EP2531730B1 - Fluid-actuated valve-actuating drive - Google Patents
Fluid-actuated valve-actuating drive Download PDFInfo
- Publication number
- EP2531730B1 EP2531730B1 EP11703397.7A EP11703397A EP2531730B1 EP 2531730 B1 EP2531730 B1 EP 2531730B1 EP 11703397 A EP11703397 A EP 11703397A EP 2531730 B1 EP2531730 B1 EP 2531730B1
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- EP
- European Patent Office
- Prior art keywords
- actuating drive
- fluid
- actuator
- fluidic
- valve
- 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.)
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Images
Classifications
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- 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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
- F15B15/06—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement
- F15B15/065—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement the motor being of the rack-and-pinion type
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- 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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/18—Combined units comprising both motor and pump
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- 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
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- 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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/202—Externally-operated valves mounted in or on the actuator
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- 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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/28—Means for indicating the position, e.g. end of stroke
- F15B15/2807—Position switches, i.e. means for sensing of discrete positions only, e.g. limit switches
Definitions
- the present invention relates to a fluid-operated actuator to a valve, in particular a shut-off, safety or control valve.
- valve actuators are known and in use.
- this particular fluid-operated valve actuators see, eg EP 0665373 B1 . EP 1418343 B1 . EP 1593893 B1 and EP 2101061 A1 ).
- Such fluid-operated valve actuators may include, in addition to a hydraulically or pneumatically actuated linear actuator, the slide may be coupled directly or optionally via a mechanical transducer to the input of the valve, a base valve having the control valves and / or other fluidic control.
- the DE 9406760 U1 discloses a drive unit for valves, especially in shipbuilding.
- a housing which encloses an electric motor, a driven by this pump, spreader elements and a hydraulic reservoir.
- the housing is connected to a pivot drive, which comprises a piston with rack and a shaft.
- the US 4647003 A discloses an actuator for the valve of a shut-off valve.
- the actuating device comprises a housing with a rotatably mounted therein, coupled to the rotary shaft of the valve shaft with an associated pinion, with which meshes the rack of at least one designed as a pneumatic cylinder linear actuator.
- one or two pneumatic cylinders can be activated be attached to the housing.
- the present invention has set itself the task of providing a fluid-operated valve actuator, which is characterized by a particular practicality, especially for a broad user base particularly relevant properties such as high reliability and durability, low maintenance and ease of use, high power density and low Manufacturing and operating costs combined.
- the fluid-operated valve actuator is characterized in particular by the fact that it comprises two opposing linear actuators and arranged between them, the slide coupling with each other mechanical converter whose output is coupled to the input of the valve comprises.
- the valve actuator is constructed as a fluidic drive system in a modular manner from individual, assembled into a functional unit components in the form of the base unit, the two linear actuators and the mechanical transducer.
- a particularly compact and efficient fluidic drive system is provided on a fitting, which can be designed as a closed system having only one electrical input and a mechanical output acting on the inlet of the fitting, and in this way to such an extent Maintenance and user-friendly, as was previously known only from electric valve actuators ago.
- the joining of the said components to the compact, closed fluidic drive system can thereby be realized in particular in that the two linear actuators are flanged to the mechanical transducer, which in turn via a flange connection to the base unit (or possibly one in turn connected to the base unit Notbetuschistsblock) connected is.
- the two linear actuators are flanged to the mechanical transducer, which in turn via a flange connection to the base unit (or possibly one in turn connected to the base unit Notbetuschistsblock) connected is.
- the said fluid connections can be equipped with self-closing barriers, especially in the area of the dividing planes through which they pass, between the said components, which prevent the escape of fluid or the unintentional penetration of contaminants along the dividing planes, in particular if individual components have been dismantled for the purpose of maintenance ,
- filter elements eg in the form of filter pots
- the valve actuator according to the invention structurally further developing technical aspects prove to be particularly advantageous in hydraulic valve actuators according to the present invention.
- Valve actuators have the particular effect that on the part of the user of the fluid-operated valve actuator with regard to maintenance and entertainment as electrical Valve actuators is considered to be completely equivalent, while preserving the specific advantages of fluid-operated valve actuators against electrical, namely the high power density and compactness, and reliability and ease of implementation of highly dynamic safety functions also required for explosion protection, the latter in particular the possibility To save fluid energy is to owe.
- the pressurized fluid supply is decentralized, ie in each case only associated with a single valve actuator, organized by the base unit of the fluid-operated valve actuator according to the invention comprising a pressurized fluid supply unit.
- a pressure fluid supply unit particularly preferably comprises a tank-powered hydraulic unit with a pump driven by an electric motor.
- the said pressurized fluid supply unit preferably comprises an ambient medium driven by an electric motor, preferably via a filter system, and sucking in a pneumatic pump.
- the fluid-operated valve actuator according to the invention has a filling connection which is suitable for first filling the fluid system with hydraulic fluid from a cartridge, in particular arranged on the base unit.
- This allows the user-side commissioning of a hydraulically operated valve actuator according to the present invention, without the user being in any way in contact with hydraulic fluid.
- This contributes to the superior (so) hydraulically operated valve actuators, which are superior in their operating behavior to electrical valve actuators, in applications in which user-friendliness is particularly important for cleanliness and a minimal risk of coming into contact with hydraulic fluid , is placed.
- module or modular construction plays a significant role, which allows the provision of individualized, specifically adapted to the particular requirement valve actuators at extremely competitive costs, not only the converter and the two linear actuators in terms of their dimensions individually can be varied, but rather the possibility explained further below, functionally different linear actuators and mechanical transducers combine with each other.
- the said mechanical converter can convert the linear movement of the slides of the two linear actuators into a rotational movement, namely if the valve has a rotatable locking member whose position can be changed by means of the valve actuator.
- a mechanical transducer with a linear output can be combined to form a functional unit with the same linear actuators.
- pneumatic or hydraulic linear actuators are installed, in turn, different embodiments can be used within the two groups such as pneumatic pneumatic actuators classical actuators, spring actuators with control air filling, spring actuators with pneumatic bias or fluid storage ,
- the fluidic control typically provided for valve actuators of the type in question here may cooperate with an electro-fluidic signal converter, which in particular may be arranged upstream of the base unit and may have a proportional output behavior.
- An external electrical control unit which may include input means, a setpoint input, a control electronics, a communication unit, a signal output and / or a signal generator, may furthermore be connected to a signal input connected to the electro-fluidic signal converter. In the sense of a closed control loop, the actual value signal of a sensor assigned to the fitting can be fed back to the electrical control unit.
- At least one of the two linear actuators in particular both linear actuators, is / is designed as a fluid-actuated actuator on both sides, wherein both working spaces are constantly connected to a pressurized fluid supply are connected.
- This is of particular advantage in pneumatic systems. Are in this sense both working spaces of the at least one double-sided fluid-actuated linear actuator connected directly to the pressurized fluid supply and acted upon by this and for positioning purposes, ie to change the position of the slide of the respective linear actuator, one of the two working spaces vented specifically, the slide of respective linear actuator in each operating position clamped with maximum rigidity, which allows a particularly good controllability.
- fluid energy can be stored in a (especially external) accumulator to bring in case of failure of the pressurized fluid supply, the valve at least in a predetermined safety position.
- a mechanical storage spring is integrated into a mechanical storage spring.
- such a mechanical accumulator spring is biased by fluid pressure and locked in the biased position, so that they are not constantly applied to the slide of the respective linear actuator in the sense that would have to be permanently worked against the force of the mechanical storage spring.
- the mechanical storage spring acts on the slide of the associated linear actuator only after actuation of an unlocking, by means of which a blockage blocking the storage spring is released.
- a blockage blocking the storage spring is released only in an emergency by removing the blockage mechanical accumulator combines the advantages of high reliability of the valve actuator with other aspects such as economy, compactness and dynamic response.
- the drawing illustrated, for actuating a valve, in particular a shut-off, safety or control valve serving fluidbetuschw, namely hydraulic actuator 1 comprises as main components a base unit 2 with an integrated pressure fluid supply unit 3, an emergency operating block 4, a flanged to this mechanical transducer 5 and a first linear actuator 6 and a second linear actuator 7.
