EP0462126A1 - Servomoteur pour soupapes de surete et de reglage. - Google Patents

Servomoteur pour soupapes de surete et de reglage.

Info

Publication number
EP0462126A1
EP0462126A1 EP90903765A EP90903765A EP0462126A1 EP 0462126 A1 EP0462126 A1 EP 0462126A1 EP 90903765 A EP90903765 A EP 90903765A EP 90903765 A EP90903765 A EP 90903765A EP 0462126 A1 EP0462126 A1 EP 0462126A1
Authority
EP
European Patent Office
Prior art keywords
spindle
safety
pressure
throttle body
brake
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
EP90903765A
Other languages
German (de)
English (en)
Other versions
EP0462126B1 (fr
Inventor
Hermann Doerr
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 EP0462126A1 publication Critical patent/EP0462126A1/fr
Application granted granted Critical
Publication of EP0462126B1 publication Critical patent/EP0462126B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F01D17/10—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
    • F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
    • 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
    • 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
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7758—Pilot or servo controlled
    • Y10T137/7761—Electrically actuated valve

Definitions

  • the invention relates to an actuator for safety and control valves of safety stations for metering energy flows in the form of gases, vapors or water, in particular in thermal or industrial power plants, according to the preamble of claim 1.
  • Safety valves with a positive direction of action The safety valves must open safely in the event of overpressure. If the systems downstream of the safety valves have to be protected against excess pressure, then one speaks of safety valves with a negative direction of action. The safety valves must close securely here.
  • Safety stations or the associated safety valves and actuators are to perform both tasks, namely - defined reduction or dosing of the energy flows - and protection of the system systems against overpressures. If these safety stations are steam valves in which the steam is also cooled by the supply of cooling water, then one speaks of safety steam forming stations.
  • the invention is based on the task of forming this that basically a safety station with positive or negative direction of action can be implemented.
  • the security of so-called bypass stations is to be increased, the actuating times are to be shortened, the connecting power of the actuators is to be reduced and finally a favorable price setting is to be achieved without loss of functionality.
  • IG 1 is an actuator for a safety valve with a positive direction of action, ie the safety valve opens when the response pressure is reached on the inflow side of the valve;
  • IG 2 in a representation corresponding to FIG. 1 shows an actuator for a safety valve with a negative direction of action, i.e. the safety valve closes when the response pressure is reached on its outflow side;
  • FIG. 1 in a representation corresponding to FIG. 1 and FIG. 2 shows an actuator for a safety valve which is also operated by the medium and which is constructed in principle in the same way as that according to FIG.
  • FIG. 4 schematically simplified a planetary gear, as is used in the actuators according to FIGS. 1-3; 5 shows the top view of the arrangement of the ring gear-planet gear-sun gear according to FIG. 4 and
  • FIG 6 shows a table for FIG 4 and 5, from which additional
  • FIG. 1 The function of the safety station with its own medium-operated safety function in the positive direction of action is shown in FIG. 1.
  • a steam valve with the housing 1 is flowed against the throttle body 3 (here, for example, a parabolic throttle body) via the inlet connection 2.
  • the steam exerts an axial force on the throttle body 3, the spindle 4 and the spindle nut 5, which is proportional to the effective throttle body cross section and the
  • Pressure difference between the inlet nozzle 2 and the outlet is 6 and acts in the up direction.
  • the axial force generated by the own medium (steam) is converted in the non-self-locking - in contrast to conventional spindle nuts - and rotatably mounted spindle nut 5 into a torque which is transmitted via the spindle nut housing 7, which is firmly connected to the spindle nut 5, to the output shaft journal 8 of the actuator is transmitted.
  • the torque reaches the planetary gear stage 11 on the one hand to the - in contrast to conventional planetary gearheads - also non-self-locking worm stage 9, which is braked by the braking device 10 when the pressure is below the safety pressure, and on the other hand to the self-locking worm stage 12 compensated there.
  • the actuator motor 13 also acts on this self-locking worm stage 12 and, in normal operation - controlled by the control system - effects the adjustment of the throttle body 3.
  • the function of the worm stage 12, the effect of the control motor 13 (also referred to as the drive or servomotor), the torque-dependent cut-off by moving the worm and pressing in the torque spring 14 correspond to the previously proven actuator technology (e.g. Siemens actuators).
  • the axial thrust generated by the internal medium (steam) and acting via the throttle body 3 and the valve spindle 4 is converted into a torque in the non-self-locking spindle nut 5 and displaces the spindle nut 5, spindle nut housing 7, output shaft journal 8, planetary gear stage 11 and non-self-locking worm stage 9 in a rotary motion.
  • the throttle body 3 and the valve spindle 4 move upward.
  • the valve is opened up to the open position.
  • the self-actuated opening process (safety stroke) is ended by braking the non-self-locking screw stage 9 via the braking device 10.
  • the self-actuated opening process can take place from the firing position and from any intermediate position.
  • the self-actuated opening process (safety stroke) is also released.
  • the self-actuated opening process also takes place when, when the contacts of the pressure switch 15 are open, the control motor 13 is actuated simultaneously in the closed direction.
  • the compensation takes place via the planetary gear stage 11.
  • control motor 13 If the control motor 13 is actuated simultaneously in the up direction (safety direction) when the safety stroke has been triggered, this actuating movement is additionally superimposed on the self-actuated opening process.
