EP0658909A1 - Dispositif d'entraînement pour un disjoncteur de puissance - Google Patents

Dispositif d'entraînement pour un disjoncteur de puissance Download PDF

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Publication number
EP0658909A1
EP0658909A1 EP93120052A EP93120052A EP0658909A1 EP 0658909 A1 EP0658909 A1 EP 0658909A1 EP 93120052 A EP93120052 A EP 93120052A EP 93120052 A EP93120052 A EP 93120052A EP 0658909 A1 EP0658909 A1 EP 0658909A1
Authority
EP
European Patent Office
Prior art keywords
section
switch
cam
radius
pawl
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
EP93120052A
Other languages
German (de)
English (en)
Other versions
EP0658909B1 (fr
Inventor
Rolf Niklaus
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.)
General Electric Switzerland GmbH
Original Assignee
GEC Alsthom T&D 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 GEC Alsthom T&D AG filed Critical GEC Alsthom T&D AG
Priority to EP93120052A priority Critical patent/EP0658909B1/fr
Priority to DE59304319T priority patent/DE59304319D1/de
Priority to AT93120052T priority patent/ATE144646T1/de
Priority to JP6323505A priority patent/JPH07201247A/ja
Priority to US08/350,878 priority patent/US5541378A/en
Publication of EP0658909A1 publication Critical patent/EP0658909A1/fr
Application granted granted Critical
Publication of EP0658909B1 publication Critical patent/EP0658909B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H3/00—Mechanisms for operating contacts
    • H01H3/22—Power arrangements internal to the switch for operating the driving mechanism
    • H01H3/30—Power arrangements internal to the switch for operating the driving mechanism using spring motor
    • H01H3/3005—Charging means
    • H01H3/3026—Charging means in which the closing spring charges the opening spring or vice versa
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H3/00—Mechanisms for operating contacts
    • H01H3/22—Power arrangements internal to the switch for operating the driving mechanism
    • H01H3/30—Power arrangements internal to the switch for operating the driving mechanism using spring motor
    • H01H2003/3084—Kinetic energy of moving parts recuperated by transformation into potential energy in closing or opening spring to be used in next operation
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H3/00—Mechanisms for operating contacts
    • H01H3/32—Driving mechanisms, i.e. for transmitting driving force to the contacts
    • H01H3/42—Driving mechanisms, i.e. for transmitting driving force to the contacts using cam or eccentric
    • 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
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams

