EP0725889B1 - Moteur de commande, notamment pour soupapes a fermeture rapide - Google Patents

Moteur de commande, notamment pour soupapes a fermeture rapide Download PDF

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Publication number
EP0725889B1
EP0725889B1 EP94929481A EP94929481A EP0725889B1 EP 0725889 B1 EP0725889 B1 EP 0725889B1 EP 94929481 A EP94929481 A EP 94929481A EP 94929481 A EP94929481 A EP 94929481A EP 0725889 B1 EP0725889 B1 EP 0725889B1
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EP
European Patent Office
Prior art keywords
actuator
hydraulic fluid
piston
region
pressure
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.)
Expired - Lifetime
Application number
EP94929481A
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German (de)
English (en)
Other versions
EP0725889A1 (fr
Inventor
Dieter MÜRBE
Matthias Hartmann
Hans-Frieder Schneider
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Publication of EP0725889A1 publication Critical patent/EP0725889A1/fr
Application granted granted Critical
Publication of EP0725889B1 publication Critical patent/EP0725889B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
    • F01D21/16—Trip gear
    • F01D21/18—Trip gear involving hydraulic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • 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
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • F15B2011/0243—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits the regenerative circuit being activated or deactivated automatically
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S91/00—Motors: expansible chamber type
    • Y10S91/03—Large area valve