  • This causes the pawl 19 of a directional lock RG, which engages in the toothed ratchet wheel or ratchet wheel 10a 1 of the braking device 10 and only releases this in the direction of rotation generated by the self-actuated opening process (safety stroke).
  • the ratchet wheel 10a 1 is rotatably connected to the first brake disc 10a.
  • the function of the safety station with its own medium-operated safety function in the negative direction is shown in FIG. 2.
  • the steam valve with the housing 1 is flowed through from the inlet port 2a from above via the throttle body 3a (here, for example, a perforated throttle body).
  • the steam exerts an axial force on the throttle body 3a, the spindle 4 and the spindle nut 5, which is proportional to the effective throttle body cross section and the pressure difference between the inlet nozzle 2a and the outlet nozzle 6a and acts in the closed direction.
  • the steam forces act in the closing direction of the throttle body 3a.
  • the safety movement of the throttle body 3a also takes place in this direction, so that the free-wheel rotation of the directional lock RG now takes place in the clockwise direction f4 (in the example according to FIG. 1, the free-wheel rotation takes place in the counter-clockwise direction f3).
  • the actuator according to FIG. 2 is constructed in the same way as that according to FIG. 1, therefore the same parts are provided with the same reference numerals, and the functional sequence is analogous.
  • the pressure in the outlet connection 6a or in the systems behind it increases above that at the pressure monitors
  • the mechanical coupling of the brake magnets 16 to the brake device 10 in connection with the springs 17 is constructed in such a way that the drop of a magnet causes the brake device 10 to be safely vented.
  • the axial thrust generated by the internal medium (steam) and acting via the throttle body 3a and the valve spindle 4 is converted into a torque in the non-self-locking spindle nut 5 and displaces the spindle nut 5, spindle nut housing 7, output connector 8, planetary gear stage 11 and non-self-locking worm stage 9 in a rotary motion.
  • the throttle body 3a and the valve spindle 4 move downward. The valve is closed until at least one of the switch contacts on the pressure monitors 15 remains open.
  • the self-actuated closing process (safety stroke) is ended by braking the non-self-locking screw stage 9 via the brake device 10.
  • the self-actuated closing process can from the end position and from any intermediate layer.
  • the self-actuated closing process also takes place when the control motor 13 is actuated simultaneously in the open direction when the pressure switch 15 is open.
  • the compensation takes place via the planetary gear stage 11.
  • control motor 13 If the control motor 13 is actuated simultaneously in the closed direction (safety direction) when the safety stroke has been triggered, this actuating movement is additionally superimposed on the self-actuated closing process.
  • This causes the pawl 19a, which engages in the toothed ratchet wheel or ratchet wheel 10a of the braking device 10 and only releases it in the direction of rotation generated by the self-actuated opening process (safety stroke).
  • safety function With the safety function in the negative direction, this direction of rotation is opposite to that with the safety function in the positive direction.
  • the exemplary embodiment according to FIG. 3 also relates to a safety station which is suitable in process engineering for reducing and metering energy flows (gases, water) and at the same time reliably protecting the system systems against excess pressure, specifically with its own-medium-operated safety function in the opening direction.
  • the safety station essentially consists of an operating line and two additional safety lines.
  • the safety stroke can be triggered both via the operating line and via each individual safety line.
  • the operating line consists of a motorized actuator, a non-self-locking spindle nut and the actuator Throttle body together.
  • the two additional, independent, safety lines are arranged between the spindle nut and the actuator of the operating line. They consist of braked, non-self-locking thread steps. In the braked state, the safety lines form a rigid connection between the spindle nut and the actuator of the operating line. In accordance with the direction of flow of the throttle body in the actuator, the safety stroke is actuated by the own medium.
  • the motorized actuator is a modification of the tried-and-tested Siemens two-motor drive with planetary gear.
  • Screw stage - is replaced by a non-self-locking worm stage with an electromagnetic braking device on the worm shaft.
  • this non-self-locking worm stage remains braked, when the safety function responds, the brake device releases and releases the worm stage for the operating stroke's own-medium-operated safety stroke.
  • the torque required to execute the safety stroke via the operating line is generated by the internal medium
  • Throttle body, the valve spindle, the spindle linkage, the braked safety strands and the non-self-locking spindle nut are brought to the motorized actuator.
  • the safety stroke is carried out via the safety strands by releasing the associated braking devices on the spindle nuts of the non-self-locking thread stages of the safety strands.
  • the non-rotatably mounted spindle shafts are pressed into the nuts by the force of the own medium, causing them to rotate when the brake is released, thereby enabling the actuator to be opened safely.
  • Both Safety lines work completely independently of one another. To safely open the actuator, it is sufficient to release the brake device on a safety line.
  • the operating line BS essentially consists of a motor-driven actuator, a non-self-locking spindle nut 5 and the actuator 1, 3.
  • the two safety lines SSt 1, SSt 2 each consist of a brakeable, non-self-locking screw stage 20a, 23; 20b 23, which are coupled via a suitable spindle linkage 4a, 4b between the spindle nut 5 and the actuator 1, 3.
  • a spring element 22 is inserted in the longitudinal axis of the spindle 4 between the safety lever 4a and the housing bridge 4b of the spindle linkage.
  • a steam valve with the housing 1 flows against the throttle body 3 (here, for example, a parabolic throttle body) via the inlet connection 2.