Definitions

  • the present invention relates to a drive device for a circuit breaker, in particular for medium and high voltage, according to the preamble of claim 1.
  • a drive device of this type is disclosed in DE-A-25 17 134.
  • a cam On a shaft rotatably mounted about its axis, on which an energy storage device designed as a tension spring acts eccentrically, a cam is seated in a rotationally fixed manner, the cam track of which has a first section, the radius of which increases steadily with increasing azimuth against the direction of rotation of the shaft.
  • At the rear end of the first section in the direction of rotation there is a second section running approximately in the radial direction with an abruptly decreasing radius, to which a third section adjoins the direction of rotation, which extends to the beginning of the first section and has a radius that corresponds approximately to the radius at the beginning of the first section.
  • a switching shaft connected to the movable contact of the circuit breaker is arranged parallel to the shaft and on it there sits a disk in a rotationally fixed manner, from which a peg-like follower projects eccentrically with respect to the axis of the switching shaft.
  • the shaft is also connected to an opening spring.
  • the disk On its circumference, the disk has a latching recess which is intended to cooperate with an opening pawl of a pawl device.
  • the shaft is rotated in the direction of rotation beyond the unstable dead center and held there supported by a closing pawl.
  • the release pawl is released, causing the shaft to rotate in the direction of rotation due to the force of the switch-on spring.
  • the cam section runs with its first section on the follower and swivels the shift shaft from its switch-off position to the switch-on position and by an overtravel as it rotates further. This overstroke is generally necessary to ensure that the latching device engages.
  • the switch-off spring accelerates the selector shaft until it is in contact with the switch-off pawl.
  • the pawl device therefore not only has to support the force of the switch-off spring, but also has to absorb the additional impact stress caused by striking the switch-off pawl.
  • the shaft rotates by approximately 180 °, the excess energy being recuperated into the switch-on spring by turning beyond the stable dead center position.
  • a cam disk which can be rotated in the direction of rotation by 360 ° by means of switch-on springs for switching on the switch has a cam track with a first and a second section.
  • the radius of the first section increases with the azimuth increasing counter to the direction of rotation, spiraling over an angle of almost 360 °.
  • the abruptly falling second section extends approximately in the radial direction.
  • a follower designed as a roller cooperates with the cam disc, which is mounted on one end of a two-armed lever, the other end of which is intended to interact with a latching device and which is connected to the movable contact of the circuit breaker and an opening spring.
  • the lever Due to the pulse-like rotation of the cam disc by 360 °, the lever is moved from its switch-off position from the first section, while simultaneously switching on the switch and tensioning the switch-off spring, into the switch-on position and beyond. If the first section runs from the follower, the switch-off spring accelerates the lever in the opposite direction until it is in contact with the latch device.
  • the pawl device also has to absorb the dynamic force due to the lever being opened.
  • a drive device having a cam disk which has a different construction and a different mode of operation than the two aforementioned drive devices, is disclosed in EP-A-0 150 756.
  • a roller-like follower interacting with the cam track of the cam is arranged on a lever that is operatively connected to the closing spring.
  • the cam track of the cam disk which can be driven in the direction of rotation by means of a motor or by hand, has a first section with an increasing azimuth opposite to the direction of rotation. Contrary to the direction of rotation, a section adjoins this first section with an increasing azimuth, gradually decreasing radius, to which in turn adjoins a second section running essentially in the radial direction, followed on the inside by the first section.
  • the closing spring When the closing spring is relaxed, the next link is at the beginning of the first section.
  • the closing spring is tensioned by slowly rotating the cam disc in the direction of rotation by a little less than 360 ° until the end of the first section.
  • the closing spring drives the cam disc in the direction of rotation.
  • the cam disc now uncoupled from the engine is prevented from turning further by means of a ratchet device.
  • the pawl device To turn on the circuit breaker connected to the drive device, the pawl device is energized to release the cam. This begins to rotate under the force of the closing spring acting via the lever and the follower reaches the abruptly falling second section, so that the cam disc no longer exerts any counterforce against the action of the closing spring.
  • the pawl device Since the follower lies against an intermediate section of the cam track until it is supported on the pawl device, the pawl device runs onto it at a low speed, so that the dynamic impact forces are considerably reduced or even avoided.
