EP0127027A1 - Servomoteur électrohydraulique pour soupapes de turbines - Google Patents

Servomoteur électrohydraulique pour soupapes de turbines Download PDF

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Publication number
EP0127027A1
EP0127027A1 EP84105238A EP84105238A EP0127027A1 EP 0127027 A1 EP0127027 A1 EP 0127027A1 EP 84105238 A EP84105238 A EP 84105238A EP 84105238 A EP84105238 A EP 84105238A EP 0127027 A1 EP0127027 A1 EP 0127027A1
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EP
European Patent Office
Prior art keywords
valve
hydraulic
quick
hydraulic supply
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.)
Granted
Application number
EP84105238A
Other languages
German (de)
English (en)
Other versions
EP0127027B1 (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
Original Assignee
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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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=4245402&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0127027(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by BBC Brown Boveri AG Switzerland filed Critical BBC Brown Boveri AG Switzerland
Publication of EP0127027A1 publication Critical patent/EP0127027A1/fr
Application granted granted Critical
Publication of EP0127027B1 publication Critical patent/EP0127027B1/fr
Expired 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
    • 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, 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, 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 object of the invention is to eliminate the aforementioned disadvantages and an electro-hydraulic actuator for turbine valves, which on the one hand meets the high requirements with regard to actuating force and actuating speed and on the other hand avoids the problems associated with the transmission of hydraulic energy.
  • the electrohydraulic actuator for turbine valves proposed according to the invention to achieve the stated object is characterized in that at least one control valve and at least one quick-closing valve are assigned to each turbine inlet valve, the drives of the same design and integrated into a compact drive unit arranged on the valve housing, these drives being paired with connected directly to a hydraulic supply and are controlled by a vblumetrically controlled oil delivery unit integrated with the hydraulic supply.
  • Another advantage of the invention can be seen in the fact that a hydraulic supply operates one control valve 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 gel delivery unit, which supplies the quantity for the actuation of the control valve.
  • 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 adjusting cylinder of the adjusting 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.
  • 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 variable displacement pump 16 integrated in the oil delivery unit 2 deliver oil from the hydraulic tank 6 via the lines 32 and respectively. 33.
  • the auxiliary pump 15 supplies the electrohydraulic 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, whereupon 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 Oe1 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, whereupon oil is additionally applied to the piston chamber of the adjustment cylinder 21 and the control 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 transmitter 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 is 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.
  • the control valve 30 When the control valve 30 is completely open, the maximum defined by the pressure relief valve 11 is established Pressure, wherein the set pressure of the pressure relief valve 11 is at least the sum of the pressure force and the spring force of the adjusting cylinder 21.
  • the control valve spindle is therefore constantly loaded.
  • the directional control valve 13 In order to prevent this permanent heavy load, the directional control valve 13 is switched and the pressure is reduced by the limit switch on the control valve 30, in its fully open position, until the pressure 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 having to swallow large amounts of oil during these load changes. So that the pumps 15, 16 can deliver a minimum amount of oil which is advantageous for their cooling during operation under constant load, the throttles 23, 23a are provided, 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 in the spring spaces of the adjusting cylinders 21, 21a and flow out from here through the already opened two-way valves 20, 20a 24.
  • Information aimed at closing is simultaneously via the electrical setpoint 27 brought up. The delivery of the pumps 15, 16 drops 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)
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
CH295583 1983-05-30
CH2955/83 1983-05-30

Publications (2)