  • the steam exerts an axial force on the throttle body 3, the spindle 4, the spindle linkage in the form of a safety lever 4a and a housing bridge 4b, the safety spindles 20a and 20b and the spindle nut 5, which is proportional to the effective throttle body cross section and the pressure difference between is the inlet connector 2 and the outlet connector 6 and acts in the up direction.
  • Axial thrust acting on safety spindles 20a and 20b is converted into a torque in the non-self-locking spindle nut 5 and sets the spindle nut 5, spindle nut housing 7, output shaft journal 8, non-self-locking worm stage 9 and planetary stage 11 in a rotary movement.
  • the throttle body 3 the valve spindle 4 and the spindle linkage 4a and 4b with the safety spindles 20a and 20b move upward. If the switch contact of the pressure switch 15a remains open for so long, the valve is opened up to the open position.
  • the self-actuated opening process of the operating line BS (safety stroke) is ended by braking the non-self-locking worm stage 9 via the braking device 10.
  • the self-operated opening process (safety stroke) of the operating line BS can take place from the end position and from any intermediate position.
  • the operating medium-operated opening process (safety stroke) of the operating line BS also takes place when the control motor 13 is actuated simultaneously in the closed direction when the pressure monitor contact 15a is open.
  • the compensation takes place via the planetary gear stage 11. If the control motor 13 when the safety stroke is triggered
  • two independent safety lines SSt 1, SSt 2, which essentially consist of the non-self-locking safety spindles 20a and 20b with the associated brake magnets 16b and 16c, are connected.
  • the safety spindles 20a, 20b are in the extended state (corresponding to the position shown).
  • the two safety spindles are braked via the associated safety spindle nuts 23 and the brake magnets 16b and 16c.
  • the brake magnets 16b or 16c are de-energized due to the pressure switches 15b or 15c responding, the rigid connection between the spindle linkages 4a and 4b is released.
  • the force of the own medium then pushes the tiltable spindle linkage 4a with the safety spindle 20a or 20b upward through the rotating safety spindle nuts via the first spindle section 4.1.
  • the throttle body 3 can always reach the open position as soon as the safety stroke is triggered via a line (operational or safety line). Of course, this also applies when two or three lines are activated at the same time.
  • the safety lines can also be checked separately using the hand switches 18b and 18c and the brake magnets 16b and 16c. Here the check is also possible below the security pressure.
  • At least one brake magnet 16a downstream of a pressure monitor 15a is provided, which locks or releases the overdrive device SG, and that at least one additional safety line SSt 1 downstream of a further pressure monitor 15b is provided, which is provided with means 16b, 20a, 4a for displacing a first spindle section 4.1 having the throttle body 3 into the open position relative to a spring-elastic (spring 22) coupled to the first spindle section 4.1, which has the non-self-locking spindle drive, is provided when a pressure switch - Trigger signal is present.
  • Two additional safety lines SSt 1, SSt 2 are shown.
  • the first spindle section 4.1 is coupled to the second spindle section 4.2 via a compression spring arrangement 22.
  • a safety lever 4a is articulated to the end of the first spindle section 4.1 facing away from the throttle body 3, with at least one free end to which an auxiliary spindle 20a, 20b which runs essentially parallel to the valve spindle 4 is articulated via an elongated hole joint.
  • the auxiliary spindle 20a, 20b includes a non-self-locking auxiliary spindle drive with at least a first brake disc 24 mounted with the spindle nut 23 and a second brake magnet 16b, which normally holds the auxiliary spindle 20a on its brake disc 24 and, if a trigger signal is supplied by the associated pressure switch 15b releases the spindle nut 23 for rotation and the auxiliary spindle 20a for axial movement.
  • the housing 25 of the auxiliary spindle drive and the second brake magnet 16b is rigidly coupled to the second spindle section 4.2 and is mounted so that it can be moved longitudinally. The same applies to the second safety line SSt 2.
  • Safety levers 4a in the manner of a rocker are designed with two arms and at each of their two free ends an auxiliary spindle 20a, 20b, each with an auxiliary spindle drive, is articulated, the housing 25 of the two auxiliary spindle drives and their associated brake magnets 16b, 16c via a housing bridge 4b and each other Housing bridge 4b are firmly connected to the second spindle section 4.2 of the valve spindle 4.
  • the planetary gear stage is generally designated B in FIGS. 4 to 6, it has two diametrically opposed planet gears bl and b2, which mesh with the sun gear A on their inner circumference and mesh with their inner circumference with an internal toothing of the ring gear C.
  • the latter is part of the overdrive device SG, i.e. if the latter is released by the brake magnet, the output shaft journal can rotate via the worm drive 9 (FIGS. 1-3) without braking; the throttle body 3 reaches its open position (FIGS. 1 and 3) or its closed position (FIG. 2).
  • the table according to FIG. 6 first shows that in normal operation the sun gear A is driven and the planetary stage B is entrained, whereas the overdrive device SG is braked.
  • the internal ring gear of C represents a fixed runway for the planet gears bl, b2.
  • the sun gear A a runway for the planet gears bl, b2, which is either fixed (if there is no control command) or moving itself.
  • the compression spring arrangement 22 in the example according to FIG. 3 has the following tasks in particular:
  • an auxiliary closing spring 27, designed as a helical compression spring, is inserted between a collar 28 of the spindle 4 and the holding body 29 fixed to the housing. It has the task of preventing the throttle body 3 from fluttering at low differential pressures between the inlet nozzle 2 and the outlet nozzle 6.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanically-Actuated Valves (AREA)
  • Transmission Devices (AREA)
  • Lift Valve (AREA)