  • the pawl device can thus be dimensioned for the static force effect of the opening spring and the reduced dynamic impact forces, which enables a light, space-saving construction of the pawl device and the entire drive device. Since the moving masses of the pawl device can be kept small, quick unlatching takes place and / or less work is required for the unlatching.
  • a particularly preferred embodiment of the drive device according to the invention enables the acceptance of large tolerances.
  • Another preferred embodiment of the drive device according to the invention is specified in claim 3. It enables the first and second sections of the curved path to be formed in a smaller azimuth range than if there were a further section with a constant radius between the first section and the intermediate section.
  • the drive device 10 shown in FIG. 1 for driving a circuit breaker 12 for medium or high voltage which is only indicated schematically, has a shaft 16, which is freely rotatably mounted on a frame 14 in a known manner and on which a cam disk 18 is seated in a rotationally fixed manner.
  • the outer surface of the cam 18 forms a cam track 20, which cooperates with a roller 22 'acting as a follower 22.
  • the roller 22 ' is freely rotatably mounted on the free end of a lever 24 which is non-rotatably seated on a control shaft 26 parallel to the shaft 16.
  • the control shaft 26 is also freely rotatably mounted on the frame 14 and connected to the moving contact piece 30 of the circuit breaker 12 via a linkage 28.
  • a pawl lever 32 On the selector shaft 26 there is also a pawl lever 32, which is intended to cooperate with the pawl 34 supported on the frame 14 in the switch-on position I shown in dash-dotted lines.
  • the pawl 34 can be pivoted by means of an electric switch-off magnet 36 to release the pawl lever 32 and thus the shift shaft 26 from a support position into a release position.
  • the pawl lever 32, the pawl 34 and the electric switch-off magnet 36 form a pawl device 37.
  • a switch-off spring 38 designed as a helical compression spring is supported on one end on the frame 14 and is connected at the other end to a pulling element 40 designed as a chain, which deflects around a deflection wheel 42 which is freely rotatably mounted on the frame 14 and is articulated on the other side to a drive lever 44 which is non-rotatably seated on the control shaft 26 is. If the control shaft 26 is rotated into the on position I, the drive lever 44 extends approximately at right angles to the direction of attack of the pulling element 40; in the off position O of the control shaft 26, the direction of engagement of the pulling element 40 is almost in the extended position relative to the drive lever 44.
  • control shaft 26 is connected to a damping element 46 in order to dampen the rotary movement of the control shaft 26 towards the end of a switch-off process.
  • the cam track 20 of the cam disc 18 has a first section 48 which has a constantly increasing radius A when the azimuth ⁇ increases counter to the direction of rotation indicated by an arrow D.
  • the first section 48 extends through an angle 48 ′′ of approximately 155 °.
  • an intermediate section 50 At the end 48 'of the first section 48 with the maximum radius A, as seen against the direction of rotation D, there is an intermediate section 50, the radius A of which decreases steadily and slowly with increasing azimuth ⁇ .
  • the intermediate section 50 extends over an angle 50 'of preferably 10 ° -20 °, in the present case of approx.
  • the radius decreases in it A by an amount B which is approximately 0.2 to 5%, preferably 0.5 to 1.5% of the difference between the minimum radius A min at the beginning of the first section 48 and the largest radius A max at the end 48 ' of the first section 48.
  • the intermediate section 50 is adjoined by a second section 52 which is concavely curved with a radius that is larger than the radius of the movement path of the follower 22 and whose end region adjoining the intermediate section 50 extends approximately in the radial direction.
  • the second section 52 extends over an angle 52 ′ of approximately 57 °. This second section 52 enables the switching shaft 26 to be turned from the on position I to the off position O without the follower 22 touching the cam plate 18 (see also FIG. 6).
  • the second section 52 is adjoined by a third section 54 with a radius A which corresponds to the minimum radius A min at the beginning of the first section and which extends over an angular range 54 ′ to the beginning of the first section 48.
  • a preferred embodiment of this pair of wheels 58 is disclosed in European Patent Application No. 93 117 797.6.
  • a chain forming a tension element 66, which is guided around a further deflection wheel 42 'which is rotatably mounted on the frame 14 and is operatively connected at the other end to a closing spring 68.
  • This is designed as a helical compression spring and is also supported on the frame 14; it forms an energy store 68 '.
  • a locking pin 70 is fastened to the large wheel 56, which interacts with a switch pawl 72 mounted on the frame 14. This is connected to an electric switch-on magnet 74, by means of which the switch pawl 72 can be retracted from a support position, in which it engages in the movement path of the locking pin 70, into a release position.
  • the latching pin 70, the catch pawl 72 and the electrical switch-on magnet 74 form a switch pawl device 75 and furthermore rotatable, after which the locking pin 70 runs further by an angle of a few degrees after reaching the unstable dead center position on the engagement pawl 72 and is held against it under the action of the tensioned engagement spring 68.
