EP0127027B1 - Servomoteur électrohydraulique pour soupapes de turbines - Google Patents

Servomoteur électrohydraulique pour soupapes de turbines Download PDF

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Publication number
EP0127027B1
EP0127027B1 EP84105238A EP84105238A EP0127027B1 EP 0127027 B1 EP0127027 B1 EP 0127027B1 EP 84105238 A EP84105238 A EP 84105238A EP 84105238 A EP84105238 A EP 84105238A EP 0127027 B1 EP0127027 B1 EP 0127027B1
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EP
European Patent Office
Prior art keywords
hydraulic
valve
valves
electro
control 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.)
Expired
Application number
EP84105238A
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German (de)
English (en)
Other versions
EP0127027A1 (fr
Inventor
Jaroslav Masek
Franz Suter
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.)
BBC Brown Boveri AG Switzerland
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BBC Brown Boveri AG Switzerland
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
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Application filed by BBC Brown Boveri AG Switzerland filed Critical BBC Brown Boveri AG Switzerland
Publication of EP0127027A1 publication Critical patent/EP0127027A1/fr
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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
    • 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
    • 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
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
    • F01D17/145—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path by means of valves, e.g. for steam turbines
    • 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
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87917—Flow path with serial valves and/or closures
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87917—Flow path with serial valves and/or closures
    • Y10T137/87981—Common actuator

Definitions

  • the invention relates to an electro-hydraulic actuator for turbine valves according to the preamble of the claim.
  • the actuators of the individual turbine valves are always supplied with hydraulic energy via a central hydraulic supply system, which comprises a central hydraulic fluid reservoir and usually several fluid pumps working against hydraulic pressure accumulators. Accordingly, at least two pipes are required for connecting an actuator to the central hydraulic supply system, with one pipe taking care of supplying the actuator with pressurized hydraulic fluid, while the other pipeline feeds the hydraulic fluid that flows when the hydraulic components are relieved into the central hydraulic fluid reservoir leads back.
  • a central hydraulic supply system which comprises a central hydraulic fluid reservoir and usually several fluid pumps working against hydraulic pressure accumulators.
  • at least two pipes are required for connecting an actuator to the central hydraulic supply system, with one pipe taking care of supplying the actuator with pressurized hydraulic fluid, while the other pipeline feeds the hydraulic fluid that flows when the hydraulic components are relieved into the central hydraulic fluid reservoir leads back.
  • the valve housing of the quick-closing valve forms part of the control valve housing, which is arranged across the turbine.
  • the hydraulic drive part of the quick-closing valve is a servo motor that is opened with oil from a control oil system and closed with spring force.
  • the control valve device has, for example, three or four control valves which open in succession, as a result of which the throttling of the entire device is kept low.
  • the individual valves are each actuated by a rotary servo motor, which is influenced by an electro-hydraulic converter, via a rotary shaft with a cam and a roller lever.
  • EP-A-0 040 732 and EP-A-0 040 737 avoid the disadvantages described above, since the hydraulic supply lines previously required and the effort associated with these lines can be dispensed with by integrating the hydraulic supply systems in the actuator.
  • the object of the invention is to remedy the aforementioned disadvantages and to provide an electrohydraulic actuator for a quick-closing valve and a control valve which on the one hand meets the high requirements in terms of actuating force and actuating speed and on the other hand avoids the problems associated with the transmission of hydraulic energy.
  • the electrohydraulic actuator for a quick-closing valve and a control valve proposed according to the invention to achieve the stated object is characterized in that the drives of the valves are structurally identical, that the compact units consisting of the valves and their associated drive are directly combined with the hydraulic supply, and that the hydraulic supply contains a volumetrically regulating oil delivery unit with an auxiliary pump for controlling the quick-closing valve, a variable pump and associated variable cylinder for controlling the control valve, and an electro-hydraulic valve for controlling the hydraulic flows of the pumps.
  • Another advantage of the invention can be seen in the fact that a hydraulic supply operates one control and one quick-closing valve. Because the hydraulic supply is no longer conditioned in terms of space, it can be made more robust, simpler and cheaper.
  • the hydraulic supply includes a volumetrically controlled oil delivery unit, which supplies the quantity for the actuation of the control valve.
  • This oil delivery unit also includes an auxiliary pump, which supplies the hydraulic quantity to act on the quick-closing valve as well as for the electro-hydraulic valve and for the adjustment cylinder of the adjustment unit of the pump.
  • the energy consumption of the unit is minimal because the variable displacement pump only supplies the quantity and pressure required by the control valve.
  • Fig. 1 electrohydraulic actuator for turbine valves for control and quick-closing valve.
  • the electrohydraulic actuator for turbine valves essentially consists of a hydraulic supply 1, an oil delivery unit 2 and two identical drives 3, 4, which are responsible for controlling the quick-closing valve 29 and the control valve 30.
  • the auxiliary pump 15 and adjusting pump 16 integrated in the oil delivery unit 2 deliver oil from the hydraulic tank 6 via the lines 32 and. 33.
  • the auxiliary pump 15 supplies the electro-hydraulic valve 10 with oil, a filter 8 being installed as an intermediate.
  • the drive 4 is also supplied with oil via the throttle 9 and line 34, as a result of which the quick-closing valve 29 opens.
  • the oil flows through the throttle 22a into the piston chamber of the adjusting cylinder 21a.
  • the spring 35a is compressed; the oil still present in the spring chamber can flow out to the tank 6 via the outlet 24.
  • the auxiliary pump 15 is secured against excess pressure by the pressure relief valve 7 and its outlet 24.
  • the control valve 30 While the quick-closing valve 29 opens completely, the control valve 30 must have a regulating effect on the amount of steam flowing through the steam line 26 to the turbine.
  • the variable displacement pump 16 in turn supplies the drive 3 with oil via the line 37.
  • the dynamics of the opening of the control valve 30 do not differ from that of the quick-closing valve 29, i.e. the piston chamber of the adjusting cylinder 21 is acted upon by the throttle 22, whereupon the spring 35 is compressed and the residual oil remaining therein can flow back to the tank 6 via the outlet 24.
  • the degree of opening of the control valve 30 is signaled by an electrical setpoint 27 to the electro-hydraulic valve 10.
  • the adjustment quantity entered on the adjustment cylinder 18 causes a change in the delivery quantity of the adjustment pump 16, whereby oil is additionally applied to the piston chamber of the adjustment cylinder 21 and the adjustment valve 30 accordingly assumes a new opening position.
  • the desired degree of opening of the control valve 30 is maintained by continuously comparing the feedback signal 28 from the feedback sensor 5 with the setpoint 27 in the comparator 36. A resulting deviation between the setpoint and actual value is signaled to the electro-hydraulic valve 10. If the control valve 30 opens too large, the control cylinder 18 closes by means of spring force.
  • the variable displacement pump 16 now delivers less accordingly; the excess oil from the actuating cylinder 18 flows to the electro-hydraulic valve 10 and from there via the outlet 24 back to the tank.
  • variable displacement pump 16 Securing the variable displacement pump 16 against excess pressure is taken over by the pressure limiting valve 11 and its outlet 24.
  • the control valve 30 When the control valve 30 is completely open, the maximum pressure defined by the pressure relief valve 11 is set, the set pressure of the pressure relief valve 11 being at least the sum of the pressure force and the spring force of the adjustment cylinder 21.
  • the control valve spindle is therefore constantly loaded.
  • the directional control valve 13 In order to prevent this constant heavy load, the directional control valve 13 is switched and the pressure is reduced by the limit switch on the control valve 30, when the control valve 30 is in its fully open position, until it corresponds to the value defined in the pressure relief valve 14.
  • a filter 12 is installed in front of the directional control valve 13 in the outflow direction.
  • the outflow amplifier 19 switches on and opens. Via the bypass line 31, the oil under pressure in the piston chamber flows into the spring chamber of the adjusting cylinder 21 and from there via the outlet 24 back into the tank 6. This prevents the pump and lines from swallowing large amounts of oil during these load changes.
  • the throttles 23, 23a are provided so that the pumps 15, 16 can deliver a minimum amount of oil which is advantageous for their cooling during operation under constant load, which ensure this recirculation.
  • the two-way valves 20, 20a open, controlled by the electrical signals 38, 38a.
  • the drain amplifiers 19, 19a also open.
  • the oil can thus suddenly escape from the piston spaces via the bypass lines 31, 31a a into the spring spaces of the adjusting cylinders 21, 21a and flow out from here through the already opened two-way valves 20, 20a via 24.
  • Information aimed at closure is simultaneously brought in via the electrical setpoint 27.
  • the pump 16 is reduced to zero.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Turbines (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (1)