- the pressurized fluid supply unit 3 is a pump block 8, an electric motor 9 and a Tank 10 comprehensive hydraulic unit 11 executed.
- the base unit 2 comprises, within the base block 12 connected directly to the pump block 8, the required control valves of the hydraulic control;
- the actuating solenoids 13, which project from the base block 12 of the base unit 2 are shown corresponding solenoid valves.
- the valve actuator For the explosion-proof design of the valve actuator is a base unit 2 together with the integrated pressure fluid supply unit 3 and the electrical and electronic components 14 enclosing flameproof enclosure provided from the in the drawing (only) the capsule base 15 shown, the associated capsule Hood is not shown, however.
- the capsule base 15 is clamped between the base unit 2 and the emergency operating block 4. It has the explosion-proof bushings designed in a known form for the electrical supply, signal and control lines. Furthermore, in the base block 12 with the emergency operating block 4 connecting hydraulic lines flame arresters are arranged.
- a connection 16 for an external hydraulic accumulator 17 (see. Fig. 4 and 5 ), which is designed and designed for an emergency operation of the valve actuator in the event of failure of the regular control.
- the other an emergency operation of the valve actuator serving components such as emergency valves are housed.
- To operate the emergency valves serve two devices, namely on the one hand a switch 18 and on the other hand a lever 19.
- the switch 18 By means of the switch 18, an electrical actuation of the emergency valves is possible, for example in the event of failure of the regular control. Is the power supply interrupted and thus an actuation of the emergency valves by means of the switch 18 is not possible remains in any case, the purely mechanical actuation of the emergency valves by means of the lever 19th
- the mechanical converter 5 comprises a designed as a converter block 20 housing, which is flanged directly to the valve to be operated, for which purpose the converter block 20 has threaded holes 21 for fastening screws on its underside. At the bottom of the transducer block is still acting on the shaft of the valve mechanical output 23 of the valve actuator. This includes in this embodiment a square socket 22. Alternative versions of the output to reliably transmit the necessary torque to the input of the valve, are known and in use in practice, such as a shaft connection by means of feather key.
- the linear movement of the slide 81 of the two oppositely arranged on the mechanical transducer 5 flanged linear actuators 6 and 7 is converted into a rotational movement of the output 23.
- a linear, parallel to the slides 81 forming piston 24 and 25 of the linear actuators 6 and 7 slidable rack 26 meshes with a pinion 27 which is rotatably connected to the mechanical output 23.
- the rack 26 is part of a slide 72, which further comprises two connected at one end fixed to the rack cylindrical Druckund guide pieces 73 which are guided in each case an associated guide bush 74 and on which the front side abutting them piston 24 and 25 of the linear actuators 6 and 7 act.
- a control box 30 covered by a sighting glass 28 having a sighting glass 29 is mounted on its upper side.
- an optical position indicator 31 connected in a rotationally fixed manner to the output 23 is arranged with a position indicator 32 protruding into the sighting dome 28 and thus readable from all sides.
- an angle encoder 33 whose signal is returned to the electronic control, as well as two also connected to the controller sensors 34 for Endlagenabfrage, the two end positions can be defined by pins 35 which in a grid 36 in a rotatably connected to the output 23 disc 37 can be inserted.
- the linear actuator 6 comprises a cylinder 38 in which the piston 24 is sealingly guided;
- the linear actuator 7 comprises a cylinder 39, in which the piston 25 is sealingly guided.
- Both cylinders 38 and 39 are each end closed by a cover 40 which defines together with the respective associated cylinder and the guided in this piston 24 and 25, a hydraulic working space 41, in which an associated hydraulic line 42 opens.
- Each of the two linear actuators is equipped with hydraulic cushioning.
- located within the respective working space 41 near the associated cover 40 each have a disc 43 with a central bore 44 and overflow 45.
- a pin 46 is disposed frontally, which, when the piston of the Disk 43 approaches, with a slight clearance (annular gap) dips into the bore 44, thereby further displacement of hydraulic fluid from the working space 41 via the connecting space 47 throttles into the hydraulic line 42 into and dampens in this way the further movement of the piston.
- the discs 43 are complementary stops for the piston, for which purpose their exact position within the associated working space 41 by means of the adjusting screw 48 is adjustable.
- the valve actuator 1 is constructed in a modular manner from the above-described individual, assembled into a functional unit components in the form of the base unit 2 including integrated pressure fluid supply unit 3, the Notbetuschistsblocks 4, the mechanical converter 5 and the two linear actuators 6 and 7.
- said individual components are connected to one another by way of mutually paired flange surfaces.
- a valve actuator in the form of a compact, closed, an electrical input and acting on the input of the valve mechanical output having fluidic drive system.
- the individual components with each other hydraulically connecting fluid connections are equipped with self-closing shutters 49 in the area of their interspersed parting planes between the individual components. These only open when the two components concerned are fully assembled and, conversely, close automatically if the relevant components are disconnected when the valve actuator is disassembled.
- the mechanical transducer shown at the connection surfaces for the linear actuators 6 and 7 each have three provided with shut-offs 49 for hydraulic fluid on, namely one for working pressure, tank and memory, the memory port functionally only comes into play, if the individual Configuration of the valve actuator, a linear actuator with a structurally associated hydraulic accumulator comprehensive assembly (see below) is used.
- the mechanical converter 5 shown has four hydraulic fluid transfers equipped with barriers 49, namely two for the working pressure of the two linear actuators and one each for tank and accumulator.
- the barriers are structurally associated respectively filter elements 82 in the form of recorded in a pot 83 filters.
- the valve actuator is prepared for a first filling of the fluid system with hydraulic fluid from (at least) one cartridge.
- a filling connection 50 is provided on the emergency operating block 4.
- Part of this filling connection is (cf. Fig. 9 ) designed as a hollow needle piercing mandrel 51, which opens the closure seal 52 of a screwed into the filling port 50 cartridge 53.
- the cartridge 53 or the last cartridge required for complete filling of the fluid system remains at the filling port 50; it closes this and at the same time provides a compensation volume.
- a hydraulic accumulator integrated into one of the two linear actuators 6 and 7 may be provided.
- a hydraulic accumulator module 54 is flanged to the end face of the linear actuator 6. This comprises a cylinder portion 55, a cover 56 which closes this end face and a mounting and coupling plate 57 closing the cylinder portion 55 at the other end.
- a guide pin 58 is mounted on the cover 56, on which a stack of disk springs 59 is guided, which on the one hand abuts on the one hand Bearing 60 of the guide pin 58 is supported and on the other hand acts on the displaceably guided in the cylinder portion 55 piston 61.
- Piston 61, cylinder section 55 and mounting and coupling plate 57 thereby limit a storage space 62, which is connected via a running in the mounting and coupling plate 57 hydraulic line 63 with the memory-side transfer 64 in combination. This is, as well as the corresponding actuator-side transfer 65, again equipped with a self-closing barrier 49.
- the hydraulic fluid clamped in the storage space 62 is switched to one of the two linear actuators 6 or 7 during emergency actuation of the valve actuator via a corresponding actuation of the valves of the emergency actuation block 4, depending on whether the valve is to be opened or closed for the safety position close is. The same is true for the rest of the use of the external hydraulic accumulator 17 described above.
- the linear actuators can be made relatively small, which allows a particularly compact design of the valve actuator.
- valve actuator By any and demand-oriented equipment of the valve actuator with a hydraulic storage module 54 on one of the two linear actuators, with two hydraulic storage modules 54 on both linear actuators and / or an external hydraulic accumulator, the valve actuator can be seen flexibly to the respective requirements as well as to the respective spatial Adjust conditions.
- one of the linear actuators can be designed as a pure spring actuator 70, which, like Fig. 11 illustrated, an integrated mechanical storage spring 71 includes and otherwise constructed substantially like the hydraulic storage module explained above.
- the two linear actuators on the mechanical transducer 5 can be functionally combined arbitrarily and the converter at each of its two connection points a fluidic actuator, a mechanically coupled Federaktuator, a mechanically decoupled spring actuator with fluidic actuation or a mechanically decoupled spring actuator with fluidic actuation and a separate independent receive mechanically coupled fluidic actuator, wherein the fluidic control is taken in all cases by the base unit.