  • the elevator motor 64 is switched off after the unstable dead center position has been exceeded.
  • FIG. 3 This figure and the further FIGS. 4-6 show the cam plate 18, a lever 24 and the pawl lever 32, on the selector shaft 26 seated triangular lever 76 on which the roller 22 'is freely rotatably mounted, and the pawl 34 of the pawl device 37.
  • the pawl nose which cooperates with the pawl 34 and corresponds to the pawl lever 32 (FIG. 1) is denoted by 78.
  • the dash-dotted segment 80 of a circle about the axis 16 'of the shaft 16 indicates that radius A k which corresponds to the position of the follower 22 or the roller 22' when the triangular lever 76 with its pawl nose 78 on the Pawl 34 abuts; this is the switch-on position.
  • the segment 80 crosses both the first section 48 and the intermediate section 50 of the curved track 20.
  • the double arrow U denotes an overstroke which is given by the difference between the largest radius A max of the first section 48 of the curved track 20 and the radius A k .
  • FIG. 6 a further segment 82 of a circle, indicated by dash-dotted lines, around the axis 26 'of the shift shaft 26 shows the range of motion of the roller 22' when shifting.
  • the drive device 10 is shown with the closing spring 68 tensioned and the switching shaft 26 in the off position O.
  • the electric closing magnet 74 is briefly energized, as a result of which the closing pawl 72 releases the latching pin 70 and the shaft 16 together with the cam plate 18 underneath Force of the closing spring 68 begins to turn in direction D.
  • the cam 18 runs onto the roller 22 'and, in cooperation with the first section 48 of the cam track 20, rotates the triangular lever 76 and thus the selector shaft 26 in the switch-on direction E, which is opposite to the direction of rotation D (FIG. 4).
  • the circuit breaker 12 is closed and the opening spring 38 is tensioned.
  • the pawl nose 78 pushes the pawl 34 back out of its support position in a clockwise direction, which by turning back into the support position engages behind the pawl nose 78 as soon as the cam 18 has reached the position at which the point of intersection of the first section 48 of the curve 20 with the segment 80 passes the roller 22 '.
  • the triangular lever 76 is moved by an excess stroke U beyond the switch-on position in order to ensure that the pawl device 37 is latched under all conditions. This position is reached when the end 48 'of the first section 48 with the radius A max interacts with the roller 22'.
  • the articulation of the tension element 66 is preferably at least approximately in the stable dead center position.
  • the intermediate section 50 interacts with the roller 22 ', as a result of which the switching shaft 26, which is under the force of the tensioned opening spring 38, counteracts the closing direction E in accordance with the intermediate section 50 moved back until the pawl nose 78 abuts the pawl lever 76. This is achieved at the rotational position of the cam plate 18 at which the intersection of the intermediate section 50 with the segment 80 lies against the roller 22 '.
  • the elevator motor 64 is now switched on until the unstable dead center position is exceeded and the locking pin 70 is again in contact with the switch pawl 72.
  • the closing spring 68 is tensioned, the third section 54 moves past the movement path 82 of the follower 20 ′, so that the circuit breaker 12 can be switched off at any time.
  • the drive device 10 is now ready for the circuit breaker 12 to be switched on again immediately.
  • the decrease in the radius A of the intermediate section 50 of the cam track 20 is matched with respect to the corresponding rotational speed of the shaft 16 such that the pawl nose 78 runs onto the switch-off pawl 34 at a low speed.
  • the triangular lever 76 is supported by the cam 18 until it contacts the switch-off pawl 34.
  • cam disk 18 shown in FIG. 2 together with the specified angles and radii is only to be understood as an example and that both the angles and the radii can vary considerably.
  • shape of the cam 18 according to the invention can also be used in a drive device in which the cam disk is rotated through 360 ° to switch on the circuit breaker, as is the case with the drive device disclosed in CH-A-498 480.
  • the first section of the cam track with a steadily increasing radius and the intermediate section with a slowly steadily decreasing radius extend together over an angle of almost 360 °, so that the second section, which runs essentially in the radial direction, ensures that the follower is switched off of the circuit breaker can move past the cam 18.
  • the intermediate section preferably extends over an angle 50 'of between 10 and 20 °.
  • this angle in particular in the case of a switching device in which the cam disk rotates through 360 ° to switch on the circuit breaker, is greater than 20 °.
  • the decrease B in the radius in the intermediate section 50 is at least the same size, preferably greater than the overstroke U.
EP93120052A 1993-12-13 1993-12-13 Dispositif d'entraînement pour un disjoncteur de puissance Expired - Lifetime EP0658909B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP93120052A EP0658909B1 (fr) 1993-12-13 1993-12-13 Dispositif d'entraînement pour un disjoncteur de puissance
DE59304319T DE59304319D1 (de) 1993-12-13 1993-12-13 Antriebsvorrichtung für einen Leistungsschalter
AT93120052T ATE144646T1 (de) 1993-12-13 1993-12-13 Antriebsvorrichtung für einen leistungsschalter
JP6323505A JPH07201247A (ja) 1993-12-13 1994-12-01 電源スイッチ用駆動装置
US08/350,878 US5541378A (en) 1993-12-13 1994-12-07 Drive device for a power switch