Publication Number Publication Date
EP0127027A1 true EP0127027A1 (fr) 1984-12-05
EP0127027B1 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 (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0419946A1 (fr) * 1989-09-28 1991-04-03 Asea Brown Boveri Ag Moteur pour une vanne
EP0430089A1 (fr) * 1989-12-01 1991-06-05 Asea Brown Boveri Ag Actuateur
EP0451543A1 (fr) * 1990-04-09 1991-10-16 Asea Brown Boveri Ag Système d'actionnement pour une vanne de régulation de vapeur
EP0462387A1 (fr) * 1990-06-18 1991-12-27 Asea Brown Boveri Ag Système hydraulique de contrôle et sécurité
US5269141A (en) * 1990-06-18 1993-12-14 Asea Brown Boveri Ltd. Hydraulic safety and regulating system
DE19636746A1 (de) * 1996-09-10 1998-03-12 Siemens Ag Ventilkombination für eine Turbine, insbesondere eine Dampfturbine
ITMI20082339A1 (it) * 2008-12-30 2010-06-30 Ansaldo Energia Spa Impianto per la produzione di energia elettrica
CN103511004A (zh) * 2013-09-17 2014-01-15 上海新力机器厂 闭式电液执行器及其组合
WO2016096222A1 (fr) * 2014-12-19 2016-06-23 Voith Patent Gmbh Mécanisme de commande pour une soupape de réglage, en particulier une soupape de réglage d'une turbine à vapeur, et son procédé de fonctionnement
WO2016096221A1 (fr) * 2014-12-19 2016-06-23 Voith Patent Gmbh Mécanisme de commande pour une soupape de réglage, en particulier une soupape de réglage d'une turbine à vapeur, et son procédé de fonctionnement
WO2017021080A1 (fr) * 2015-07-31 2017-02-09 Voith Patent Gmbh Entraînement hydraulique servant à l'exécution d'un mouvement linéaire
WO2017071912A1 (fr) * 2015-10-30 2017-05-04 Siemens Aktiengesellschaft Turbine munie de soupapes à fermeture rapide et de soupapes de régulation
CN109404065A (zh) * 2018-10-12 2019-03-01 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
CN111566357A (zh) * 2017-12-21 2020-08-21 穆格股份有限公司 带液压排流增益器的执行驱动装置

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4320937A1 (de) * 1993-06-24 1995-01-05 Abb Management Ag Stellantrieb für ein Regelventil
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
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
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
WO2020198599A1 (fr) * 2019-03-27 2020-10-01 Salvatore Shifrin Appareil de verrouillage hydraulique autonome
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
US20230383672A1 (en) * 2022-05-26 2023-11-30 General Electric Company System and method for hydraulically actuating main and bypass valves of a steam turbine

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3603083A (en) * 1970-02-16 1971-09-07 Laval Turbine Hydraulic actuator
FR2426174A1 (fr) * 1978-05-17 1979-12-14 Harnischfeger Corp Engin hydraulique de terrassement comportant des groupes moteurs electrohydrauliques autonomes
EP0040737A1 (fr) * 1980-05-22 1981-12-02 Kraftwerk Union Aktiengesellschaft Positionneur électro-hydraulique pour vanne de turbine
EP0040732A1 (fr) * 1980-05-22 1981-12-02 Kraftwerk Union Aktiengesellschaft Positionneur électro-hydraulique pour vanne de turbine à vapeur

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US2741262A (en) * 1950-11-24 1956-04-10 Exxon Research Engineering Co Apparatus for controlling and releasing pressure
FR2232226A5 (fr) * 1973-05-28 1974-12-27 Poclain Sa
FR2247112A5 (fr) * 1973-10-03 1975-05-02 Poclain Sa
FR2260013B1 (fr) * 1974-02-04 1976-10-08 Poclain Sa
US4147325A (en) * 1977-03-29 1979-04-03 Combustion Engineering, Inc. Hydraulic control assembly
US4247077A (en) * 1979-06-20 1981-01-27 Automatic Switch Company Slow-opening valve operated by a solenoid pump
US4294284A (en) * 1979-11-13 1981-10-13 Smith International, Inc. Fail-safe, non-pressure locking gate valve
US4368520A (en) * 1980-09-29 1983-01-11 Westinghouse Electric Corp. Steam turbine generator control system

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3603083A (en) * 1970-02-16 1971-09-07 Laval Turbine Hydraulic actuator
FR2426174A1 (fr) * 1978-05-17 1979-12-14 Harnischfeger Corp Engin hydraulique de terrassement comportant des groupes moteurs electrohydrauliques autonomes
EP0040737A1 (fr) * 1980-05-22 1981-12-02 Kraftwerk Union Aktiengesellschaft Positionneur électro-hydraulique pour vanne de turbine
EP0040732A1 (fr) * 1980-05-22 1981-12-02 Kraftwerk Union Aktiengesellschaft Positionneur électro-hydraulique pour vanne de turbine à vapeur

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
BROWN BOVERI REVIEW, Band 63, Nr. 6, Juni 1976, Seiten 354-359, Baden, CH; K. WIRZ: "The control of the industrial steam turbine" *
ESCHER WYSS MITTEILUNGEN, 1/1981 / 1/1982, Seiten 43-50, Winterthur, CH; M. SCHLEGEL u.a.: "Regelung von Kaplan- und Rohrturbinen mit elektrisch angetriebenen Steuerpumpen" *

