EP0651409B1 - Federantrieb für ein Schaltgerät - Google Patents

Federantrieb für ein Schaltgerät Download PDF

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Publication number
EP0651409B1
EP0651409B1 EP93117797A EP93117797A EP0651409B1 EP 0651409 B1 EP0651409 B1 EP 0651409B1 EP 93117797 A EP93117797 A EP 93117797A EP 93117797 A EP93117797 A EP 93117797A EP 0651409 B1 EP0651409 B1 EP 0651409B1
Authority
EP
European Patent Office
Prior art keywords
switch
tooth
wheel
spring
flank
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP93117797A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0651409A1 (de
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 DE59307350T priority Critical patent/DE59307350D1/de
Priority to EP93117797A priority patent/EP0651409B1/de
Priority to AT93117797T priority patent/ATE158105T1/de
Priority to US08/328,650 priority patent/US5595287A/en
Priority to JP29583494A priority patent/JP3605620B2/ja
Publication of EP0651409A1 publication Critical patent/EP0651409A1/de
Application granted granted Critical
Publication of EP0651409B1 publication Critical patent/EP0651409B1/de
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
    • 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
    • H01H2003/3063—Decoupling charging handle or motor at end of charging cycle or during charged condition
    • 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
    • H01H3/36—Driving mechanisms, i.e. for transmitting driving force to the contacts using belt, chain, or cord
    • 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
    • Y10T74/19—Gearing
    • Y10T74/19949—Teeth
    • Y10T74/19963—Spur
    • Y10T74/19972—Spur form