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP93120052A EP0658909B1 (fr) 1993-12-13 1993-12-13 Dispositif d'entraînement pour un disjoncteur de puissance

Publications (2)

Publication Number Publication Date
EP0658909A1 true EP0658909A1 (fr) 1995-06-21
EP0658909B1 EP0658909B1 (fr) 1996-10-23

Family

ID=8213486

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93120052A Expired - Lifetime EP0658909B1 (fr) 1993-12-13 1993-12-13 Dispositif d'entraînement pour un disjoncteur de puissance

Country Status (5)

Country Link
US (1) US5541378A (fr)
EP (1) EP0658909B1 (fr)
JP (1) JPH07201247A (fr)
AT (1) ATE144646T1 (fr)
DE (1) DE59304319D1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1237169A1 (fr) * 2001-03-01 2002-09-04 Alstom Disjoncteur à haute tension ayant une commande à ressorts avec un ressort additionnel de récuperation d'énergie
CN112382517A (zh) * 2020-11-02 2021-02-19 平高集团有限公司 一种弹簧操动机构合闸系统及弹簧操动机构

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19650590B4 (de) * 1996-12-06 2006-08-17 Areva Sachsenwerk Gmbh Antrieb für einen Schalter
FR2763740B1 (fr) * 1997-05-26 1999-07-16 Gec Alsthom T & D Ag Mecanisme d'entrainement a ressort pour un appareil de commutation, en particulier un disjoncteur
FR2770929B1 (fr) * 1997-11-13 2000-01-28 Alsthom Gec Mecanisme d'entrainement a ressort pour un appareil de commutation, en particulier un disjoncteur
UA72529C2 (en) * 1999-07-29 2005-03-15 Hatebur Umformmaschinen Ag Lifting and lowering device
JP3853619B2 (ja) * 2001-08-20 2006-12-06 三菱電機株式会社 開閉機器の操作装置
WO2004022425A1 (fr) * 2002-09-03 2004-03-18 Airbus Deutschland Gmbh Dispositif pour avertir d'une pression differentielle lors de l'ouverture d'un dispositif de fermeture soumis a une pression d'une ouverture menagee dans le fuselage d'un avion
CN100458995C (zh) * 2003-09-13 2009-02-04 Abb技术有限公司 电气开关设备的起动装置
DE102008035871B4 (de) * 2008-08-01 2011-03-24 Abb Technology Ag Nockenscheibe und Federwegschalter für einen Federspeicherantrieb sowie Federspeicherantrieb
WO2013143620A1 (fr) 2012-03-30 2013-10-03 Abb Ab Commutation de circuit électrique
CN103632861B (zh) * 2013-11-30 2016-04-20 安徽鑫辰电气设备有限公司 一种高压柜安全装置
US9349277B2 (en) * 2014-04-01 2016-05-24 Prof4Tech Ltd. Personal security devices and methods
EP3153722A1 (fr) * 2015-10-07 2017-04-12 General Electric Technology GmbH Ensemble pour disjoncteur tel qu'un ensemble à levier d'actionnement et procédé de fabrication d'un tel ensemble
DE102018132027B4 (de) * 2018-12-13 2020-07-02 Maschinenfabrik Reinhausen Gmbh GETRIEBE sowie Laststufenschalter mit dem Getriebe
EP3958284A1 (fr) * 2020-08-19 2022-02-23 Hitachi Energy Switzerland AG Came d'entraînement à ressort pour une transmission par ressort d'un disjoncteur

