EP0451543B1 - Système d'actionnement pour une vanne de régulation de vapeur - Google Patents

Système d'actionnement pour une vanne de régulation de vapeur Download PDF

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Publication number
EP0451543B1
EP0451543B1 EP91104112A EP91104112A EP0451543B1 EP 0451543 B1 EP0451543 B1 EP 0451543B1 EP 91104112 A EP91104112 A EP 91104112A EP 91104112 A EP91104112 A EP 91104112A EP 0451543 B1 EP0451543 B1 EP 0451543B1
Authority
EP
European Patent Office
Prior art keywords
valve
drive
control valves
control valve
control
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.)
Revoked
Application number
EP91104112A
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German (de)
English (en)
Other versions
EP0451543A1 (fr
Inventor
Edi Burch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ABB Asea Brown Boveri Ltd
ABB AB
Original Assignee
ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
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Publication date
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Application filed by ABB Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Asea Brown Boveri Ltd
Publication of EP0451543A1 publication Critical patent/EP0451543A1/fr
Application granted granted Critical
Publication of EP0451543B1 publication Critical patent/EP0451543B1/fr
Anticipated expiration legal-status Critical
Revoked legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • 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
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/20—Devices dealing with sensing elements or final actuators or transmitting means between them, e.g. power-assisted
    • F01D17/22—Devices dealing with sensing elements or final actuators or transmitting means between them, e.g. power-assisted the operation or power assistance being predominantly non-mechanical
    • F01D17/26—Devices dealing with sensing elements or final actuators or transmitting means between them, e.g. power-assisted the operation or power assistance being predominantly non-mechanical fluid, e.g. hydraulic