  1. Servomoteur électrohydraulique pour une soupape à fermeture rapide (29) et une servo-soupape (30) pour la régulation d'une turbine à vapeur, avec une alimentation hydraulique (1), dans lequel les commandes (4; 3) des deux soupapes (29; 30) sont rassemblées avec celles-ci en une unité compacte, caractérisé en ce que les commandes (4; 3) des soupapes (29; 30) sont de construction identique, en ce que les unités compactes se composant des soupapes (29; 30) et de leurs commandes respectives (4; 3) sont directement réunies à l'alimentation hydraulique (1) et en ce que l'alimentation hydraulique (1) comprend une unité de circulation d'huiie (2) à régulation volumétrique avec une pompe auxiliaire (15) pour la commande de la soupape à fermeture rapide (29), une pompe à cylindrée variable (16) et un cylindre variable (18) approprié pour la commande de la servo- soupape (30) ainsi qu'une soupape électrohydraulique (10) pour la commande des courants hydrauliques des pompes (15; 16).
EP84105238A 1983-05-30 1984-05-09 Servomoteur électrohydraulique pour soupapes de turbines Expired EP0127027B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH2955/83 1983-05-30
CH295583 1983-05-30

Publications (2)

Publication Number Publication Date
EP0127027A1 EP0127027A1 (fr) 1984-12-05
EP0127027B1 true EP0127027B1 (fr) 1988-03-09