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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)
- Fluid-Driven Valves (AREA)
- Actuator (AREA)
- Magnetically Actuated Valves (AREA)
- Mechanically-Actuated Valves (AREA)
- Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
Description
Die vorliegende Erfindung betrifft einen fluidbetätigten Stellantrieb an einer Armatur, insbesondere einer Absperr-, Sicherheits- oder Regelarmatur.The present invention relates to a fluid-operated actuator to a valve, in particular a shut-off, safety or control valve.
In der Praxis sind verschiedene Armaturen-Stellantriebe bekannt und im Einsatz. Neben verbreitet eingesetzten elektrischen Armaturen-Stellantrieben sind dies insbesondere auch fluidbetätigte Armaturen-Stellantriebe (vgl. z.B.
Die
Die
Die vorliegende Erfindung hat sich zur Aufgabe gemacht, einen fluidbetätigten Armaturen-Stellantrieb bereitzustellen, der sich durch eine besondere Praxistauglichkeit auszeichnet, indem er namentlich für eine breite Anwenderschaft besonders relevante Eigenschaften wie hohe Zuverlässigkeit und Lebensdauer, geringen Wartungsaufwand und hohe Anwenderfreundlichkeit, hohe Leistungsdichte und geringe Herstellungs- und Betriebskosten in sich vereinigt.The present invention has set itself the task of providing a fluid-operated valve actuator, which is characterized by a particular practicality, especially for a broad user base particularly relevant properties such as high reliability and durability, low maintenance and ease of use, high power density and low Manufacturing and operating costs combined.
Gelöst wird diese Aufgabenstellung durch den in Anspruch 1 angegebenen fluidbetätigten Stellantrieb an einer Armatur. In diesem Sinne zeichnet sich der erfindungsgemäße fluidbetätigte Armaturen-Stellantrieb insbesondere dadurch aus, dass er zwei einander gegenüberstehende Linearaktuatoren und einen zwischen diesen angeordneten, deren Schieber miteinander koppelnden mechanischen Wandler, dessen Ausgang mit dem Eingang der Armatur gekoppelt ist, umfasst. Dabei ist der Armaturen-Stellantrieb als fluidisches Antriebssystem baukastenartig aus einzelnen, zu einer Funktionseinheit zusammengefügten Komponenten in Form der Basiseinheit, der beiden Linearaktuatoren und des mechanischen Wandlers aufgebaut. Insbesondere wird auf diese Weise ein besonders kompaktes und leistungsfähiges fluidisches Antriebssystem an einer Armatur bereitgestellt, das als geschlossenes, nur einen elektrischen Eingang und einen auf den Eingang der Armatur wirkenden mechanischen Abtrieb aufweisendes System ausgeführt sein kann und auf diese Weise in einem solchen Maße wartungs- und bedienerfreundlich ist, wie dies bisher nur von elektrischen Armaturenantrieben her bekannt war.This problem is solved by the fluid-actuated actuator specified in claim 1 on a valve. In this sense, the fluid-operated valve actuator according to the invention is characterized in particular by the fact that it comprises two opposing linear actuators and arranged between them, the slide coupling with each other mechanical converter whose output is coupled to the input of the valve comprises. In this case, the valve actuator is constructed as a fluidic drive system in a modular manner from individual, assembled into a functional unit components in the form of the base unit, the two linear actuators and the mechanical transducer. In particular, in this way a particularly compact and efficient fluidic drive system is provided on a fitting, which can be designed as a closed system having only one electrical input and a mechanical output acting on the inlet of the fitting, and in this way to such an extent Maintenance and user-friendly, as was previously known only from electric valve actuators ago.
Das Zusammenfügen der besagten Komponenten zu dem kompakten, geschlossenen fluidischen Antriebssystem kann dabei insbesondere dadurch realisiert sein, dass die beiden Linearaktuatoren an den mechanischen Wandler angeflanscht sind, der seinerseits über eine Flanschverbindung mit der Basiseinheit (oder ggf. einem seinerseits mit der Basiseinheit verbundnen Notbetätigungsblock) verbunden ist. Dies ermöglicht, dass - gemäß einem weiteren für die vorliegende Erfindung wesentlichen Aspekt - sämtliche Fluidverbindungen zwischen der Basiseinheit und den Aktuatoren sowie gegebenenfalls dem mechanischen Wandler innerhalb der betreffenden Komponenten verlaufen, so dass keinerlei freiliegende Fluidleitungen existieren. Die besagten Fluidverbindungen können dabei namentlich im Bereich der von ihnen durchsetzten Trennebenen zwischen den besagten Komponenten mit selbstschließenden Absperrungen ausgestattet sein, welche das Austreten von Fluid bzw. das unbeabsichtigte Eindringen von Verunreinigungen entlang der Trennebenen verhindern, insbesondere wenn einzelne Komponenten zum Zwecke der Wartung demontiert sind. Im Bereich der Absperrungen können dabei, insbesondere in diese integriert oder mit diesen jeweils zu einer Baueinheit verbunden, Filterelemente (z.B. in Form von Filtertöpfen) vorgesehen sein. Sämtlich vorstehend aufgezeigten, den erfindungsgemäßen Armaturen-Stellantrieb konstruktiv weiterbildenden technischen Gesichtspunkten erweisen sich als besonders vorteilhaft bei hydraulischen Armaturen-Stellantrieben gemäß der vorliegenden Erfindung. Sie wirken sich insbesondere dahingehend aus, dass auf Seiten des Anwenders der fluidbetätigte Armaturen-Stellantrieb hinsichtlich der Wartung und Unterhaltung als elektrischen Armaturen-Stellantrieben vollkommen gleichwertig angesehen wird, bei gleichzeitigem Erhalt der spezifischen Vorteile von fluidbetätigten gegenüber elektrischen Armaturen-Stellantrieben, nämlich der hohen Leistungsdichte und besonderen Kompaktheit sowie Zuverlässigkeit und einfachen Realisierung von bei bedarf hochdynamischen Sicherheitsfunktionen auch für den Explosionsschutz, wobei letzteres insbesondere der Möglichkeit, fluidische Energie zu speichern, zu verdanken ist.The joining of the said components to the compact, closed fluidic drive system can thereby be realized in particular in that the two linear actuators are flanged to the mechanical transducer, which in turn via a flange connection to the base unit (or possibly one in turn connected to the base unit Notbetätigungsblock) connected is. This makes it possible that, according to a further aspect essential to the present invention, all fluid connections between the base unit and the actuators and optionally the mechanical converter run within the respective components, so that no exposed fluid lines exist. The said fluid connections can be equipped with self-closing barriers, especially in the area of the dividing planes through which they pass, between the said components, which prevent the escape of fluid or the unintentional penetration of contaminants along the dividing planes, in particular if individual components have been dismantled for the purpose of maintenance , In the area of the barriers, filter elements (eg in the form of filter pots) can be provided, in particular integrated in them or connected to these in each case to form a structural unit. All of the above-mentioned, the valve actuator according to the invention structurally further developing technical aspects prove to be particularly advantageous in hydraulic valve actuators according to the present invention. They have the particular effect that on the part of the user of the fluid-operated valve actuator with regard to maintenance and entertainment as electrical Valve actuators is considered to be completely equivalent, while preserving the specific advantages of fluid-operated valve actuators against electrical, namely the high power density and compactness, and reliability and ease of implementation of highly dynamic safety functions also required for explosion protection, the latter in particular the possibility To save fluid energy is to owe.