Cited By (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH678968A5 (fr) * 1989-09-28 1991-11-29 Asea Brown Boveri
US5193779A (en) * 1989-09-28 1993-03-16 Asea Brown Boveri Ltd. Actuating drive
EP0419946A1 (fr) * 1989-09-28 1991-04-03 Asea Brown Boveri Ag Moteur pour une vanne
US5137253A (en) * 1989-12-01 1992-08-11 Asea Brown Boveri Ltd. Actuator
EP0430089A1 (fr) * 1989-12-01 1991-06-05 Asea Brown Boveri Ag Actuateur
US5095804A (en) * 1990-04-09 1992-03-17 Asea Brown Boveri Ltd. Drive for a steam servo valve
EP0451543A1 (fr) * 1990-04-09 1991-10-16 Asea Brown Boveri Ag Système d'actionnement pour une vanne de régulation de vapeur
CH681380A5 (fr) * 1990-04-09 1993-03-15 Asea Brown Boveri
EP0462387A1 (fr) * 1990-06-18 1991-12-27 Asea Brown Boveri Ag Système hydraulique de contrôle et sécurité
US5269141A (en) * 1990-06-18 1993-12-14 Asea Brown Boveri Ltd. Hydraulic safety and regulating system
CH683017A5 (de) * 1990-06-18 1993-12-31 Asea Brown Boveri Elektrohydraulischer Stellantrieb.
DE19636746A1 (de) * 1996-09-10 1998-03-12 Siemens Ag Ventilkombination für eine Turbine, insbesondere eine Dampfturbine
ITMI20082339A1 (it) * 2008-12-30 2010-06-30 Ansaldo Energia Spa Impianto per la produzione di energia elettrica
EP2204551A1 (fr) * 2008-12-30 2010-07-07 Ansaldo Energia S.p.A. Turbine à gaz pour la production d'énergie électrique
CN103511004A (zh) * 2013-09-17 2014-01-15 上海新力机器厂 闭式电液执行器及其组合
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
US10400799B2 (en) 2014-12-19 2019-09-03 Voith Patent Gmbh Actuating drive for a control valve, in particular a steam turbine control valve, and method for operating same
WO2016096222A1 (fr) * 2014-12-19 2016-06-23 Voith Patent Gmbh Mécanisme de commande pour une soupape de réglage, en particulier une soupape de réglage d'une turbine à vapeur, et son procédé de fonctionnement
WO2016096221A1 (fr) * 2014-12-19 2016-06-23 Voith Patent Gmbh Mécanisme de commande pour une soupape de réglage, en particulier une soupape de réglage d'une turbine à vapeur, et son procédé de fonctionnement
CN107109961B (zh) * 2014-12-19 2020-02-14 福伊特专利有限公司 用于调节阀、尤其蒸汽透平调节阀的伺服驱动装置和其运行方法
CN107109961A (zh) * 2014-12-19 2017-08-29 福伊特专利有限公司 用于调节阀、尤其蒸汽透平调节阀的伺服驱动装置和其运行方法
US10578227B2 (en) 2015-07-31 2020-03-03 Voith Patent Gmbh Hydraulic drive for executing a linear movement
WO2017021080A1 (fr) * 2015-07-31 2017-02-09 Voith Patent Gmbh Entraînement hydraulique servant à l'exécution d'un mouvement linéaire
WO2017071912A1 (fr) * 2015-10-30 2017-05-04 Siemens Aktiengesellschaft Turbine munie de soupapes à fermeture rapide et de soupapes de régulation
US10900375B2 (en) 2015-10-30 2021-01-26 Siemens Aktiengesellschaft Turbine with quick-closing valves and regulating valves
CN111566357A (zh) * 2017-12-21 2020-08-21 穆格股份有限公司 带液压排流增益器的执行驱动装置
CN111566357B (zh) * 2017-12-21 2022-06-17 穆格股份有限公司 带液压排流增益器的执行驱动装置
CN109404065A (zh) * 2018-10-12 2019-03-01 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

Also Published As

Publication number Publication date
YU85884A (en) 1987-12-31
US4589444A (en) 1986-05-20
PL145034B1 (en) 1988-07-30
YU43361B (en) 1989-06-30
DE3469777D1 (en) 1988-04-14
JPH0472042B2 (fr) 1992-11-17
CS244819B2 (en) 1986-08-14
CS394484A2 (en) 1985-08-15
JPS59231108A (ja) 1984-12-25
PL247906A1 (en) 1985-03-12
EP0127027B1 (fr) 1988-03-09

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