Definitions

  • the invention relates in particular to a servomotor for a quick-closing valve, as is used, for example, on a steam turbine, for which a possibility for rapid stopping is required.
  • a servomotor for a quick-closing valve as is used, for example, on a steam turbine, for which a possibility for rapid stopping is required.
  • This is the case on practically every steam turbine that drives a generator for generating electrical power, both in a power plant and in an industrial plant.
  • a steam turbine, which operates a compressor or the like in a chemical plant, must usually also be provided with such a quick-closing valve along with the associated servomotor.
  • a servomotor of the type mentioned above emerges for a quick-closing valve, in which the pressure range is given by an area of the cylinder which is delimited by the piston, which is non-positively connected to the rod and is slidingly mounted in the cylinder, and one leading to the switching element, which is a plate Pipe socket.
  • the plate is pressed onto the pipe socket by a compression spring and largely closes it off.
  • a panel is provided in the plate, through which the infeed area above the plate communicates with the print area below the plate.
  • An outer pipe socket which surrounds the already mentioned pipe socket, delimits the annular drainage area through which hydraulic fluid can flow when the plate is lifted out of the pressure area by hydraulic fluid, which occurs when the pressure of the hydraulic fluid in the inflow area decreases and a positive pressure drop occurs from the pressure area to the inflow area.
  • the servomotor according to DD 263 801 A1 is characterized in that it can be operated from a single feed system for the hydraulic fluid. If the quick-closing valve to which the servomotor is connected is to be opened, it is sufficient to supply hydraulic fluid to the inflow area and thus to build up a pressure in the inflow area. This pressure presses the plate onto the pipe socket and prevents the hydraulic fluid from draining into the drain area; through the orifice in the plate, the hydraulic fluid reaches the pressure area and ensures a gradual pressure build-up, whereby the piston, which is pressed into an initial position by a corresponding compression spring, is moved into an end position and the quick-closing valve opens.
  • the servomotor is also set up to operate a so-called push-up valve, ie a valve with an annular valve seat and a matching valve cone, which is fastened on a side facing the valve seat to a spindle which projects through the valve seat; at this spindle must be connected to the actuator so that the valve seat is between the valve plug and the actuator.
  • a so-called push-up valve ie a valve with an annular valve seat and a matching valve cone, which is fastened on a side facing the valve seat to a spindle which projects through the valve seat; at this spindle must be connected to the actuator so that the valve seat is between the valve plug and the actuator.
  • the servomotor is unsuitable for operating a so-called opening valve, which also has an annular valve seat with a matching valve cone on a spindle, although the spindle does not protrude through the valve seat, but is connected to the valve cone on a side facing away from the valve seat; an actuator is to be connected to the spindle in such a way that the valve cone is located between the valve seat and the actuator.
  • a winding valve makes it possible to keep the spindle away from fluid which flows through the opened valve; this is not possible with an abutting valve, since the spindle always protrudes through the valve seat through which the fluid flows.
  • An opening valve therefore usually offers an operational advantage over an opening valve.
  • the object of the invention is to provide an improved servomotor of the type mentioned, which is particularly suitable for connection to a so-called opening quick-closing valve.
  • This servomotor can be designed as a compact and largely cylindrical unit.
  • the arrangement of the trigger behind the actuator also benefits the effectiveness of the servomotor, in particular the speed that can be achieved with a quick close.
  • This servomotor in particular opens up the advantages offered by the servomotor, which emerges from the prior art and is intended for an opening valve.
  • the servomotor according to the invention is relatively easy to operate since it only requires a single delivery system for hydraulic fluid, and it enables use on an opening quick-closing valve, i.e. a quick-closing valve, in which a closing element is opened for opening via a valve spindle.
  • a quick-closing valve has the advantage that the valve spindle which serves to open the closing element during normal operation, i.e. while the quick-closing valve is filled with a fluid such as e.g.
  • the switching element in the servomotor is advantageously a plate which is arranged in the inflow region and which lies sealingly on two pipe sockets which adjoin the pressure region and the outlet region.
  • This plate also advantageously contains the aperture in the form of a small hole; In this configuration, a particularly compact shape of the trigger is achieved.
  • the plate is preferably on with another compression spring pressed the pipe socket and thus allows to arrange the trigger in any spatial position.
  • connection between the weight room and the pressure area is advantageously designed as a variable-length pipe connection.
  • a pipe connection is in particular formed with two sealingly inserted pipe sockets, one of the pipe sockets being connected to the stationary trigger and another pipe socket being connected to the movable piston.
  • the plate mentioned advantageously rests as a switching element.
  • the compression spring pressing the piston is preferably arranged in the discharge area; in this way it is wetted by the hydraulic fluid during operation and thus protected to a certain extent against corrosion, and this arrangement also benefits the compactness of the servomotor.
  • the piston has a projection which projects into the weight space and can protrude into a corresponding recess in the end wall while leaving a gap.