Im Rahmen der vorliegenden Erfindung ist die Druckfluid-Versorgung dezentral, d.h. jeweils nur einem einzelnen Armaturen-Stellantrieb zugeordnet, organisiert, indem die Basiseinheit des erfindungsgemäßen fluidbetätigten Armaturen-Stellantriebs eine Druckfluid-Versorgungseinheit umfasst. Im Falle eines hydraulisch betätigten Armaturen-Stellantriebs nach der vorliegenden Erfindung umfasst eine solche Druckfluid-Versorgungseinheit besonders bevorzugt ein aus einem Tank gespeistes Hydraulikaggregat mit einer von einem Elektromotor angetriebenen Pumpe. Bei einem pneumatisch betätigen Armaturen-Stellantrieb umfasst die besagte Druckfluid-Versorgungseinheit demgegenüber bevorzugt eine von einem Elektromotor angetriebene, Umgebungsmedium - bevorzugt über ein Filtersystem - ansaugende Pneumatikpumpe. Der erfindungsgemäße fluidbetätigte Armaturen-Stellantrieb weist einen für die Erstbefüllung des Fluidsystems mit Hydraulikfluid aus einer Kartusche geeigneten, insbesondere an der Basiseinheit angeordneten Füllanschluss auf. Dies ermöglicht die anwenderseitige Inbetriebnahme eines hydraulisch arbeitenden Armaturen-Stellantriebs nach der vorliegenden Erfindung, ohne dass der Anwender in irgend einer Form mit Hydraulikfluid in Berührung kommt. Dies wiederum trägt dazu bei, die hinsichtlich ihres Betriebsverhaltens elektrischen Armaturen-Stellantrieben überlegenen (s.o.) hydraulisch betätigten Armaturen-Stellantriebe auch in solchen Anwendungen zum Einsatz zu bringen, in denen nutzerseitig besonderer Wert auf Sauberkeit und ein minimales Risiko, mit Hydraulikfluid in Kontakt zu kommen, gelegt wird.In the context of the present invention, the pressurized fluid supply is decentralized, ie in each case only associated with a single valve actuator, organized by the base unit of the fluid-operated valve actuator according to the invention comprising a pressurized fluid supply unit. In the case of a hydraulically actuated valve actuator according to the present invention, such a pressure fluid supply unit particularly preferably comprises a tank-powered hydraulic unit with a pump driven by an electric motor. In contrast, in the case of a pneumatically actuated valve actuator, the said pressurized fluid supply unit preferably comprises an ambient medium driven by an electric motor, preferably via a filter system, and sucking in a pneumatic pump. The fluid-operated valve actuator according to the invention has a filling connection which is suitable for first filling the fluid system with hydraulic fluid from a cartridge, in particular arranged on the base unit. This allows the user-side commissioning of a hydraulically operated valve actuator according to the present invention, without the user being in any way in contact with hydraulic fluid. This, in turn, contributes to the superior (so) hydraulically operated valve actuators, which are superior in their operating behavior to electrical valve actuators, in applications in which user-friendliness is particularly important for cleanliness and a minimal risk of coming into contact with hydraulic fluid , is placed.
In Anwendung der vorliegenden Erfindung ergibt sich, anders als dies bisher bei fluidischen Armaturenantrieben realisierbar war, die Möglichkeit eines vollständig schlüsselfertigen Armaturenantriebs, dessen Inbetriebnahme durch den jeweiligen Nutzer bzw. Anwender problemlos möglich ist, und zwar bei für leistungsmäßig vergleichbare fluidische Armaturenantriebe bisher nicht erreichbaren geringen Inbetriebnahmekosten. Insoweit spielt die in Anwendung der vorliegenden Erfindung umgesetzte Modul- bzw. Baukastenbauweise eine erhebliche Rolle, die die Bereitstellung von individualisierten, an die jeweilige Anforderung spezifisch angepassten Armaturenantrieben zu äußerst konkurrenzfähigen Kosten gestattet, wobei nicht nur der Wandler und die beiden Linearaktuatoren hinsichtlich ihrer Dimensionierung individuell variiert werden können, sondern vielmehr die weiter unten noch näher erläuterte Möglichkeit besteht, funktional unterschiedliche Linearaktuatoren und mechanische Wandler beliebig miteinander zu kombinieren. So kann der besagte mechanische Wandler beispielsweise die Linearbewegung der Schieber der beiden Linearaktuatoren in eine Drehbewegung umsetzen, nämlich wenn die Armatur ein verdrehbares Sperrglied aufweist, dessen Stellung mittels des Armaturen-Stellantriebs veränderbar ist. Für eine andere Anwendung kann demgegenüber mit den gleichen Linearaktuatoren ein mechanischer Wandler mit einem linearen Abtrieb zu einer Funktionseinheit kombiniert werden. Entsprechendes gilt für die beiden Linearaktuatoren. Hier können insbesondere, in Abhängigkeit von der jeweiligen Anwendung, pneumatische oder hydraulische Linearaktuatoren verbaut werden, wobei innerhalb der beiden Gruppen wiederum unterschiedliche Ausführungsformen zum Einsatz gebracht werden können wie beispielsweise bei pneumatischem Funktionsprinzip klassische pneumatische Aktuatoren, Federaktuatoren mit Steuerluftfüllung, Federaktuatoren mit pneumatischer Vorspannung oder Fluidspeicher.In application of the present invention, unlike heretofore achievable with fluidic valve drives, there is the possibility of a fully turnkey valve drive, the commissioning of which is easily possible by the respective user or user, namely at low for not comparable in terms of performance fluidic valve drives start-up costs. In that regard, implemented in the application of the present invention module or modular construction plays a significant role, which allows the provision of individualized, specifically adapted to the particular requirement valve actuators at extremely competitive costs, not only the converter and the two linear actuators in terms of their dimensions individually can be varied, but rather the possibility explained further below, functionally different linear actuators and mechanical transducers combine with each other. For example, the said mechanical converter can convert the linear movement of the slides of the two linear actuators into a rotational movement, namely if the valve has a rotatable locking member whose position can be changed by means of the valve actuator. For another application In contrast, a mechanical transducer with a linear output can be combined to form a functional unit with the same linear actuators. The same applies to the two linear actuators. Here, in particular, depending on the particular application, pneumatic or hydraulic linear actuators are installed, in turn, different embodiments can be used within the two groups such as pneumatic pneumatic actuators classical actuators, spring actuators with control air filling, spring actuators with pneumatic bias or fluid storage ,
Mit der bei Armaturen-Stellantrieben der hier in Rede stehenden Art typischerweise vorgesehenen fluidischen Steuerung kann ein elektro-fluidischer Signalwandler zusammenwirken, der insbesondere der Basiseinheit vorgelagert sein und ein proportionales Ausgangsverhalten aufweisen kann. An einem mit dem elektro-fluidischen Signalwandler in Verbindung stehenden Signaleingang kann dabei weiterhin eine externe elektrische Regeleinheit angeschlossen sein, welche Eingabemittel, einen Sollwerteingang, eine Regelelektronik, eine Kommunikationseinheit, einen Signalausgang und/oder einen Signalgeber umfassen kann. Im Sinne eines geschlossenen Regelkreises kann dabei das Istwertsignal eines der Armatur zugeordneten Messaufnehmers auf die elektrische Regeleinheit zurückgeführt werden.The fluidic control typically provided for valve actuators of the type in question here may cooperate with an electro-fluidic signal converter, which in particular may be arranged upstream of the base unit and may have a proportional output behavior. An external electrical control unit, which may include input means, a setpoint input, a control electronics, a communication unit, a signal output and / or a signal generator, may furthermore be connected to a signal input connected to the electro-fluidic signal converter. In the sense of a closed control loop, the actual value signal of a sensor assigned to the fitting can be fed back to the electrical control unit.
