EP0419946B1 - Moteur pour une vanne - Google Patents

Moteur pour une vanne Download PDF

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Publication number
EP0419946B1
EP0419946B1 EP90117575A EP90117575A EP0419946B1 EP 0419946 B1 EP0419946 B1 EP 0419946B1 EP 90117575 A EP90117575 A EP 90117575A EP 90117575 A EP90117575 A EP 90117575A EP 0419946 B1 EP0419946 B1 EP 0419946B1
Authority
EP
European Patent Office
Prior art keywords
valve
control valve
control
pilot control
actuating drive
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
EP90117575A
Other languages
German (de)
English (en)
Other versions
EP0419946A1 (fr
Inventor
Heinz Frey
Kamil Prochazka
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ABB Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Asea Brown Boveri Ltd
Priority to AT90117575T priority Critical patent/ATE103035T1/de
Publication of EP0419946A1 publication Critical patent/EP0419946A1/fr
Application granted granted Critical
Publication of EP0419946B1 publication Critical patent/EP0419946B1/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
    • 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 invention relates to an actuator for a control valve according to the preamble of patent claim 1.
  • the main piston of this actuator is connected via a linkage to a control orifice which interacts with a pilot piston arrangement and regulates the flow of oil to the main piston.
  • a control orifice which interacts with a pilot piston arrangement and regulates the flow of oil to the main piston.
  • This can only be achieved by a complex device integrated in the linkage, such as scenes or cams with a corresponding mechanism.
  • the stroke of the actuator is usually monitored during operation, which is only possible here using a comparatively complex measuring device.
  • the main piston always runs after the piston of the pilot piston arrangement, so that additional measures generally have to be taken in order to avoid overshooting of the main piston. It also has the disadvantage that the actuator function cannot be directly secured by a safety oil circuit.
  • the invention seeks to remedy this.
  • the invention as characterized in the claims, solves the problem of creating an actuator for a control valve which has a higher dynamic range during operation.
  • the single figure shows a schematic representation of an actuator according to the invention.
  • the figure shows an actuator 1, which actuates a control valve 2, which can open and close a schematically illustrated superheated steam line 2a.
  • the control valve 2 is connected to a main piston 4 via a rod 3.
  • a drive volume 5 charged with oil pressure.
  • a schematically indicated master cylinder 7 includes the spring 6, the master piston 4 and the drive volume 5.
  • On the side of the spring 6, a further rod 8 is connected to the main piston 4. This rod 8 penetrates, just like the rod 3, the master cylinder 7. The construction of these pressure-tight penetrations will not be described here.
  • the rod 8 is guided by a guide 9, it is articulated to a rocker 11 via an articulated intermediate piece 10.
  • the rocker 11 is rotatably mounted in an indicated fixed bearing 12.
  • the other end of the rocker 11 is articulated to a rod 13 which interacts with a control panel 14.
  • the rod 13 is provided in the upper region with a part, not shown, which, like the intermediate piece 10 between the rod 8 and the rocker 11, implements the rotary movement of the rocker 1 in a straight line movement of the rods 13 and 8 facilitated.
  • the assembly consisting of the rod 8, the intermediate piece 10, the rocker 11, the bearing 12 and the rod 13 is referred to as the linkage 15.
  • this linkage 15 which is shown in a greatly simplified manner, non-linear links such as, for example, cam disks or link controls can also be provided.
  • the control orifice 14 has a schematically indicated closure piece 16, which is rigidly connected to a piston 17 of a pilot piston arrangement 18.
  • the pilot piston arrangement 18 has an actuating volume 19 above which the piston 17 is subjected to oil pressure and a spring 20 which is provided below the piston 17 and acts thereon.
  • the position of the piston 17 is controlled by a displacement measuring device 21 rigidly connected to it.
  • path-proportional electrical signals emitted by the path measuring device 21 are fed into an electronic controller 31.
  • the controller 31 is, as indicated by a dashed line of action 32, in operative connection with a proportional directional control valve 33.
  • This operative connection comprises, on the one hand, the electromagnetic actuation of the proportional directional control valve 33, which is controlled by the electronic controller 31 according to certain predetermined criteria, and, on the other hand, the path-proportional electrical signals fed back into the controller 31 of a position measuring device 34, which monitors the position of the proportional directional control valve 33.
  • a defined starting position of the proportional directional valve 33 is achieved with the aid of a spring, not shown.
  • the proportional directional control valve 33 also has an additional stroke feedback, not shown, which, together with an electronic position control, also not shown, achieves a proportional control behavior of this proportional directional control valve 33, namely an oil flow rate is set proportional to an electrical signal acting on it.
  • Oil is fed in under pressure through a line 40, and the necessary oil pressure is generated by a pump (not shown).
  • the flow rate of the oil is regulated by an orifice 41 arranged in the line 40.
  • the aperture 41 can either have an opening with a constant cross section or an opening with a controllable cross section.
  • the oil flows into the drive volume 5 and from there, as indicated schematically by the branching line 42, to the control orifice 14, through this further into a line 43, which leads to a drain device, not shown. From this drain device, the oil continues through the aforementioned pump back into line 40.