Definitions

  • the present invention is based on a drive for a steam control valve according to the preamble of patent claim 1.
  • a drive for a steam control valve is known with a control valve arrangement which regulates the pressure of the oil for the hydraulic actuation of an actuator.
  • This control valve arrangement has a slide valve with sealing edges. For oil pressures above about 40 bar, slide valves are only suitable to a limited extent, since oil resin can impair their function.
  • a hydraulic drive is known from US Pat. No. 4,401,009, which has two control valves, each of which has a passage position with an adjustable cross section and a blocking position.
  • the sealing point effective in the blocking position is not designed as a seat valve.
  • the actuator in the control valve is throttled by means of a specially shaped piston until only a small amount of oil flows; this small oil flow is then interrupted by an upstream pilot valve.
  • the two control valves work independently of one another, each being activated in a different direction of movement of the drive.
  • the invention solves the problem of creating a drive for a steam control valve which can always be actuated safely and quickly even with a comparatively high oil pressure.
  • Fig. 1 shows a schematic representation of an actuator 1 for a steam control valve 2, which controls the amount of hot steam flowing through a hot steam line 3 to a turbine, not shown.
  • the steam control valve 2 is through a valve spindle 4 with a in a master cylinder 5 sliding main piston 6 connected.
  • a drive volume 7 pressurized with oil is arranged below the main piston 6.
  • another fluid or a gaseous medium can also be provided.
  • the use of water or water emulsions is also possible.
  • An oil-filled buffer volume 8 is provided above the main piston 6, in which a spring 9 is also arranged, which counteracts the oil pressure in the drive volume 7.
  • a rod 10 is provided on the spring side on the main piston 6 and connects it to a displacement measuring device 11.
  • the rod 10 and the valve spindle 4 penetrate the master cylinder 5 on opposite sides, the instruction of these pressure-tight penetrations being assumed to be known.
  • Oil is fed in under pressure through a line 13, and the necessary oil pressure is generated by a pump (not shown).
  • the line 13 leads through an orifice 14 provided for limiting the opening time of the actuator 1 to an inlet 16 of a first control valve 17 designed as a control valve.
  • Oil 15 is fed in under pressure from a safety oil circuit through a line 15.
  • a line 18 branches off from line 15, which has an orifice 19 and opens into a drive volume 20 of a second control valve 21 designed as a control valve.
  • the line 15 also has an orifice 26 and leads into a drive volume 27 of the first control valve 17. Between the orifice 26 and the drive volume 27, a line 28 branches off from the line 15 and leads into a first proportional pressure valve 29 designed as a seat valve leads.
  • An outlet 30 of this proportional pressure valve 29 is connected to a line 31 which is connected on the one hand to the buffer volume 8 and on the other hand via a check valve 32 to a drain device, not shown.
  • the check valve 32 prevents oil pressure surges, which possibly get into the drain device, from interfering with the actuator 1 through the line 31. From this drain device the oil passes through the aforementioned pump back into line 13.
  • a line 33 branches off from line 18 and leads into a second proportional pressure valve 34 designed as a seat valve.
  • An output 35 of this proportional pressure valve 34 is connected to the line 31.
  • the first control valve 17 is shown in the closed state in FIG. 1, specifically a seat valve 40 prevents the inlet 16 from being connected through to an outlet 41.
  • the input 16 is connected to a drive volume 44 via a line 43.
  • a pressure building up in this drive volume 44 acts in the same direction as the force of a spring 42, that is to say counter to the pressure prevailing in the drive volume 27.
  • the piston area belonging to the drive volume 44 is smaller than that of the piston belonging to the drive volume 27, so that it is ensured that the control valve 17 can always be actuated solely by the pressure of the safety oil.
  • the first control valve 17 has three schematically illustrated switching positions, of which the uppermost, the blocking position, has already been described, the middle position shows a passage position with a controllable cross section and the bottom one shows a passage position with a constant cross section.
  • the control valve 17 is actuated by oil pressure in the drive volume 27, i.e. as the oil pressure rises, it is pressed from the blocking position through the open position with adjustable cross section to the open position with constant cross section.
  • the pressure in the drive volume 44 and the force of the spring 42 work against this oil pressure in the drive volume 27.
  • the outlet 41 is connected via a line 46 to a connection 47 which establishes a connection with the drive volume 7 of the actuator 1. In addition, this connection is 47 connected to an input 48 of the second control valve 21.
  • the inlet 48 of the second control valve 21 is connected to an outlet 49.
  • the output 49 is connected to the line 31 via a line 50.
  • the second control valve 21 has three schematically illustrated switching positions, the uppermost of which acts as a passage position with a constant cross section. The middle switching position acts as an open position with an adjustable cross-section and the lowest as a blocking position.
  • the control valve 21 is actuated by oil pressure in the drive volume 20, ie with increasing oil pressure it is pressed from the open position with a constant cross section to the open position with a controllable cross section into the blocking position.
  • the force of a spring 51 works against this oil pressure in the drive volume 20.
  • the blocking position is realized by a seat valve 52.
  • the input 48 is also connected to a drive volume 54 via a line 53.
  • a pressure building up in this drive volume 54 acts in the same direction as the force of the spring 51, that is to say counter to the pressure prevailing in the drive volume 20.
  • the piston area belonging to the drive volume 54 is smaller than that of the piston belonging to the drive volume 20, so that it is ensured that the control valve 21 can always be actuated solely by the pressure of the safety oil.
  • the two control valves 17 and 21 each have a passage position with a controllable cross section, each with a specific control characteristic.
  • This control characteristic can now be configured identically in both control valves 17, 21, the cross sections to be controlled being configured differently. However, it is also possible for this control characteristic to be designed differently in each of the two control valves 17, 21.