Gemäß einer bevorzugten Weiterbildung der Erfindung ist vorgesehen, dass mindestens einer der beiden Linearaktuatoren, insbesondere beide Linearaktuatoren als beidseitig fluidbeaufschlagter Aktuator ausgeführt ist/sind, wobei beide Arbeitsräume ständig an eine Druckfluid-Versorgung angeschlossen sind. Dies ist von besonderem Vorteil bei pneumatischen Systemen. Werden in diesem Sinne beide Arbeitsräume des mindestens einen beidseitig fluidbeaufschlagten Linearaktuators direkt an die Druckfluid-Versorgung angeschlossen bzw. von dieser beaufschlagt und zu Positionierzwecken, d.h. zur Veränderung der Position des Schiebers des betreffenden Linearaktuators, einer der beiden Arbeitsräume gezielt entlüftet, ist der Schieber des betreffenden Linearaktuators in jeder Betriebslage mit maximaler Steifigkeit eingespannt, was eine besonders gute Regelbarkeit erlaubt. Weiterhin kann mit einem solchen Aufbau sichergestellt werden, dass niemals Umgebungsluft in den betreffenden Linearaktuator eingesogen wird, wodurch das Eindringen von Verunreinigungen in das System ausgeschlossen und die Lebensdauer erhöht wird. Ein weiterer Vorteil dieser Weiterbildung besteht in dem kostengünstigen und sehr einfach zu beherrschenden Aufbau, indem der mindestens eine doppelt wirkende Linearaktuator, besonders bevorzugt beide doppelt wirkenden Linearaktuatoren mit einem einzigen elektro-fluidischen Signalwandler geregelt werden kann/können. All die genannten Vorteile sind wiederum insbesondere bei pneumatischen Armaturen-Stellantrieben von besonderer praktischer Relevanz.According to a preferred development of the invention, it is provided that at least one of the two linear actuators, in particular both linear actuators, is / is designed as a fluid-actuated actuator on both sides, wherein both working spaces are constantly connected to a pressurized fluid supply are connected. This is of particular advantage in pneumatic systems. Are in this sense both working spaces of the at least one double-sided fluid-actuated linear actuator connected directly to the pressurized fluid supply and acted upon by this and for positioning purposes, ie to change the position of the slide of the respective linear actuator, one of the two working spaces vented specifically, the slide of respective linear actuator in each operating position clamped with maximum rigidity, which allows a particularly good controllability. Furthermore, it can be ensured with such a construction that ambient air is never sucked into the respective linear actuator, whereby the penetration of impurities into the system is excluded and the life is increased. Another advantage of this development is the cost-effective and very easy to control structure by the at least one double-acting linear actuator, more preferably both double-acting linear actuators can be controlled with a single electro-fluidic signal converter / can. All the advantages mentioned are again of particular practical relevance, in particular in the case of pneumatic valve actuators.
Im Sinne einer hohen Ausfallsicherheit des Systems kann nicht nur, wie weiter oben bereits angesprochen, Fluidenergie in einem (insbesondere externen) Druckspeicher gespeichert werden, um im Falle eines Ausfalls der Druckfluid-Versorgung die Armatur zumindest noch in eine vorgegebene Sicherheitsstellung bringen zu können. Vielmehr kann auch, gegebenenfalls zusätzlich, in mindestens einen der beiden Linearaktuatoren (oder ggf., insbesondere durch Anflanschen eines Federmoduls an den betreffenden Linearaktuator, in eine den betreffenden Linearaktuator umfassende Baugruppe) eine mechanische Speicherfeder integriert sein. Besonders bevorzugt wird eine solche mechanische Speicherfeder dabei über fluidischen Druck vorgespannt und in der vorgespannten Stellung verriegelt, so dass sie den Schieber des betreffenden Linearaktuators nicht in dem Sinne ständig beaufschlagt, dass permanent gegen die Kraft der mechanischen Speicherfeder gearbeitet werden müsste. In diesem Falle beaufschlagt die mechanische Speicherfeder den Schieber des zugeordneten Linearaktuators nur nach Betätigen einer Entriegelung, mittels derer eine die Speicherfeder sperrende Blockade aufgehoben wird. Eine solche im normalen Betriebsfall blockierend gesperrte, nur im Notfall durch Aufheben der Blockade freigegebene mechanische Speicherfeder kombiniert die Vorteile einer hohen Zuverlässigkeit des Armaturen-Stellantriebs mit weiteren Gesichtspunkten wie Wirtschaftlichkeit, Kompaktheit sowie Stelldynamik.In terms of a high reliability of the system not only, as already mentioned above, fluid energy can be stored in a (especially external) accumulator to bring in case of failure of the pressurized fluid supply, the valve at least in a predetermined safety position. Rather, in addition, in at least one of the two linear actuators (or, if appropriate, in particular by flanging a spring module to the relevant linear actuator, into an assembly comprising the respective linear actuator), if appropriate in addition. be integrated into a mechanical storage spring. Particularly preferably, such a mechanical accumulator spring is biased by fluid pressure and locked in the biased position, so that they are not constantly applied to the slide of the respective linear actuator in the sense that would have to be permanently worked against the force of the mechanical storage spring. In this case, the mechanical storage spring acts on the slide of the associated linear actuator only after actuation of an unlocking, by means of which a blockage blocking the storage spring is released. Such blocked in normal operation blocking locked, released only in an emergency by removing the blockage mechanical accumulator combines the advantages of high reliability of the valve actuator with other aspects such as economy, compactness and dynamic response.
Weitere vorteilhafte Weiterbildungen der vorliegenden Erfindung sind in den Unteransprüchen angegeben bzw. ergeben sich aus der nachfolgenden Erläuterung bevorzugter Ausführungsbeispiele der vorliegenden Erfindung.Further advantageous developments of the present invention are specified in the dependent claims or will become apparent from the following description of preferred embodiments of the present invention.
Es zeigt
- Fig. 1
- in perspektivischer Ansicht von oben einen Armaturen-Stellantrieb nach der vorliegenden Erfindung,
- Fig. 2
- in perspektivischer Ansicht von unten den Armaturen-Stellantrieb nach
Fig. 1 , - Fig. 3
- den Armaturen-Stellantrieb nach den
Fig. 1 und2 in Draufsicht von oben, - Fig. 4
- den Armaturen-Stellantrieb nach den
Fig. 1 bis 3 in der Ansicht gemäßFig. 3 mit zusätzlich montieren Anbauteilen, - Fig. 5
- den Armaturen-Stellantrieb nach
Fig. 4 in Seitenansicht, - Fig. 6
- den mechanischen Wandler des Armaturen-Stellantriebs nach den
Fig. 1 bis 5 in perspektivischer Ansicht von oben, - Fig. 7
- den mechanischen Wandler nach
Fig. 6 in Seitenansicht, - Fig. 8
- den mechanischen Wandler mit angeflanschten Linearaktuatoren nach
Fig. 7 im horizontalen Längsschnitt, - Fig. 9
- im Detail die Befüllungskartusche des Armaturen-Stellantriebs nach den
Fig. 4 und5 - Fig. 10
- im Längsschnitt eine bei dem Armaturen-Stellantrieb nach den
Fig. 1 wahlweise alternativ zu den dort gezeigten Linearaktuatoren einsetzbare, einen Linearaktuator und einen angeflanschten Hydraulikspeicher umfassende Baugruppe undbis 5 - Fig. 11
- einen bei dem Armaturen-Stellantrieb nach den
Fig. 1 wahlweise alternativ einsetzbaren Linearaktuator in Form eines Federaktuators im Längsschnitt.bis 5
- Fig. 1
- in perspective view from above a valve actuator according to the present invention,
- Fig. 2
- in perspective view from below the valve actuator after
Fig. 1 . - Fig. 3
- the valve actuator after the
Fig. 1 and2 in top view from above, - Fig. 4
- the valve actuator after the
Fig. 1 to 3 in the view according toFig. 3 with additional mounting parts, - Fig. 5
- the valve actuator after
Fig. 4 in side view, - Fig. 6
- the mechanical converter of the valve actuator after the
Fig. 1 to 5 in a perspective view from above, - Fig. 7
- the mechanical transducer after
Fig. 6 in side view, - Fig. 8
- the mechanical converter with flanged linear actuators after
Fig. 7 in horizontal longitudinal section, - Fig. 9
- in detail the filling cartridge of the valve actuator after the
Fig. 4 and5 - Fig. 10
- in longitudinal section one in the valve actuator after the
Fig. 1 to 5 optionally as an alternative to the linear actuators shown there, a linear actuator and a flanged hydraulic accumulator comprehensive assembly and - Fig. 11
- one at the valve actuator after the
Fig. 1 to 5 optionally alternatively usable linear actuator in the form of a spring actuator in longitudinal section.
Der in den
An dem Notbetätigungsblock 4 ist ein Anschluss 16 für einen externen Hydraulikspeicher 17 (vgl.