Abstract

Dans un servomoteur pour soupapes de sûreté et de réglage, utilisé dans des postes de sécurité pour le dosage de flux énergétiques sous forme de gaz, de vapeurs, ou d'eau, notamment dans des centrales thermiques ou des centrales industrielles, la force de propulsion pour le parcours de sécurité du corps d'étranglement (3) du flux résulte de la différence de pression exercée par le fluide moteur sur ce corps. De plus, la commande de la tige de la soupape de sûreté n'est pas à blocage automatique. On utilise, à la place du moteur à vitesse surmultipliée, un dispositif à vitesse surmultipliée (SG) qui est accouplé, par l'intermédiaire d'une transmission non autobloquante (9), au niveau (11) de l'engrenage planétaire du servomoteur et qui présente un arbre (9a) normalement bloqué par un dispositif de freinage amovible (10), ce dispositif de freinage (10) débloquant, en cas de pression de réponse, le dispositif à vitesse surmultipliée (SG) en vue d'assurer le déplacement de sécurité, commandé par le fluide proprement dit, du corps d'étranglement (3) dans saposition prescrite. Pour un sens d'actionnement positif, la position prescrite est la position d'ouverture du corps d'étranglement (3) et, pour un sens d'actionnement négatif, la position prescrite est la position de fermeture.
EP90903765A 1989-03-07 1990-03-06 Servomoteur pour soupapes de surete et de reglage Expired - Lifetime EP0462126B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3907289 1989-03-07
DE3907289A DE3907289A1 (de) 1989-03-07 1989-03-07 Stellantrieb fuer sicherheitsventile

