure. However, only those components are provided with reference numerals, which are necessary to explain this figure or the deviations from Figure 1.
  • control valves 46, 48, 50 are deliberately de-energized, so that the corresponding return springs on these valves spend them in a predefined end position, the second position, and hold there.
  • the internal interconnection of the control valves 46, 48, 50 is designed such that the pressure prevailing in the control line 44 passes via the first control valve 46 to the second supply line 57 and thus supplies the hydraulic cylinder 22 with pressure, and thus the first input switching valve 16 in a Position is spent, in which the flow of hydraulic oil through the first pipe 14 to the second pipe 24 is interrupted. Since all input switching valves 16, 18, 20 close the first pipe 14, the pressure supply of the manifold 26 is prevented altogether.
  • first supply line 56 is now connected to the drainage pipe 68 by the described valve position of the first control valve 46.
  • the valves allow passage of hydraulic oil from the manifold 26 to the drainage pipe 68. Since there are two switching valves in each drainage line 72, 74, 76, both switching valves are switched to passage to allow the hydraulic oil from the manifold 26 to enter the drainage pipe 68 can. This is inventively achieved in that all three control valves 46, 48, 50 are connected without power, so that all existing switching valves are spent in their second position and are also held there.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Fluid-Driven Valves (AREA)
EP06015961A 2005-08-23 2006-08-01 Arrangement de valve pour contrôler une soupape à fermeture rapide de turbine à gaz ou à vapeur Active EP1757817B8 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL06015961T PL1757817T3 (pl) 2005-08-23 2006-08-01 Układ zaworowy do regulowania zaworu szybkozamykającego turbin gazowych lub parowych

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005040039A DE102005040039B4 (de) 2005-08-23 2005-08-23 Ventilanordnung zur Ansteuerung eines Bauelements

Publications (4)

Publication Number Publication Date
EP1757817A2 true EP1757817A2 (fr) 2007-02-28
EP1757817A3 EP1757817A3 (fr) 2009-09-09
EP1757817B1 EP1757817B1 (fr) 2012-06-20
EP1757817B8 EP1757817B8 (fr) 2012-11-28

Family

ID=37496098

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06015961A Active EP1757817B8 (fr) 2005-08-23 2006-08-01 Arrangement de valve pour contrôler une soupape à fermeture rapide de turbine à gaz ou à vapeur

Country Status (7)

Country Link
US (1) US7444920B2 (fr)
EP (1) EP1757817B8 (fr)
CN (1) CN1924368B (fr)
DE (1) DE102005040039B4 (fr)
DK (1) DK1757817T3 (fr)
ES (1) ES2389096T3 (fr)
PL (1) PL1757817T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012104046A1 (fr) * 2011-02-04 2012-08-09 Robert Bosch Gmbh Dispositif de réglage hydraulique

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011082599B4 (de) 2011-09-13 2013-08-14 Keicher Hydraulik GmbH Ventilanordnung, Verwendung, Turbine und Kraftwerk
PH12013000162A1 (en) * 2012-06-08 2015-03-16 Emerson process man power and water solutions inc Electronically controllable and testable turbine trip system with redundant bleed manifolds
US9896962B2 (en) 2014-02-28 2018-02-20 General Electric Company Trip manifold assembly for turbine systems
DE102014007475B4 (de) 2014-05-21 2017-06-08 Stephan Amelunxen Ventilanordnung zur gesteuerten Druckentlastung fluidgefüllter Leitungen unter erhöhten Sicherheitsanforderungen

Family Cites Families (7)

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Publication number Priority date Publication date Assignee Title
FR2266022B1 (fr) * 1974-03-26 1976-12-17 Gratzmuller Jean Louis
US4640095A (en) * 1985-01-28 1987-02-03 Caterpillar Inc. Digital electro-hydraulic valve arrangement
DE59103692D1 (de) * 1991-01-25 1995-01-12 Asea Brown Boveri Zuschaltventil und hydraulisches Sicherheits- und Kraftölsystem, in welchem das Zuschaltventil verwendet wird.
EP0540963B1 (fr) * 1991-11-04 1995-08-30 Asea Brown Boveri Ag Système d'alimentation pour système hydraulique divisé
DE4330038A1 (de) * 1993-09-06 1995-03-09 Abb Management Ag Hydraulische Sicherheitsschaltung
DE4336074C2 (de) * 1993-10-22 1998-07-02 Abb Patent Gmbh Hydraulikeinrichtung für einen Hydraulikantrieb für einen Hochspannungsleistungsschalter
CN1274810A (zh) * 1999-05-21 2000-11-29 株式会社岛津制作所 多阀门装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012104046A1 (fr) * 2011-02-04 2012-08-09 Robert Bosch Gmbh Dispositif de réglage hydraulique
US9328842B2 (en) 2011-02-04 2016-05-03 Robert Bosch Gmbh Hydraulic actuating assembly

Also Published As

Publication number Publication date
ES2389096T3 (es) 2012-10-23
DK1757817T3 (da) 2012-10-01
CN1924368A (zh) 2007-03-07
CN1924368B (zh) 2011-01-19
DE102005040039A1 (de) 2007-03-01
EP1757817A3 (fr) 2009-09-09
EP1757817B1 (fr) 2012-06-20
US20070044651A1 (en) 2007-03-01
US7444920B2 (en) 2008-11-04
DE102005040039B4 (de) 2013-01-31
PL1757817T3 (pl) 2013-01-31
EP1757817B8 (fr) 2012-11-28

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