  • a line 44 branches off with an orifice 44 a, which leads to an inlet 45 of the proportional directional valve 33.
  • An outlet 46 of the proportional directional control valve 33 is connected by a line 47 to the actuating volume 19 of the pilot piston arrangement 18.
  • a line 48 branches off from this line 47 and opens into line 43.
  • a line 50 leads from a further outlet 49 of the proportional directional valve 33, which also opens into line 43.
  • the proportional directional control valve 33 is advantageously arranged in the immediate vicinity of the pilot piston arrangement 18 or flanged together to form a monolithic assembly, as a result of which the line 47 and thus the line volume to be filled with oil are small.
  • the dynamics of the control system are greatly increased by the elimination of pulse lines. All lines that are pressurized with oil pressure are designed with the smallest possible longitudinal extension in order to reduce line volumes and thereby increase the dynamics of the actuator.
  • a safety valve 60 which is designed as a plate valve and has an actuating volume 61 is used here.
  • the safety valve 60 is usually closed, since the actuating volume 61 is so strongly acted upon by a line 62 with the pressure of the safety oil from a safety oil circuit, not shown, that a spring 63 acting in the opening direction of the safety valve cannot relax.
  • the line 48 is also made as short as possible.
  • the proportional directional control valve 33 is switched in such a way that oil can flow out of the actuating volume 19 of the pilot piston arrangement 18 through the lines 47 and 50 into the line 43 and through this into the drain device.
  • the result of this is that the spring 20 can push the piston 17 and with it the closure piece 16 of the control orifice 14 upward, as a result of which the flow cross-section of the control orifice 14 is enlarged.
  • the orifice 41 limits the flow rate of the oil, but since more oil can now flow out through the control orifice 14, the oil pressure in the drive volume 5 drops and the spring 6 presses the main piston 4 down and the control valve 2 is moved in the closing direction.
  • the electronic controller 31 determines on the basis of the incoming path-proportional signals coming from the displacement measuring device 21 that the desired target position of the control valve 2 has been reached. Any non-linearities in the closing behavior of the control valve 2 are compensated in the controller 31. These non-linearities are entered into the controller 31 when this actuator 1 is started up, and any necessary fine adjustments can also be made via an entry into the controller 31.
  • One and the same type of controller can therefore be used for a wide variety of control valves, since only corresponding programming is necessary to adapt the controller.
  • any closing and opening characteristics of the control valve 2 can be set using the controller 31. In this way, complex mechanical changes to the linkage 15 can be avoided that would otherwise be necessary to change the drive characteristics of the actuator 1.
  • the proportional directional control valve 33 is switched over by a command from the controller 31, specifically in such a way that the circuit diagram shown at the top of this valve applies.
  • the inlet 45 is connected to the outlet 46, so that oil, the quantity of which is controlled by the proportional directional control valve 33, can flow through the lines 44 and 47 into the actuating volume 19 of the pilot piston arrangement 18 and can increase the oil pressure there, since through the Line 48 does not drain any oil.
  • the opening speed of the pilot piston arrangement 18 is limited by the aperture 44a.
  • the pilot piston arrangement 18 closes or reduces the flow cross-section of the control orifice 14, so that, fed by the line 40, the oil pressure in the drive volume 5 rises, as a result of which the main piston 4 is moved upward and at the same time the control valve 2 is moved in the opening direction.
  • the controller 31 recognizes this and controls the proportional directional control valve 33, so that no additional oil gets into the actuating volume 19.
  • control valve 2 The function of the control valve 2 must be checked at regular intervals in order to be sure that it can also carry out its closing movement at any time in the event of a fault.
  • an additional oil pressure line had to be led into the pilot piston arrangement 18 for this purpose, so that it could be actuated against the pressure prevailing in the actuating volume 19.
  • the piston 17 was then moved upward, the control orifice 14 was opened, the pressure from the drive volume 5 was able to escape via the control orifice 14 and the control valve 2 carried out a closing movement that was independent of the rest of the control system.
  • This additional oil pressure line had to be equipped with valves and securely sealed off from the rest of the control system in order to avoid unwanted, dangerous actuations of the pilot piston arrangement 18. This elaborate solution is no longer required, since this control can be initiated directly via the controller 31 by corresponding electrical control of the proportional directional valve 33.
  • the safety valve 60 opens immediately when the pressure of the safety oil in the line 62 drops.
  • the oil from the actuating volume 19 of the pilot piston arrangement 18 flows very quickly through the line 48 and the actuator 1 closes the control valve 2 immediately. This closing takes place even in the event of a power failure, since the springs 63, 20 and 6 ensure that the switch-off position is safely reached even without an additional one Ensure energy. In this way, a safe final state of the actuator 1 is always achieved; unstable operating states cannot occur.