Family

ID=4245402

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84105238A Expired EP0127027B1 (fr) 1983-05-30 1984-05-09 Servomoteur électrohydraulique pour soupapes de turbines

Country Status (7)

Country Link
US (1) US4589444A (fr)
EP (1) EP0127027B1 (fr)
JP (1) JPS59231108A (fr)
CS (1) CS244819B2 (fr)
DE (1) DE3469777D1 (fr)
PL (1) PL145034B1 (fr)
YU (1) YU43361B (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014226672B3 (de) * 2014-12-19 2015-12-24 Voith Patent Gmbh Stellantrieb für ein Regelventil, insbesondere Dampfturbinenregelventil und Verfahren zum Betreiben desselben

Families Citing this family (23)

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CH678968A5 (fr) * 1989-09-28 1991-11-29 Asea Brown Boveri
US5137253A (en) * 1989-12-01 1992-08-11 Asea Brown Boveri Ltd. Actuator
CH681380A5 (fr) * 1990-04-09 1993-03-15 Asea Brown Boveri
CH683017A5 (de) * 1990-06-18 1993-12-31 Asea Brown Boveri Elektrohydraulischer Stellantrieb.
US5269141A (en) * 1990-06-18 1993-12-14 Asea Brown Boveri Ltd. Hydraulic safety and regulating system
DE4320937A1 (de) * 1993-06-24 1995-01-05 Abb Management Ag Stellantrieb für ein Regelventil
DE19636746A1 (de) * 1996-09-10 1998-03-12 Siemens Ag Ventilkombination für eine Turbine, insbesondere eine Dampfturbine
DE10058560A1 (de) * 2000-11-24 2002-06-13 Voith Turbo Kg Elektrohydraulischer Stellantrieb
DE102004042891B3 (de) * 2004-08-31 2005-10-06 Hydac System Gmbh Sicherheitsschaltung für medienbetriebene Verbraucher und Verfahren zum Betrieb derselben
ITMI20082339A1 (it) * 2008-12-30 2010-06-30 Ansaldo Energia Spa Impianto per la produzione di energia elettrica
CN101629496B (zh) * 2009-07-30 2011-08-17 杭州和利时自动化有限公司 一种孤网运行汽轮机数字电液控制系统
CN102922771A (zh) * 2012-11-19 2013-02-13 无锡市京锡冶金液压机电有限公司 一种高速冲床负载控制双压力系统连接方法
CN102950804A (zh) * 2012-11-19 2013-03-06 无锡市京锡冶金液压机电有限公司 一种可实现快速换向的高速冲床液压系统连接方法
CN103511004B (zh) * 2013-09-17 2015-05-13 上海新力机器厂 闭式电液执行器及其组合
JP6352781B2 (ja) * 2014-11-26 2018-07-04 三菱日立パワーシステムズ株式会社 蒸気弁用の油圧駆動装置、組合せ蒸気弁及び蒸気タービン
DE102014226666B3 (de) * 2014-12-19 2015-12-24 Voith Patent Gmbh Stellantrieb für ein Regelventil, insbesondere Dampfturbinenregelventil und Verfahren zum Betreiben desselben
DE102016102387A1 (de) * 2015-07-31 2017-02-02 Voith Patent Gmbh Hydraulischer Antrieb zum Ausführen einer linearen Bewegung
DE102015221311A1 (de) 2015-10-30 2017-05-04 Siemens Aktiengesellschaft Turbine mit Schnellschluss- und Regelventilen
DE102017131004A1 (de) * 2017-12-21 2019-06-27 Moog Gmbh Stellantrieb mit hydraulischem Abflussverstärker
CN109404065B (zh) * 2018-10-12 2021-12-17 上海华电电力发展有限公司 防止主机汽门遮断电磁阀故障引起机组跳闸的控制方法
US20220145774A1 (en) * 2019-03-27 2022-05-12 Salvatore Shifrin Self contained hydraulic lock apparatus
JP7227845B2 (ja) * 2019-05-14 2023-02-22 株式会社東芝 蒸気弁駆動装置、蒸気弁装置および蒸気タービンプラント
CN110345113A (zh) * 2019-08-13 2019-10-18 国电浙江北仑第一发电有限公司 一种电站旁路控制油增压系统

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014226672B3 (de) * 2014-12-19 2015-12-24 Voith Patent Gmbh Stellantrieb für ein Regelventil, insbesondere Dampfturbinenregelventil und Verfahren zum Betreiben desselben
US10473128B2 (en) 2014-12-19 2019-11-12 Voith Patent Gmbh Actuating drive for a control valve, in particular steam turbine control valve and method for operating same

Also Published As

Publication number Publication date
US4589444A (en) 1986-05-20
JPH0472042B2 (fr) 1992-11-17
DE3469777D1 (en) 1988-04-14
YU85884A (en) 1987-12-31
CS394484A2 (en) 1985-08-15
JPS59231108A (ja) 1984-12-25
PL145034B1 (en) 1988-07-30
YU43361B (en) 1989-06-30
EP0127027A1 (fr) 1984-12-05
CS244819B2 (en) 1986-08-14
PL247906A1 (en) 1985-03-12

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