  • the embodiment just described makes it possible to brake the piston shortly before reaching the initial position when the servomotor is triggered; This is because when the projection of the piston dips into the recess in the end wall, two spaces communicating with each other only through the mentioned gap are formed in the weight room, the hydraulic fluid having to drain through the gap from one room, depending on the size of the latter Gap and the corresponding flow resistance, which the gap opposes the hydraulic fluid, is only possible in a significantly slower manner. In this way, the piston is braked shortly before it reaches its initial position, which makes a significant contribution to avoiding damage to the servomotor itself and to a valve or the like to which the servomotor is connected.
  • the effect described is achieved in particular when the piston has at least one bore through which the weight space communicates with the pressure area of the trigger and which crosses the projection.
  • the outflow of hydraulic fluid from the weight room takes place at least partially through the gap and provides the desired braking effect.
  • the servomotor of any configuration is particularly suitable for driving a valve, in particular a quick-closing valve.
  • the servomotor of any configuration is used in particular to bring about a quick close on a valve, in particular a quick close valve, in a steam power plant.
  • a servomotor with a trigger is in no way limited to servomotors which are used exclusively to drive quick-closing valves. It is by no means excluded that a servomotor according to the invention can be further strengthened to the extent that it is capable of a continuous and controlled displacement of the rod in addition to performing a quick close using the trigger.
  • Figure 1 shows an actuator for moving a rod 1 along an axis 2, the rod 1 protruding from an end wall 15 of a cylinder 3. Due to the force of a compression spring 17, which acts on a piston 14 movably mounted in the cylinder 3 and connected to the rod 1 and loaded with a compression spring 17, the axis 2 can be pushed out of the cylinder 3 and can be actuated by the cylinder 3 and the hydraulic actuator formed with the piston 14 with hydraulic fluid, in particular hydraulic oil, be drawn into the cylinder 3.
  • a variable force space 16 is provided between the piston 14 and the end wall 15 and defined by the piston 14 against other areas of the cylinder 3. The weight space 16 is acted upon by the hydraulic fluid via a trigger 4.
  • the trigger 4 as seen from the rod 1 along the axis 2, is arranged behind the actuator 3, 14.
  • the trigger 4 has an inflow region 5 which can be acted upon by the hydraulic fluid from a delivery system 6.
  • a hydraulic pump 24 is shown, which can set the hydraulic fluid in the delivery system 6 under a certain pressure, and a control valve 25, through which the hydraulic fluid can optionally flow out of the delivery system 6 and thus the pressure in the delivery system 6 decreased.
  • the regulating valve 25 is closed, so that a pressure can build up in the inflow region 5.
  • This pressure causes a switching element 10 of the trigger 4, namely a plate 10, to be pressed onto two pipe sockets 11 and 12 which are concentric with one another.
  • the inner pipe socket 12 forms the pressure area 7 in its interior, which communicates with the inflow area 5 through an orifice 8, namely a bore 8 in the plate 10.
  • a pressure also builds up in the pressure region 7.
  • Drain bores 26 serve this purpose, for which several possibilities are drawn in FIG. 1.
  • Another compression spring 13 presses the plate 10 onto the pipe socket 11 and 12, thus ensuring that seals, which are not shown in detail, are generally effective between the two pipe socket 11 and 12 and the plate 10.
  • the further compression spring 13 can be designed so that the servomotor can be operated in any spatial position.
  • the compression spring 17 can push the piston 14 back to the end wall 15 into the initial position and thereby convey the hydraulic fluid through the bores 18 and the pipe sockets 19 and 12 in the outlet area 9. This results in an abrupt movement of the piston 14 towards the end wall 15, and the rod 1 is also suddenly pushed out of the cylinder 3. In this way, a quick-closing valve or the like can be closed in the shortest possible time. This process is called "triggering" the trigger.
  • FIG. 1 A specific configuration of the piston 14 and the end wall 15 can also be seen from FIG. 1, which enables the sudden movement of the piston 14 to be braked when triggered by the trigger 4.
  • the piston 14 has a projection 20 projecting towards the end wall 15, which can plunge into a corresponding recess 21 in the end wall 15 while leaving a relatively narrow gap 22. If this occurs, the outflow of the hydraulic fluid is braked due to the increased flow resistance of the gap 22, as a result of which the sudden movement of the piston 14 is braked or intercepted just before the end wall 15.
  • FIG. 2 shows how an actuator can be connected to an opening valve 23, in particular a quick-closing valve 23. Means are not shown which support the cylinder 3 of the servomotor against the quick-closing valve 23. In this regard, reference is made to the relevant specialist knowledge. Certain details of the servomotor shown in sections corresponding to the details shown in FIG. 1, provided with the same reference numerals, so that a new explanation is unnecessary at this point.
  • the rod 1 of the servomotor is connected to a valve spindle 28 of the quick-closing valve 23 via a coupling 27. This valve spindle 28 protrudes into the quick-closing valve 23 and carries at its end a valve cone 29 which can close a corresponding valve opening 30.
  • valve cone 29 If the quick-closing valve 23 is fully open, which is usually the case, the valve cone 29 is seated on a support 31 and thus removes the valve spindle 28 from direct contact with the fluid, in particular steam, which flows through the quick-closing valve 23. Also, the valve cone 29 is not directly flowed around by the fluid and thus offers at most a low flow resistance, which is favorable for avoiding losses.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Actuator (AREA)
  • Lift Valve (AREA)
  • Fluid-Driven Valves (AREA)
  • Hydraulic Turbines (AREA)