Claims (5)

  1. Servocommande (1) pour une soupape de régulation (2) avec un piston principal (4) actionnable par une pression d'huile et avec une commande pilote activement reliée au piston principal (4) par une tringlerie (15), commande pilote qui présente au moins un diaphragme de régulation (14) régulant la pression d'huile au piston principal (4) et au moins un dispositif à piston de commande pilote (18) actionné par voie hydraulique, dans laquelle ledit au moins un dispositif à piston de commande pilote (18) est constitué de telle sorte qu'il puisse être actionné par l'intermédiaire d'au moins une vanne électrohydraulique, caractérisée en ce que:
    - audit au moins un dispositif à piston de commande pilote (18) et à ladite au moins une vanne électrohydraulique, il est prévu un dispositif propre de mesure de trajet (21, 34), émettant un signal électrique; en ce que
    - ces signaux électriques sont introduits dans un régulateur électronique (31) et y sont comparés avec une valeur de consigne; et en ce que
    - le régulateur électronique (31) applique une correction à la vanne électrohydraulique, en cas d'écarts avec la valeur de consigne.
  2. Servocommande suivant la revendication 1, caractérisée en ce que
    - ladite au moins une vanne électrohydraulique est constituée par un distributeur proportionnel (33).
  3. Servocommande suivant la revendication 1, caractérisée en ce que
    - le distributeur proportionnel (33) est combiné au dispositif à piston de commande pilote (18) en une unité monolithique.
  4. Servocommande suivant la revendication 1, caractérisée en ce que
    - des défauts de linéarité de la soupape de régulation (2) sont compensés par des éléments non linéaires dans la tringlerie (15) ou par l'introduction de la caractéristique de la soupape dans le régulateur électronique (31) ou par une combinaison de ces deux mesures.
  5. Servocommande suivant l'une ou l'autre des revendications précédentes, caractérisée en ce que
    - en cas de panne, la fermeture de la soupape de régulation (2) est assurée par une soupape de sécurité (60).
EP90117575A 1989-09-28 1990-09-12 Moteur pour une vanne Expired - Lifetime EP0419946B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90117575T ATE103035T1 (de) 1989-09-28 1990-09-12 Stellantrieb.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH3518/89 1989-09-28
CH3518/89A CH678968A5 (fr) 1989-09-28 1989-09-28