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Publication number Priority date Publication date Assignee Title
AT208451B (de) * 1958-12-20 1960-04-11 Sprecher & Schuh Ag Einschaltvorrichtung mit Federkraftspeicher für elektrische Leistungsschalter
FR2019610A1 (fr) * 1968-10-01 1970-07-03 Asea Ab
CH561956A5 (fr) * 1974-04-25 1975-05-15 Sprecher & Schuh Ag
EP0150756A2 (fr) 1984-01-30 1985-08-07 Merlin Gerin Dispositif de commande d'un disjoncteur électrique

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US3072763A (en) * 1960-02-15 1963-01-08 Allis Chalmers Mfg Co Spring actuated contact opening and closing mechanism
US3203505A (en) * 1963-06-06 1965-08-31 Allis Chalmers Transmission mechanism
DE2244613C2 (de) * 1972-09-12 1973-12-13 Olympia Werke Ag, 2940 Wilhelmshaven Getriebeanordnung für Zahnrad getriebe
US3890853A (en) * 1974-07-31 1975-06-24 Singer Co Gear mechanism for producing periodic rotation
JPH0693338B2 (ja) * 1987-05-13 1994-11-16 三菱電機株式会社 遮断器の操作機構

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT208451B (de) * 1958-12-20 1960-04-11 Sprecher & Schuh Ag Einschaltvorrichtung mit Federkraftspeicher für elektrische Leistungsschalter
FR2019610A1 (fr) * 1968-10-01 1970-07-03 Asea Ab
CH498480A (de) 1968-10-01 1970-10-31 Asea Ab Antriebsvorrichtung für einen elektrischen Schalter
CH561956A5 (fr) * 1974-04-25 1975-05-15 Sprecher & Schuh Ag
DE2517134A1 (de) 1974-04-25 1975-11-13 Sprecher & Schuh Ag Antrieb fuer einen elektrischen leistungsschalter
EP0150756A2 (fr) 1984-01-30 1985-08-07 Merlin Gerin Dispositif de commande d'un disjoncteur électrique

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1237169A1 (fr) * 2001-03-01 2002-09-04 Alstom Disjoncteur à haute tension ayant une commande à ressorts avec un ressort additionnel de récuperation d'énergie
FR2821696A1 (fr) * 2001-03-01 2002-09-06 Alstom Disjoncteur haute tension ayant une commande a ressorts avec un ressort additionnel de recuperation d'energie
US6667452B2 (en) 2001-03-01 2003-12-23 Alstom High-voltage circuit-breaker having a spring-loaded control mechanism with an energy-recovering additional spring
CN112382517A (zh) * 2020-11-02 2021-02-19 平高集团有限公司 一种弹簧操动机构合闸系统及弹簧操动机构

Also Published As

Publication number Publication date
EP0658909B1 (fr) 1996-10-23
DE59304319D1 (de) 1996-11-28
US5541378A (en) 1996-07-30
ATE144646T1 (de) 1996-11-15
JPH07201247A (ja) 1995-08-04

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