Publications (2)

Publication Number Publication Date
EP0462126A1 true EP0462126A1 (fr) 1991-12-27
EP0462126B1 EP0462126B1 (fr) 1993-11-10

Family

ID=6375717

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90903765A Expired - Lifetime EP0462126B1 (fr) 1989-03-07 1990-03-06 Servomoteur pour soupapes de surete et de reglage

Country Status (8)

Country Link
US (1) US5152316A (fr)
EP (1) EP0462126B1 (fr)
JP (1) JPH04503988A (fr)
KR (1) KR920701613A (fr)
CN (1) CN1023148C (fr)
AU (1) AU631406B2 (fr)
DE (2) DE3907289A1 (fr)
WO (1) WO1990010783A1 (fr)

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US5735456A (en) * 1994-09-07 1998-04-07 The Steam-O-Stat Company Universal retrofit valve actuator and system
US5806553A (en) * 1995-07-17 1998-09-15 Sidwell; Herbert R. Fluid pressure control and relief apparatus
DE19652583C1 (de) * 1996-12-17 1997-11-20 Holter Gmbh & Co Elektrischer Stellantrieb für ein Ventil o. dgl.
RU2178842C1 (ru) * 2001-01-09 2002-01-27 Саяпин Вадим Васильевич Пневматический привод, струйный двигатель (варианты) и электропневматическое управляющее устройство
DE20311032U1 (de) * 2003-07-17 2004-11-25 Cooper Cameron Corp., Houston Antriebsvorrichtung
US7287541B2 (en) * 2004-01-16 2007-10-30 Battelle Energy Alliance, Llc Method, apparatus and system for controlling fluid flow
US20060278836A1 (en) * 2005-06-14 2006-12-14 Vincent Raymond A Valve mechanism for a plumbing device
US9163479B2 (en) * 2007-08-03 2015-10-20 Baker Hughes Incorporated Flapper operating system without a flow tube
US7703532B2 (en) * 2007-09-17 2010-04-27 Baker Hughes Incorporated Tubing retrievable injection valve
ES2397227T3 (es) * 2008-04-18 2013-03-05 Oventrop Gmbh. & Co. Kg. Combinación de grifería para regular el caudal o la diferencia de presión
DE102009053829A1 (de) * 2009-11-18 2011-05-19 Mahle International Gmbh Stellvorrichtung und Verwendung
JP5863362B2 (ja) * 2011-09-28 2016-02-16 三菱重工コンプレッサ株式会社 蒸気タービン
US20130245840A1 (en) * 2012-03-16 2013-09-19 Gerard S. Lazzara Modulated Reset Relief Valve
CN102679523A (zh) * 2012-06-06 2012-09-19 上海华东电脑系统工程有限公司 具有齿轮结构的动态气流调节风阀
CN102678993A (zh) * 2012-06-06 2012-09-19 上海华东电脑系统工程有限公司 动态气流调节风阀
US9958083B1 (en) * 2016-10-27 2018-05-01 National Enviornmental Products, Ltd. Force limited valve actuator and method therefor
DE202020102557U1 (de) 2020-05-06 2021-08-09 Karl Morgenbesser Stelleinrichtung für Systeme mit strömendem Fluid sowie System mit Stelleinrichtung
DE202020102558U1 (de) 2020-05-06 2021-08-09 Karl Morgenbesser Stelleinrichtung für Systeme mit strömendem Fluid sowie System mit Stelleinrichtung
CN112856226B (zh) * 2021-01-12 2022-01-14 佛冈鼎立气体有限公司 一种实现智能化控制的气瓶阀门
CN113057015B (zh) * 2021-03-23 2022-02-11 中国水产科学研究院渔业机械仪器研究所 一种养殖筏架吊绳脱扣装置

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Also Published As

Publication number Publication date
DE59003479D1 (de) 1993-12-16
JPH04503988A (ja) 1992-07-16
US5152316A (en) 1992-10-06
CN1048094A (zh) 1990-12-26
WO1990010783A1 (fr) 1990-09-20
EP0462126B1 (fr) 1993-11-10
CN1023148C (zh) 1993-12-15
KR920701613A (ko) 1992-08-12
AU631406B2 (en) 1992-11-26
DE3907289A1 (de) 1990-09-13
AU5169590A (en) 1990-10-09

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