  • the first proportional pressure valve 29 acts similarly to an adjustable orifice, in which on the one hand the orifice opening is to be enlarged via a line 55 with the aid of the oil pressure present, while on the other hand an electromagnet 56, working against this oil pressure, wants to reduce the orifice opening.
  • a line of action 57 indicates that the electromagnet 56 is selectively actuated by an electronic control arrangement 58.
  • the second proportional control valve 34 also acts, in which the oil pressure acts via a line 59 in the opening direction and an electromagnet 60 in the closing direction.
  • a line of action 61 indicates that the electromagnet 60 is also selectively actuated by the electronic control arrangement 58.
  • the electronic control arrangement 58 is also, as indicated by an action line 62, in operative connection with the path measuring device 11.
  • An action line 63 indicates that commands and signals of a higher-level system control system are also entered into the electronic control arrangement 58 and implemented therein.
  • the two proportional pressure valves 29 and 34 are designed as seat valves, so that any decomposition or resinification of the oil cannot impair the function of these valves. Due to the seat construction, a comparatively high level of safety and availability of these valves is achieved. However, it is also possible to use servo valves at these points in the arrangement.
  • control valves 17 and 21 are each additionally provided with a displacement measuring device 65 and 66.
  • the signals emitted by the displacement measuring device 65 become, as by an action line 67 indicated, fed into the electronic control arrangement 58 and further implemented there.
  • a line of action 68 the signals emitted by the displacement measuring device 66 are fed into the electronic control arrangement 58 and processed there further.
  • the embodiment according to FIG. 3 has only a single proportional pressure valve 29 compared to the embodiment according to FIG. 1, which is pressurized with oil via the line 15 and the orifice 26.
  • the drive volume 27 of the control valve 17 is pressurized with this oil.
  • a line 67 branches off from line 15 between orifice 26 and drive volume 27. This line 67 opens directly into the drive volume 20 of the control valve 21.
  • the drive volumes 27 and 20 are accordingly pressurized in parallel and simultaneously with the oil fed in from the line 15.
  • the springs 42 and 51 of the two control valves 17 and 21 counteracting this oil under pressure are mounted in such a way that their pretensioning force can be adjusted mechanically. This adjustability is symbolized by arrows.
  • FIG. 1 shows the drive in the fail-save position, in which, for example, the line 15 is without pressure and in which the steam control valve 2 is closed.
  • both the line 13 and the line 15 can be pressurized, and for the steam control valve 2 to be closed solely by electrically deactivating the proportional pressure valves 29 and 34.
  • the electromagnets 56 and 60 are controlled such that the oil pressure present through the lines 55 and 59 sets the proportional pressure valves 29 and 34 to passage, so that no oil pressure can build up in the drive volumes 20 and 27.
  • the control valves 17 and 21 are not actuated, so that their 1 position is maintained and the steam control valve 2 remains closed.
  • the path measuring device 11 delivers path-dependent signals into the electronic control arrangement 58, where they are evaluated and compared with a predetermined target value. This setpoint is specified by a higher-level system control system. In accordance with the result of this target / actual comparison, the excitation of the electromagnets 56 and 60 is changed by the electronic control arrangement 58, as a result of which the position of the controllable control valves 17 and 21 is also changed accordingly.
  • the orifice 14 limits the opening time of the actuator 1, so that in the actuator 1 about fast moving and decelerating masses no mechanical defects can occur. Furthermore, this opening time limitation has a positive effect on the operating behavior of the turbine, which is not subjected to sudden loads with hot steam.
  • the main piston 6 is pressed upward by the oil fed into the drive volume 7, at the same time the oil in the buffer volume 8 flows through the line 31 into the outlet.
  • the opening movement of the actuator 1 is comparatively slow, but the closing must be done very quickly for safety reasons.
  • the oil flows from the drive volume 7 through the control valve 21, the line 50 and the upper part of the line 31 directly into the buffer volume 8. In this way, the oil can be discharged in the shortest possible way and thus very quickly to remove the drive volume 7, whereby an advantageously high dynamic of the actuator 1 is achieved in the closing direction.
  • the embodiment according to FIG. 2 enables an even more sensitive and rapid approximation to the specified setpoint, since the signals from the path measuring devices 65, 66 are additionally processed in the electronic control arrangement 58, which enables the setpoint of the drive position to be reached more quickly and more precisely.
  • the mode of operation of this arrangement is otherwise the same as for the arrangement according to FIG. 1.
  • the embodiment according to FIG. 3 also works similarly to the embodiment according to FIG. 1.
  • the pressure build-up in the drive volumes 27 and 20 is achieved here with the aid of only one proportional pressure valve 29, so that both drive volumes 27 and 20 are pressurized simultaneously and identically will.
  • Any settings for the response behavior of the control valves 17 and 21 can be made here when the system is started up using the adjustable preload force of the springs 42 and 51 are carried out, so that here, despite identical pressurization, different response times can be set corresponding to the respective operating tasks of the control valves 17 and 21. With a comparatively low effort, this simplified design can cover a comparatively large range of requirements in an economically justifiable manner.
  • this drive for a steam control valve 2 is suitable for actuation by high oil pressures, namely pressures of up to 200 bar and higher are possible.
  • high oil pressures namely pressures of up to 200 bar and higher are possible.
  • These high pressures do not negatively influence the operational safety and the availability of the drive, since seat valves are provided at all sealing points where these high pressures occur, the operating behavior of which is not impaired by any oil resinification, in particular these are the proportional pressure valves 29 and 34 and the seat valves 40 and 52 of the control valves 17 and 21.
  • the dynamic gain of the arrangement achieved by the high actuation pressure can therefore be used advantageously and in full to improve the control behavior of the arrangement.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Turbines (AREA)
  • Temperature-Responsive Valves (AREA)
  • Servomotors (AREA)
  • Fluid-Driven Valves (AREA)