Abstract

Un moteur de commande qui sert à déplacer une tige (1) le long d'un axe (2) comprend un organe hydraulique d'actionnement (3, 14) avec un cylindre (3) dans lequel est monté coulissant et étanche un piston (14) lié par friction à la tige, ainsi qu'un ressort de compression (17) qui est lié par friction à la tige (1) et qui agit en sens contraire de l'organe d'actionnement (3, 14). Le moteur de commande (4) comprend un déclencheur (4) avec une zone d'amenée (5) susceptible de recevoir un fluide hydraulique, une zone de compression (7) qui est en communication avec la zone d'amenée (5) par l'intermédiaire d'un diaphragme (8) et qui est raccordée à l'organe d'actionnement (3, 14), et une zone de drainage (9) de laquelle le fluide hydraulique peut être évacué sans pression, ainsi qu'un élément commutateur (10) qui relie la zone de compression (7) à la zone de drainage (9) lorsqu'une différence positive de pression s'établit entre la zone de compression (7) et la zone de drainage (5), et qui autrement obture la zone de drainage (9). La tige (1) peut être poussée hors du cylindre (3) par le ressort de compression et peut être poussée dans le cylindre (3) lorsque le fluide hydraulique est introduit dans la zone d'amenée (5). Ce moteur de commande est particulièrement utile pour entraîner des soupapes à fermeture rapide (23) à tige montante, telles les soupapes souvent utilisées dans des centrales thermiques à vapeur.

Claims (11)

  1. Servomoteur pour le déplacement d'une barre (1) le long d'un axe (2), comportant un actionneur (3, 14) hydraulique et un déclencheur (4), qui est réuni par construction avec celui-ci, qui peut être chargé par un fluide hydraulique et qui communique par l'intermédiaire du fluide hydraulique avec l'actionneur (3, 14),
    a) l'actionneur (3, 14) comporte un cylindre (3), dans lequel est monté de manière glissante et étanche un piston (14) relié de manière positive à la barre (1), et un ressort (17) de pression relié de manière positive à la barre (1) et agissant à l'encontre de l'actionneur (3, 14), la barre (1) pouvant être sortie du cylindre (3) par le ressort (17) de pression et pouvant être rentrée dans le cylindre (3) par chargement en fluide hydraulique de l'actionneur (3, 14) ;
    b) le déclencheur (4) comporte une zone (5) d'admission pouvant être chargée par le fluide hydraulique, une zone (7) de pression, avec laquelle l'actionneur (3, 14) communique, une ouverture (8), par l'intermédiaire de laquelle la zone (5) d'admission communique avec la zone (7) de pression, une zone (9) d'écoulement, de laquelle le fluide hydraulique peut être évacué sans pression, ainsi qu'un élément (10) d'interruption, qui fait communiquer la zone (7) de pression avec la zone (9) d'écoulement, lorsqu'une chute positive de pression de la zone (7) de pression vers la zone (5) d'admission apparaît et qui obture sinon la zone (9) d'écoulement,
    c) le piston (14) délimite, entre lui-même et une paroi frontale (15) du cylindre (3), par laquelle la barre (1) est guidée et sur laquelle le piston est pressé par le ressort (17) de pression, une chambre (16) motrice pouvant être chargée par le fluide hydraulique ;
       caractérisé en ce que
    d) le déclencheur (4) est monté, vu de la barre (1) le long de l'axe (2), derrière l'actionneur (3, 14) ; et
    e) le piston (14) comporte au moins un perçage (18), par lequel la chambre (16) motrice communique avec la zone (7) de pression.
  2. Servomoteur suivant la revendication 1, dans lequel l'élément (10) d'interruption est un plateau (10), qui est monté dans la zone (5) d'admission et qui repose sur deux tubulures (11, 12) qui délimitent la zone (7) de pression et la zone (9) d'écoulement.
  3. Servomoteur suivant la revendication 2, dans lequel le plateau (10) comprend l'ouverture (8).
  4. Servomoteur suivant la revendication 2 ou 3, dans lequel le plateau (10) est pressé sur les tubulures (11, 12) par un ressort supplémentaire de pression (13).
  5. Servomoteur suivant la revendication 1, dans lequel le piston (14) communique par l'intermédiaire d'un raccord (12, 19) tubulaire de longueur variable avec la zone (7) de pression.
  6. Servomoteur suivant la revendication 5, dans lequel le raccord tubulaire (12, 19) est formé de deux tubulures (12, 19) montées l'une dans l'autre de manière étanche.
  7. Servomoteur suivant l'une des revendications précédentes, dans lequel le ressort (17) de pression est monté dans la zone (9) d'écoulement.
  8. Servomoteur suivant l'une des revendications précédentes, dans lequel le piston (14) comporte une saillie (20) dans la chambre (16) motrice, laquelle saillie peut plonger dans un évidement (21) correspondant de la paroi (15) frontale en laissant subsister un intervalle (22).
  9. Servomoteur suivant la revendication 8, dans lequel le piston (14) comporte au moins un perçage (18), par lequel la chambre (16) motrice communique avec la zone (7) de pression et traverse la saillie (20).
  10. Servomoteur suivant l'une des revendications précédentes, qui communique avec une soupape (23), notamment avec une soupape (23) à fermeture rapide.
  11. Utilisation d'un servomoteur suivant l'une des revendications précédentes, pour effectuer une fermeture rapide d'une soupape (23), notamment d'une soupape (23) à fermeture rapide, dans une installation motrice à vapeur.
EP94929481A 1993-10-29 1994-10-17 Moteur de commande, notamment pour soupapes a fermeture rapide Expired - Lifetime EP0725889B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4337113 1993-10-29
DE4337113 1993-10-29
PCT/DE1994/001228 WO1995012057A1 (fr) 1993-10-29 1994-10-17 Moteur de commande, notamment pour soupapes a fermeture rapide