Publications (2)

Publication Number Publication Date
EP0419946A1 EP0419946A1 (fr) 1991-04-03
EP0419946B1 true EP0419946B1 (fr) 1994-03-16

Family

ID=4257735

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90117575A Expired - Lifetime EP0419946B1 (fr) 1989-09-28 1990-09-12 Moteur pour une vanne

Country Status (7)

Country Link
US (1) US5193779A (fr)
EP (1) EP0419946B1 (fr)
JP (1) JP2974749B2 (fr)
AT (1) ATE103035T1 (fr)
CH (1) CH678968A5 (fr)
DE (1) DE59005002D1 (fr)
ES (1) ES2053042T3 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007120679A (ja) * 2005-10-28 2007-05-17 Sun Wave Ind Co Ltd 板材の接合構造
US8290631B2 (en) * 2009-03-12 2012-10-16 Emerson Process Management Power & Water Solutions, Inc. Methods and apparatus to arbitrate valve position sensor redundancy
CN106801629B (zh) * 2017-03-07 2019-04-12 北京博力威格智能传控设备有限公司 一种汽轮机用速关阀油动机装置
US20220145774A1 (en) * 2019-03-27 2022-05-12 Salvatore Shifrin Self contained hydraulic lock apparatus

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE474923C (de) * 1929-04-13 J A Maffei A G Regelungseinrichtung an Dampfturbinen
BE464678A (fr) * 1945-05-24
DE1601759B2 (de) * 1967-07-19 1972-02-24 Siemens AG, 1000 Berlin u 8000 München Hydraulisch betaetigter stellantrieb mit kraftkolben vorzugs weise zur betaetigung von ventilen fuer grosse mengenstroeme
SE372055B (fr) * 1973-03-23 1974-12-09 Stal Laval Turbin Ab
JPS6014201B2 (ja) * 1975-12-01 1985-04-12 黒田精工株式会社 空圧デイジタルシリンダー装置
CH624187A5 (fr) * 1977-09-29 1981-07-15 Bbc Brown Boveri & Cie
US4335867A (en) * 1977-10-06 1982-06-22 Bihlmaier John A Pneumatic-hydraulic actuator system
DE2835771A1 (de) * 1978-08-16 1980-02-28 Schwelm & Towler Hydraulics Anordnung zur aussteuerung eines cartridgeelementes
US4215844A (en) * 1978-08-28 1980-08-05 The Babcock & Wilcox Company Valve actuator system
JPS58174701A (ja) * 1982-04-07 1983-10-13 Diesel Kiki Co Ltd 油圧アクチユエ−タ装置
DE3309441A1 (de) * 1983-03-16 1984-09-27 Kraftwerk Union AG, 4330 Mülheim Turbinen-regel- und steuersystem
EP0127027B1 (fr) * 1983-05-30 1988-03-09 BBC Brown Boveri AG Servomoteur électrohydraulique pour soupapes de turbines
CH666132A5 (de) * 1984-07-20 1988-06-30 Bbc Brown Boveri & Cie Einrichtung zur ueberwachung von physikalischen groessen an anlagen.
US4807518A (en) * 1986-10-14 1989-02-28 Cincinnati Milacron Inc. Counterbalance mechanism for vertically movable means
EP0322503A3 (fr) * 1987-12-29 1991-09-25 Daihatsu Diesel Mfg. Co., Ltd. Appareil à fluide
US4901625A (en) * 1989-01-03 1990-02-20 Increcyl, Inc. Apparatus and method for positioning equipment

Also Published As

Publication number Publication date
ES2053042T3 (es) 1994-07-16
US5193779A (en) 1993-03-16
EP0419946A1 (fr) 1991-04-03
JPH03121203A (ja) 1991-05-23
DE59005002D1 (de) 1994-04-21
CH678968A5 (fr) 1991-11-29
JP2974749B2 (ja) 1999-11-10
ATE103035T1 (de) 1994-04-15

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