Claims (10)

  1. Commande pour une servo-soupape à vapeur (2) avec un dispositif de vannes-pilotes pour la régulation de la pression de commande d'un servomoteur (1), dans laquelle le dispositif de vannes-pilotes comporte au moins deux vannes-pilotes (17, 21) réglables avec chacune une première position de passage à section réglable et une position de fermeture, et où les au moins deux vannes-pilotes (17, 21) sont soumises à la pression par l'intermédiaire d'au moins une soupape de régulation pilote, caractérisée en ce que
    - chacune des au moins deux vannes-pilotes (17, 21) présente en outre une deuxième position de passage à section constante; et en ce que
    - un point d'étanchéité effectif dans la position de fermeture des vannes-pilotes est constitué par une soupape à siège (40, 52).
  2. Commande suivant la revendication 1, caractérisée en ce que
    - la position de passage à section réglable présente la même caractéristique de régulation dans chacune des au moins deux vannes-pilotes (17, 21); et en ce que
    - cette caractéristique de régulation est active en même temps ou avec un décalage temporel dans les au moins deux vannes-pilotes (17, 21).
  3. Commande suivant la revendication 1, caractérisée en ce que
       - la position de passage à section réglable présente une caractéristique de régulation différente dans chacune des au moins deux vannes-pilotes (17, 21).
  4. Commande suivant la revendication 1, caractérisée en ce que
       - les au moins deux vannes-pilotes (17, 21) sont soumises à la pression chacune par l'intermédiaire d'au moins une soupape de régulation pilote.
  5. Commande suivant l'une des revendications 1 à 4, caractérisée en ce que
       - la au moins une soupape de régulation pilote est actionnée de manière appropriée par un dispositif de régulation électronique (58) en fonction d'une position mesurée du servomoteur (1) et d'une valeur de consigne prédéterminée de cette position.
  6. Commande suivant la revendication 5, caractérisée en ce que
       - il est prévu une soupape de refoulement proportionnelle (29, 34) ou une servo-soupape en guise d'au moins une soupape de régulation pilote.
  7. Commande suivant la revendication 6, caractérisée en ce que
       - la soupape de refoulement proportionnelle (29, 34) est constituée par une soupape à siège.
  8. commande suivant la revendication 5, caractérisée en ce que
    - les au moins deux vannes-pilotes (17, 21) sont chacune pourvues d'un dispositif de mesure de déplacement (65, 66); et en ce que
    - des signaux émis par au moins un dispositif de mesure de déplacement (65, 66) sont introduits dans le dispositif de régulation électronique (58) en vue d'un traitement ultérieur.
  9. Commande suivant la revendication 1, caractérisée en ce que
       - une sortie (41) de la première vanne-pilote (17) est raccordée par une canalisation (46) à la fois à un raccord (47) qui conduit dans un volume de commande (7) du servomoteur (1) et aussi à une entrée (48) de la seconde vanne-pilote (21).
  10. Commande suivant la revendication 1, caractérisée en ce que
       - dans la position Fail-Save, la position de fermeture de la première vanne-pilote (17) correspond avec la position de passage à section constante de la seconde vanne-pilote (21).
EP91104112A 1990-04-09 1991-03-16 Système d'actionnement pour une vanne de régulation de vapeur Revoked EP0451543B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1204/90A CH681380A5 (fr) 1990-04-09 1990-04-09
CH1204/90 1990-04-09

Publications (2)

Publication Number Publication Date
EP0451543A1 EP0451543A1 (fr) 1991-10-16
EP0451543B1 true EP0451543B1 (fr) 1994-07-13

Family

ID=4204939

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91104112A Revoked EP0451543B1 (fr) 1990-04-09 1991-03-16 Système d'actionnement pour une vanne de régulation de vapeur

Country Status (8)