Publications (2)

Publication Number Publication Date
EP0725889A1 EP0725889A1 (fr) 1996-08-14
EP0725889B1 true EP0725889B1 (fr) 1997-04-23

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EP94929481A Expired - Lifetime EP0725889B1 (fr) 1993-10-29 1994-10-17 Moteur de commande, notamment pour soupapes a fermeture rapide

Country Status (11)

Country Link
US (1) US5848779A (fr)
EP (1) EP0725889B1 (fr)
JP (1) JP2762400B2 (fr)
CN (1) CN1055148C (fr)
BR (1) BR9407901A (fr)
CZ (1) CZ286873B6 (fr)
DE (1) DE59402560D1 (fr)
ES (1) ES2101576T3 (fr)
PL (1) PL182380B1 (fr)
RU (1) RU2132468C1 (fr)
WO (1) WO1995012057A1 (fr)

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DE4244304A1 (de) * 1992-12-28 1994-06-30 Asea Brown Boveri Betätigungsvorrichtung für einen hydraulischen Stellantrieb mit druckproportionalem Stellsignal

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112004000191B4 (de) * 2003-05-07 2013-08-29 Richard Steinborn Antrieb für ein Turbinenventil

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PL314006A1 (en) 1996-08-05
JP2762400B2 (ja) 1998-06-04
BR9407901A (pt) 1996-11-19
EP0725889A1 (fr) 1996-08-14
CZ286873B6 (en) 2000-07-12
US5848779A (en) 1998-12-15
JPH08511327A (ja) 1996-11-26
DE59402560D1 (de) 1997-05-28
CN1055148C (zh) 2000-08-02
RU2132468C1 (ru) 1999-06-27
ES2101576T3 (es) 1997-07-01
CN1133624A (zh) 1996-10-16
PL182380B1 (pl) 2001-12-31
CZ120196A3 (en) 1997-01-15
WO1995012057A1 (fr) 1995-05-04

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