Der mechanische Wandler 5 umfasst ein als Wandlerblock 20 ausgeführtes Gehäuse, das unmittelbar an die zu betätigende Armatur anflanschbar ist, zu welchem Zweck der Wandlerblock 20 an seiner Unterseite Gewindebohrungen 21 für Befestigungsschrauben aufweist. An der Unterseite des Wandlerblocks befindet sich weiterhin der auf die Welle der Armatur wirkende mechanische Abtrieb 23 des Armaturen-Stellantriebs. Dieser umfasst in diesem Ausführungsbeispiel einen Innenvierkant 22. Alternative Ausführungen des Abtriebs, um das notwendige Drehmoment zuverlässig auf den Eingang der Armatur zu übertragen, sind bekannt und in der Praxis im Einsatz, beispielsweise eine Wellenverbindung mittels Passfeder. Innerhalb des mechanischen Wandlers 5 wird die Linearbewegung der Schieber 81 der beiden einander gegenüberliegend angeordnet an den mechanischen Wandler 5 angeflanschten Linearaktuatoren 6 und 7 in eine Drehbewegung des Abtriebs 23 umgesetzt. Dies wird erreicht, indem eine linear, parallel zu den die Schieber 81 bildenden Kolben 24 und 25 der Linearaktuatoren 6 und 7 verschiebbare Zahnstange 26 mit einem Ritzel 27 kämmt, welches drehfest mit dem mechanischen Abtrieb 23 verbunden ist. Die Zahnstange 26 ist dabei Teil eines Schiebers 72, der weiterhin zwei an jeweils einem Ende fest mit der Zahnstange verbundene zylindrische Druckund Führungsstücke 73 aufweist, die in jeweils einer zugeordneten Führungsbuche 74 verschiebbar geführt sind und auf die die stirnseitig an ihnen anliegenden Kolben 24 bzw. 25 der Linearaktuatoren 6 bzw. 7 wirken.The
Auf dem Wandlerblock 20 ist an dessen Oberseite ein durch ein eine Sichtkuppel 28 aufweisendes Sichtglas 29 abgedeckter Kontrollkasten 30 angebracht. Innerhalb des Kontrollkastens ist eine mit dem Abtrieb 23 drehfest verbundene optische Stellungsanzeige 31 mit einem in die Sichtkuppel 28 hinein ragenden und somit von allen Seiten ablesbaren Stellungszeiger 32 angeordnet. Weiterhin befinden sich unterhalb der optischen Stellungsanzeige ein Winkelgeber 33, dessen Signal zu der elektronischen Steuerung rückgeführt wird, sowie zwei ebenfalls auf die Steuerung geschaltete Sensoren 34 für eine Endlagenabfrage, wobei die beiden Endlagen durch Stifte 35 definiert werden können, die in eine Rasterung 36 in einer mit dem Abtrieb 23 drehfest verbundenen Scheibe 37 einsteckbar sind.On the
Der Linearaktuator 6 umfasst einen Zylinder 38, in dem der Kolben 24 dichtend geführt ist; in entsprechender Weise umfasst der Linearaktuator 7 einen Zylinder 39, in dem der Kolben 25 dichtend geführt ist. Beide Zylinder 38 und 39 sind stirnseitig jeweils durch einen Deckel 40 abgeschlossen, der zusammen mit dem jeweils zugeordneten Zylinder und dem in diesem geführten Kolben 24 bzw. 25 einen hydraulischen Arbeitsraum 41 begrenzt, in den eine zugeordnete Hydraulikleitung 42 mündet. Jeder der beiden Linearaktuatoren ist mit einer hydraulischen Endlagendämpfung ausgestattet. Zu diesem Zweck befindet sich innerhalb des jeweiligen Arbeitsraumes 41 nahe dem zugeordneten Deckel 40 jeweils eine Scheibe 43 mit einer zentrischen Bohrung 44 und Überströmkanälen 45. An dem jeweiligen Kolben 24 bzw. 25 ist stirnseitig ein Zapfen 46 angeordnet, der, wenn sich der Kolben der Scheibe 43 nähert, mit leichtem Spiel (Ringspalt) in die Bohrung 44 eintaucht, hierdurch die weitere Verdrängung von Hydraulikflüssigkeit aus dem Arbeitsraum 41 über den Verbindungsraum 47 in die Hydraulikleitung 42 hinein drosselt und auf diese Weise die weitere Bewegung des Kolbens dämpft. Die Scheiben 43 stellen ergänzend Anschläge für die Kolben dar, zu welchem Zweck jeweils ihre genaue Position innerhalb des zugeordneten Arbeitsraumes 41 mittels der Verstellschraube 48 einstellbar ist.The
Der Armaturen-Stellantrieb 1 ist baukastenartig aus den vorstehend erläuterten einzelnen, zu einer Funktionseinheit zusammengefügten Komponenten in Form der Basiseinheit 2 samt integrierter Druckfluid-Versorgungseinheit 3, des Notbetätigungsblocks 4, des mechanischen Wandlers 5 und der beiden Linearaktuatoren 6 und 7 aufgebaut. Die besagten Einzelkomponenten sind hierzu über jeweils einander paarweise zugeordnete Flanschflächen miteinander verbunden. Dabei verlaufen sämtliche die Basiseinheit 2 samt integrierter Druckfluid-Versorgungseinheit 3, den Notbetätigungsblock 4 und die Linearaktuatoren 6 und 7 untereinander verbindende Fluidverbindungen als Hydraulikleitungen innerhalb der betreffenden Komponenten, wobei der hydraulische Anschluss der beiden Linearaktuatoren 6 und 7 an den Notbetätigungsblock 4 über durch den Wandlerblock 20 hindurch verlaufende Hydraulikleitungen erfolgt. Erkennbar existieren auf diese Weise keinerlei freiliegende Fluidleitungen. Und es ergibt sich ein Armaturen-Stellantrieb in Form eines kompakten, geschlossenen, einen elektrischen Eingang und einen auf den Eingang der Armatur wirkenden mechanischen Abtrieb aufweisenden fluidischen Antriebssystems.The valve actuator 1 is constructed in a modular manner from the above-described individual, assembled into a functional unit components in the form of the
Die besagten, die einzelnen Komponenten untereinander hydraulisch verbindenden Fluidverbindungen sind im Bereich der von ihnen durchsetzten Trennebenen zwischen den einzelnen Komponenten mit selbstschließenden Absperrungen 49 ausgestattet. Diese öffnen erst bei einer vollständigen Montage der beiden jeweils betroffenen Komponenten und schließen umgekehrt selbsttätig, wenn bei einem Zerlegen des Armaturen-Stellantriebs die betreffenden Komponenten getrennt werden. So weist der gezeigte mechanische Wandler an den Anschlussflächen für die Linearaktuatoren 6 und 7 jeweils drei mit Absperrungen 49 ausgestattete Übergaben für Hydraulikfluid auf, nämlich jeweils eine für Arbeitsdruck, Tank und Speicher, wobei der Speicheranschluss funktional nur dann zum Tragen kommt, wenn bei der individuellen Konfiguration des Armaturen-Stellantriebs eine einen Linearaktuator mit einem baulich zugeordneten Hydraulikspeicher umfassende Baugruppe (s.u.) zum Einsatz kommt. Und an der Anschlussfläche für den Notbetätigungsblock 4 weist der gezeigte mechanische Wandler 5 vier mit Absperrungen 49 ausgestattete Übergaben für Hydraulikfluid auf, nämlich zwei für den Arbeitsdruck der beiden Linearaktuatoren und jeweils einen für Tank und Speicher. Den Absperrungen sind baulich jeweils Filterelemente 82 in Form von in einem Topf 83 aufgenommenen Filtern zugeordnet.The said, the individual components with each other hydraulically connecting fluid connections are equipped with self-closing
Der Armaturen-Stellantrieb ist für eine Erstbefüllung des Fluidsystems mit Hydraulikflüssigkeit aus (mindestens) einer Kartusche hergerichtet. Zu diesem Zweck ist an dem Notbetätigungsblock 4 ein Befüllanschluss 50 vorgesehen. Teil dieses Befüllanschlusses ist (vgl.