Country Link
US (1) US5095804A (fr)
EP (1) EP0451543B1 (fr)
JP (1) JPH04224303A (fr)
AT (1) ATE108512T1 (fr)
CH (1) CH681380A5 (fr)
DE (1) DE59102144D1 (fr)
DK (1) DK0451543T3 (fr)
ES (1) ES2058962T3 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101871840A (zh) * 2010-07-12 2010-10-27 山东电力研究院 汽轮机高压调门流量特性在线测试方法
CN110753795A (zh) * 2017-07-03 2020-02-04 列奥纳多股份公司 用于控制液压回路的安全阀和方法

Families Citing this family (10)

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Publication number Priority date Publication date Assignee Title
DE4037524A1 (de) * 1990-11-26 1992-05-27 Leybold Ag Lecksuchgeraet
DE59203461D1 (de) * 1991-11-04 1995-10-05 Asea Brown Boveri Speiseschaltung für eine Zweirohr-Hydraulik.
DE4244304A1 (de) * 1992-12-28 1994-06-30 Asea Brown Boveri Betätigungsvorrichtung für einen hydraulischen Stellantrieb mit druckproportionalem Stellsignal
GB9421149D0 (en) * 1994-10-20 1994-12-07 Smiths Industries Plc Hydraulic systems
US5568759A (en) * 1995-06-07 1996-10-29 Caterpillar Inc. Hydraulic circuit having dual electrohydraulic control valves
DE19535691C1 (de) * 1995-09-26 1997-01-23 Rothenberger Werkzeuge Masch Hydraulisch angetriebenes Handwerkzeug
JP4369292B2 (ja) * 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 緊急遮断弁装置
CN103438040A (zh) * 2013-08-21 2013-12-11 上海汇益控制系统股份有限公司 高压调节阀的液压控制装置
DE102017131004A1 (de) * 2017-12-21 2019-06-27 Moog Gmbh Stellantrieb mit hydraulischem Abflussverstärker
FR3143072A1 (fr) * 2022-12-13 2024-06-14 Safran Power Units Actionneur, turbomachine et aéronef comprenant un tel actionneur, et procédé d’actionnement correspondant

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US3620129A (en) * 1970-07-15 1971-11-16 Gen Signal Corp Hydraulic power circuit with emergency lowering provisions
US4401009A (en) * 1972-11-08 1983-08-30 Control Concepts, Inc. Closed center programmed valve system with load sense
US4276810A (en) * 1972-11-08 1981-07-07 Control Concepts, Inc. Programmed valve system used for positioning control
SE372055B (fr) * 1973-03-23 1974-12-09 Stal Laval Turbin Ab
US4165613A (en) * 1978-03-27 1979-08-28 Koehring Company Control apparatus for a plurality of simultaneously actuatable fluid motors
US4275691A (en) * 1979-02-05 1981-06-30 Wolff George D Electromechanical precision governor for internal combustion engines
DE3140266A1 (de) * 1981-10-10 1983-04-28 Mannesmann Rexroth GmbH, 8770 Lohr "vorrichtung zum steuern eines hydromotors"
DE3201546C2 (de) * 1982-01-20 1986-03-27 Mannesmann Rexroth GmbH, 8770 Lohr Vorrichtung zum Steuern eines Hydromotors
DE3469777D1 (en) * 1983-05-30 1988-04-14 Bbc Brown Boveri & Cie Electro-hydraulic actuator for turbine valves
JPS6213204U (fr) * 1985-07-10 1987-01-27
US4741247A (en) * 1986-09-17 1988-05-03 Rexa Corporation Pneumatic actuator apparatus
DE3804744A1 (de) * 1988-02-16 1989-08-24 Danfoss As Steuereinrichtung fuer einen hydraulischen stellmotor

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101871840A (zh) * 2010-07-12 2010-10-27 山东电力研究院 汽轮机高压调门流量特性在线测试方法
CN110753795A (zh) * 2017-07-03 2020-02-04 列奥纳多股份公司 用于控制液压回路的安全阀和方法
CN110753795B (zh) * 2017-07-03 2021-11-30 列奥纳多股份公司 用于控制液压回路的安全阀和方法

Also Published As

Publication number Publication date
JPH04224303A (ja) 1992-08-13
DE59102144D1 (de) 1994-08-18
EP0451543A1 (fr) 1991-10-16
DK0451543T3 (da) 1994-10-31
CH681380A5 (fr) 1993-03-15
ES2058962T3 (es) 1994-11-01
ATE108512T1 (de) 1994-07-15
US5095804A (en) 1992-03-17

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