Statt des weiter oben beschriebenen externen Hydraulikspeichers 17 oder ggf. ergänzend zu diesem kann mindestens ein baulich in einen der beiden Linearaktuatoren 6 und 7 integrierter Hydraulikspeicher vorgesehen sein. Entsprechendes gilt für die Verbindung von Linearaktuator und Hydraulikspeicher zu einer baulichen Einheit, d.h. einer Baugruppe. Eine solche Möglichkeit ist in
Die in dem Speicherraum 62 eingespannte Hydraulikflüssigkeit wird bei Notbetätigung des Armaturen-Stellantriebs über eine entsprechende Betätigung der Ventile des Notbetätigungsblocks 4 auf einen der beiden Linearaktuatoren 6 oder 7 geschaltet, und zwar in Abhängigkeit davon, ob für die Sicherheitsstellung die Armatur zu öffnen oder aber zu schließen ist. Entsprechendes gilt im übrigen für die Verwendung des weiter oben beschriebenen externen Hydraulikspeichers 17. Indem weder eine mechanische Speicherfeder den Schieber 72 des mechanischen Wandlers 5, noch der Speicherraum 62 ständig einen hydraulischen Arbeitsraum 41 eines der Linearaktuatoren 6 bzw.7 ständig beaufschlagt, sondern nur nach Betätigen einer - hier durch die Ventile des Notbetätigungsblocks 4 realisierten - Entriegelung, mittels derer eine die Speicherfedern 59 sperrende - hier hydraulische - Blockade aufgehoben wird, steht im Normalbetrieb die gesamte Leistung der Linearaktuatoren für die Verstellung der Armatur zur Verfügung. Dementsprechend können die Linearaktuatoren vergleichsweise klein ausgeführt werden, was eine besonders kompakte Ausführung des Armaturen-Stellantriebs ermöglicht. Durch beliebige und bedarfsorientierte Ausstattung des Armaturen-Stellantriebs mit einem Hydraulikspeichermodul 54 an einem der beiden Linearaktuatoren, mit zwei Hydraulikspeichermodulen 54 an beiden Linearaktuatoren und/oder einem externen Hydraulikspeicher lässt sich der Armaturen-Stellantrieb ersichtlich flexibel an die jeweiligen Anforderungen wie auch an die jeweiligen räumlichen Verhältnisse anpassen.The hydraulic fluid clamped in the
Einer der Linearaktuatoren kann im Übrigen als reiner Federaktuator 70 ausgeführt sein, der, wie
Erkennbar können die beiden Linearaktuatoren am mechanischen Wandler 5 funktionell beliebig kombiniert werden und der Wandler an jeder seiner beiden Anschlussstellen einen fluidischen Aktuator, einen mechanisch gekoppelten Federaktuator, einen mechanisch entkoppelten Federaktuator mit fluidischer Betätigung oder einen mechanisch entkoppelten Federaktuator mit fluidischer Betätigung sowie einen davon unabhängigen zusätzlichen mechanisch gekoppelten fluidischen Aktuator aufnehmen, wobei die fluidische Steuerung in allen Fällen von der Basiseinheit übernommen wird.Visible, the two linear actuators on the
Claims (11)
- A fluid-actuated actuating drive (1) for a valve, in particular an actuating drive for shut-off, safety or regulating valves, comprising a base unit (2) having control valves, two linear actuators (6, 7) which are located opposite one another and can be actuated fluidically by means of the control valves, a mechanical transducer (5) which is disposed between the two linear actuators and couples the gates (81) thereof with one another, the outlet of said transducer being coupled to the inlet of the valve, and an electrically driven hydraulic fluid supply unit (3) integrated into the base unit (2), wherein the valve actuating drive uses hydraulic fluid as a working fluid, comprises a connection (16) for an external hydraulic accumulator (17) and is constituted as a closed fluidic drive system comprising an electrical inlet and a mechanical drive (23) acting on the inlet of the valve,
characterised in that
the valve actuating drive (1) is constituted in a modular manner by individual components in the form of the base unit, the two linear actuators and the mechanical transducer fitted together to form a functional unit and all the fluidic connections between the base unit (2) and the linear actuators (6, 7) and, as the case may be, the mechanical transducer (5) run inside the components concerned, so that no exposed fluid lines exist, wherein it further comprises a self-priming filling device which comprises a filling connection (50) and is disposed in particular on the base unit (2) or an emergency actuation unit (4), provided if required, and is suitable for the initial filling of the fluid system with hydraulic fluid from a cartridge (53), said filling device requiring no additional external top-up connection apart from the cartridge connection. - The actuating drive according to claim 1, characterised in that the hydraulic fluid supply unit (3) comprises a hydraulic unit (11) supplied from a tank (10) with a pump driven by an electric motor (9).
- The actuating drive according to claim 1, characterised in that the fluid connections are equipped, in the region of parting planes between the components through which said fluid connections pass, with self-closing shut-off elements (49), to which filter elements 82 are assigned in each case, where necessary structurally.
- The actuating drive according to any one of claims 1 to 3, characterised in that the two linear actuators (6, 7) are flange-mounted on the mechanical transducer (5), which for its part is connected via a flange connection to the base unit (2) or an emergency actuation unit (4) disposed between the base unit (2) and the transducer.
- The actuating drive according to any one of claims 1 to 4, characterised in that it comprises preset or flexibly set display means, limit switches, limit stops, end-of-travel dampers, manual actuation means and/or position sensors.
- The actuating drive according to any one of claims 1 to 5, characterised in that at least one of the linear actuators (6, 7) is constituted as a double-acting actuator acted upon by fluid on both sides, wherein both working chambers of the respective linear actuator are always connected to a pressure supply and acted upon by hydraulic fluid.
- The actuating drive according to any one of claims 1 to 6, characterised in that at least one mechanical storage spring (59; 71) is integrated into at least one of the two linear actuators (6, 7; 70) or at least one assembly comprising one of the two linear actuators (6, 7).
- The actuating drive according to claim 7, characterised in that at least one mechanical storage spring (59) does not act at all times on the gate (81) of the respective linear actuator, but only after actuation of an unlocking device, by means of which a blockade blocking the storage springs is removed.
- The actuating drive according to claim 7 or claim 8, characterised in that the mechanical storage spring (59) is placed under tension and blocked by means of a fluid, wherein in particular the fluidic blockade can be electrically released when defined disruptive events occur and the actuating drive assumes a defined safety position.
- The actuating drive according to any one of claims 1 to 9, characterised in that a fluidic pressure accumulator equipped with a storage spring (59) is used, which in the loaded state accumulates at least the fluidic energy including the necessary safety reserves required to reach a safety position of the valve in the event of a failure of a hydraulic fluid supply unit (3).
- The actuating drive according to any one of claims 1 to 10, characterised in that the two linear actuators on the mechanical transducer can be combined arbitrarily in a functional manner and the transducer can accommodate at each of its two connection points a fluidic actuator, a mechanically coupled spring actuator, a mechanically decoupled spring actuator with fluidic actuation or a mechanically decoupled spring actuator with fluidic actuation as well as an additional mechanically coupled fluidic actuator independent thereof, wherein the fluidic control is assumed in all cases by the base unit.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102010007137A DE102010007137A1 (en) | 2010-02-05 | 2010-02-05 | Fluid operated actuator on a valve |
PCT/EP2011/000527 WO2011095350A1 (en) | 2010-02-05 | 2011-02-04 | Fluid-actuated actuating drive on a valve |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2531730A1 EP2531730A1 (en) | 2012-12-12 |
EP2531730B1 true EP2531730B1 (en) | 2015-06-10 |
Family
ID=43836890
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11703397.7A Active EP2531730B1 (en) | 2010-02-05 | 2011-02-04 | Fluid-actuated valve-actuating drive |
Country Status (9)
Country | Link |
---|---|
US (1) | US8752806B2 (en) |
EP (1) | EP2531730B1 (en) |
JP (1) | JP5816200B2 (en) |
KR (1) | KR101730208B1 (en) |
CN (1) | CN102834617B (en) |
BR (1) | BR112012019643B1 (en) |
DE (1) | DE102010007137A1 (en) |
RU (1) | RU2551468C2 (en) |
WO (1) | WO2011095350A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2016202354A1 (en) * | 2015-06-15 | 2016-12-22 | Festo Ag & Co. Kg | Rotary drive with position indicator and process valve unit |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013007927B4 (en) | 2013-05-10 | 2014-12-24 | Hoerbiger Automatisierungstechnik Holding Gmbh | drive unit |
DE202013006583U1 (en) * | 2013-07-22 | 2014-10-23 | Liebherr-Aerospace Lindenberg Gmbh | Valve block module for a positioning cylinder |
CN103644154B (en) * | 2013-12-20 | 2015-11-18 | 东莞市泽森自动化设备有限公司 | Pneumatic actuator and control integration module thereof |
CN106321936A (en) * | 2015-07-01 | 2017-01-11 | 泰思康公司 | Explosion resistant electro-pneumatic controller |
US10385879B2 (en) * | 2016-06-27 | 2019-08-20 | Tescom Corporation | Explosion resistant electro-pneumatic controller |
ES2902788T3 (en) * | 2015-07-22 | 2022-03-29 | Bucher Hydraulics Gmbh | Compact electric linear drive for a rack, in particular a hydraulic valve, and method for mounting it |
US10670054B2 (en) | 2017-10-25 | 2020-06-02 | Dresser, Llc | Constructing valve positioners for hazardous areas |
US11306748B2 (en) | 2017-10-25 | 2022-04-19 | Dresser, Llc | Constructing valve positioners for hazardous areas |
DE102018116830A1 (en) * | 2018-07-11 | 2020-01-16 | Agilent Technologies, Inc. - A Delaware Corporation - | Valve arrangement with valve module and basic module |
CN110514946B (en) * | 2019-07-12 | 2021-11-23 | 国网浙江省电力有限公司嘉兴供电公司 | High-safety direct-current grounding test device |
CN110608311B (en) * | 2019-07-23 | 2024-04-16 | 太重集团榆次液压工业(济南)有限公司 | Manual-automatic integrated hydraulic driver for marine valve and driving method |
DE102020112548A1 (en) * | 2020-05-08 | 2021-11-11 | Auma Riester Gmbh & Co. Kg | Fail-safe drive and actuator with a fail-safe drive |
DE102021200100A1 (en) * | 2021-01-08 | 2022-07-14 | Robert Bosch Gesellschaft mit beschränkter Haftung | Hydraulic gear unit, especially for deep sea applications |
Family Cites Families (31)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1780471A (en) * | 1928-07-20 | 1930-11-04 | Nat Automatic Tool Co | Hydraulic control valve unit |
US2716015A (en) * | 1952-07-18 | 1955-08-23 | Stewart Warner Corp | Snap acting thermostatic valve |
US3218024A (en) * | 1962-07-18 | 1965-11-16 | Sealol | Fluid motor actuated ball valve |
US3452961A (en) * | 1966-05-02 | 1969-07-01 | Keystone Valve Corp | Disc valve operator with compound driving linkage |
US3887160A (en) * | 1970-09-18 | 1975-06-03 | Sperry Rand Australia Ltd | Fluid operated actuator for movable members |
JPS5180721U (en) * | 1974-12-20 | 1976-06-26 | ||
DE2533076A1 (en) * | 1975-07-24 | 1977-02-24 | Kromberg Gmbh | Universal rack and pinion gear - provides for manual or power drive to convert linear into rotary motion |
SU1225930A1 (en) * | 1982-06-29 | 1986-04-23 | Ордена Трудового Красного Знамени Институт Сверхтвердых Материалов Ан Усср | Servo actuator |
CH661331A5 (en) * | 1983-08-25 | 1987-07-15 | Fischer Ag Georg | VALVE DEVICE WITH A REMOTE CONTROLLED ACTUATOR. |
JPS6235105A (en) * | 1985-08-07 | 1987-02-16 | Nippon Soken Inc | Hydraulic actuator |
JPS6453505U (en) * | 1987-09-28 | 1989-04-03 | ||
IT1233979B (en) * | 1989-03-08 | 1992-04-22 | Biffi Spa | SUBMARINE VALVE ACTUATOR |
JPH0322104U (en) * | 1989-07-14 | 1991-03-06 | ||
EP0665373B1 (en) | 1993-12-28 | 2000-05-10 | Zexel Corporation | Fuel injection pump |
DE9406760U1 (en) * | 1994-04-22 | 1994-08-18 | Paul Pleiger Maschinenfabrik GmbH & Co KG, 58452 Witten | Compact actuator unit for fittings, especially in shipbuilding |
DE59503395D1 (en) * | 1994-01-28 | 1998-10-08 | Pleiger Maschf Paul | Device for operating hydraulically operated fittings |
US5810326A (en) * | 1996-02-16 | 1998-09-22 | Mueller Industries, Inc. | Refrigerant powered actuated ball valve |
CA2269585A1 (en) * | 1996-09-12 | 1998-03-19 | Etrema Products, Inc. | Compact actuator and controller and pumping apparatus for same |
JP3769387B2 (en) * | 1998-07-22 | 2006-04-26 | カヤバ工業株式会社 | Hydraulic control device |
US5967167A (en) * | 1998-08-06 | 1999-10-19 | Ctb, Inc. | Remote controlled drinker system |
JP2002274488A (en) * | 2001-03-22 | 2002-09-25 | Showa Corp | Tilt device for ship propelling machine |
US6659119B2 (en) * | 2001-12-18 | 2003-12-09 | Taylor Innovations, L.L.C. | Fluid pressure responsive dual piston or emergency shutdown valve actuator |
JP3968266B2 (en) * | 2002-04-30 | 2007-08-29 | 株式会社東芝 | Hydraulic pressure generator |
FR2847116A1 (en) | 2002-11-07 | 2004-05-14 | Ksb Sas | DEVICE FOR CONTROLLING AN INTEGRATED ELECTRO-HYDRAULIC ACTUATOR |
DE10317282B4 (en) * | 2003-04-11 | 2005-07-28 | Schunk Gmbh & Co. Kg Fabrik Für Spann- Und Greifwerkzeuge | Turning or swiveling device and connection module for a turning or swiveling device |
JP4369292B2 (en) | 2004-05-06 | 2009-11-18 | タイコ フローコントロールジャパン株式会社 | Emergency shut-off valve device |
US7913971B2 (en) * | 2005-04-29 | 2011-03-29 | Cameron International Corporation | Hydraulic override |
JP4864521B2 (en) * | 2006-04-17 | 2012-02-01 | 株式会社キッツ | Spring actuator |
DE102006045442A1 (en) * | 2006-09-26 | 2008-03-27 | Robert Bosch Gmbh | Hydrostatic drive unit |
DE102008014539A1 (en) | 2008-03-15 | 2009-09-17 | Hoerbiger Automatisierungstechnik Holding Gmbh | Hydromechanical system |
US8467907B2 (en) * | 2009-01-17 | 2013-06-18 | Certus Process Solutions | Automated valve with self-contained valve actuator system |
-
2010
- 2010-02-05 DE DE102010007137A patent/DE102010007137A1/en not_active Withdrawn
-
2011
- 2011-02-04 KR KR1020127020553A patent/KR101730208B1/en active IP Right Grant
- 2011-02-04 RU RU2012134334/06A patent/RU2551468C2/en active
- 2011-02-04 CN CN201180017826.3A patent/CN102834617B/en active Active
- 2011-02-04 JP JP2012551555A patent/JP5816200B2/en active Active
- 2011-02-04 EP EP11703397.7A patent/EP2531730B1/en active Active
- 2011-02-04 BR BR112012019643-0A patent/BR112012019643B1/en active IP Right Grant
- 2011-02-04 WO PCT/EP2011/000527 patent/WO2011095350A1/en active Application Filing
-
2012
- 2012-08-03 US US13/566,604 patent/US8752806B2/en active Active
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2016202354A1 (en) * | 2015-06-15 | 2016-12-22 | Festo Ag & Co. Kg | Rotary drive with position indicator and process valve unit |
Also Published As
Publication number | Publication date |
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BR112012019643B1 (en) | 2021-01-12 |
JP5816200B2 (en) | 2015-11-18 |
RU2551468C2 (en) | 2015-05-27 |
CN102834617B (en) | 2016-03-02 |
US20130015379A1 (en) | 2013-01-17 |
JP2013519046A (en) | 2013-05-23 |
KR20120120285A (en) | 2012-11-01 |
KR101730208B1 (en) | 2017-05-11 |
DE102010007137A1 (en) | 2011-08-11 |
CN102834617A (en) | 2012-12-19 |
BR112012019643A2 (en) | 2016-05-03 |
WO2011095350A1 (en) | 2011-08-11 |
RU2012134334A (en) | 2014-03-10 |
EP2531730A1 (en) | 2012-12-12 |
US8752806B2 (en) | 2014-06-17 |
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