Definitions

  • the present invention relates to a spring drive for a switching device, in particular a circuit breaker for medium and high voltage, according to the preamble of claim 1.
  • a spring drive of this type is known from EP-A-0 294 561.
  • a large wheel on which a tab is articulated with respect to the axis of rotation of the switch-on shaft, which is connected at the other end to a lever which in turn interacts with a switch-in spring designed as a torsion bar.
  • the large wheel meshes with a small wheel, which is driven by a drive element, around the closing shaft from an initial position, in which the closing spring is at least partially relaxed, via a dead center position, in which the line of action of the tab runs through the axis of rotation, and in which the closing spring is tensioned to drive in the direction of rotation.
  • a ratchet device supports the switch-on shaft against the action of the tensioned switch-on spring in a support position which is offset by a small angle in the direction of rotation with respect to the dead center position.
  • the sprocket of the large wheel has a tooth space at that point which is arranged on the small wheel when the switch-on shaft is supported on the ratchet device. This is to prevent the large wheel from being driven further by the small wheel when the switch-on spring is tensioned, thereby additionally loading the pawl device.
  • the pawl device releases the closing shaft, which is driven in the direction of rotation under the force of the closing spring.
  • the ring gear of the large wheel comes into engagement with the small wheel again.
  • the first tooth mentioned is in the radial direction designed to be resiliently pushed back. If this tooth hits the crown of a tooth of the small wheel at the start of switching on, it can back away towards the center of the large wheel and thus slide over the crown surface of the relevant tooth of the small wheel. He then intervenes in the gap for this tooth of the small wheel and thus synchronizes the small wheel with the large wheel.
  • US Patent No. 3,890,853 discloses a gearbox for non-blocking generation of a periodic output rotation from an input rotation.
  • the driven large wheel of a pair of wheels is designed as a ring wheel with an internal toothing having a gap.
  • the flanks of the teeth of the small wheel interacting with the large wheel abut one another radially on the outside in a common edge.
  • the first tooth following the gap in the direction of rotation of the large wheel has an asymmetrical pointed profile and its tooth height is greater than that of the other teeth of the large wheel.
  • the teeth of the small wheel Since the flanks of the teeth of the small wheel abut one another radially on the outside, the teeth have no tangential apex surfaces against which the first tooth following the gap of the large wheel could abut. It is also prevented that a tooth of the small wheel can rest on the tangential apex surface of the first tooth following the gap of the large wheel. This, albeit unlikely case, could occur with an existing crown surface if, immediately after tensioning the closing spring, when the small wheel is still in the outlet, the pawl device releases the closing shaft for switching on.
  • the frictional losses are minimized in that the teeth of the small wheel driven to tension the closing spring have an involute shape on the loaded flank that leads in the direction of rotation.
  • a flank plane inclined to a radial straight line can be produced in a simple manner, for example by grinding. This design of the small wheel enables the use of a commercially available toothed wheel with involute toothing, in which the tangential apex surface is removed by generating the inclined flank plane.
  • a further preferred embodiment of the spring drive according to the invention enables the use of a large wheel with involute toothing, which is only to be reworked to form the gap and to attach the inclined flat flank part to the first tooth following the gap.
  • a chain 26 On the large wheel 16, the end of a chain 26 is articulated with respect to the axis 14 'eccentrically and on the side facing away from the switch-on shaft 14, which chain is guided around a deflection wheel 27 which is also freely rotatably mounted on the frame 30 and through a switch-on spring 28 designed as a helical compression spring. With its end on this side, the chain 26 is attached to the free end of the switch-on spring 28 which is supported on the frame 30 at the other end.
  • a support roller 32 is rotatably mounted on the front side of the large wheel 16, which is intended to interact with a ratchet device 34 arranged on the frame 30.
  • This has a switch pawl 36 pivotably mounted on the frame 30, which can be brought into and out of a release position outside the path of movement of the support roller 32 by means of an electrical switch-on magnet 38 from a working position shown in FIG.
  • a cam disk 40 which cooperates with a roller lever 42 to switch on the circuit breaker 12, also sits on the closing shaft in a rotationally fixed manner.
  • a dead center position of the switch-on shaft 14 is indicated, in which the linkage of the chain 26 to the large wheel 16 is at 44', the switch-on spring 28 is maximally tensioned and the line of action of the chain 26 through the axis 14 'runs.
  • the switch-on shaft 14 is in the support position, which follows the dead center position 44 in the direction of rotation D indicated by arrows and is offset with respect to this by an angle, preferably measuring a few degrees.
  • the tensioned closing spring 28 acts in the direction of rotation D on the closing shaft 14, which is prevented from rotating by supporting the support roller 32 on the closing pawl 36.
  • Fig. 2 shows the pair of wheels 18, wherein the switch-on shaft 14 is in the support position 48. Also shown is the end region of the chain 26 on this side with its linkage 46 to the large wheel 16.
  • the toothing 52 of the large wheel 16 has a gap 54 at that point which is arranged on the small wheel 20 when the switch-on shaft 14 is in the support position 48.
  • the gap 54 has such a large extent that the small wheel 20 can rotate freely in relation to the large wheel 16 in the support position 48.
  • FIG 3 shows part of the large wheel 16 with the gap 54 of the toothing 52 and the small wheel 20 enlarged.
  • the flanks 56 and 58 of the teeth 60 of the small wheel 20 abut one another radially on the outside in an edge 62 running parallel to the axis of rotation 20 ′.
  • the small wheel 20 meshing with the teeth 52 is driven by the drive motor 22 in the drive direction A, whereby the large wheel 16 is rotated in the direction D.
  • the loaded flank 56 of the teeth 60 of the small wheel 20, seen in the drive direction A has an involute shape up to the edge 62.
  • the flank 58 of the teeth 60 which is unloaded when the closing spring 28 is tensioned and seen in the drive direction A has a flank plane 64 which abuts the flank 56 at the edge 62 and by an angle with respect to a radial straight line 66 through the center of the tooth 60 concerned ⁇ is preferably inclined at 45 °.
  • the flank 58 is adjacent to the flank plane 64 the remaining part of an involute up to bottom 68.
  • the small wheel 20 shown in FIG. 3 is made from a commercially available toothed wheel with involute teeth.
  • a portion 70, indicated by dash-dotted lines, is removed from each tooth, preferably by grinding, when forming the flank plane 64.
  • the resulting edge 62 is located in the region of the transition of the flank 56 into the tangential end face 70 'of the involute toothing.
  • the toothing 52 of the large wheel 16 also has an involute shape, with a flat flank part 74, also preferably by grinding, being formed on the first tooth 72 trailing in the direction of rotation D of the gap 54, so that the flanks 76 and 78 of this tooth 72 are in a common shape Butt axis 14 'parallel tooth edge 80.
  • the flank 76 leading in the direction of rotation D has an involute shape up to the tooth edge 80.
  • the flat flank part 74 of the trailing flank 78 abuts against the flank 76, the flat flank part 74 being inclined at an angle ⁇ by approximately 60 ° to a radial straight line 72 ′ through the center of the tooth 72.
  • a gearwheel with involute teeth can also be used in the manufacture of the large wheel 16.
  • the number of teeth required to form the gap 54 is removed by grinding.
  • the flat flank part 74 is formed on the tooth 72.
  • a flat flank part 74 is also preferably formed on the second tooth 84 trailing the gap 54, as described above with reference to tooth 72.
  • the large wheel is driven in the direction of rotation D by means of the drive motor 22 via the reduction gear 24 and the small wheel 20 meshing with the teeth 52 of the large wheel 16 to tension the switch-on spring 28.
  • the tensioned closing spring 28 also drives the closing shaft 14 in the direction of rotation D.
  • the support roller 32 from running on the pawl 36 which is in the rest position.
  • the small wheel 20 disengages from the toothing 52 of the large wheel 16 because the gap 54 has moved into the area of the small wheel 20.
  • the pawl device 34 is loaded only by the force generated by the closing spring 28. As a result of the close to the dead center position 44 support layer 48, this support force is small even when the closing spring 28 is tensioned with a large force. All this allows the pawl device 34 to be dimensioned for low forces. The resulting small mass of the pawl device 34 allows the reaction time of the spring drive 10 to be reduced. An additional load on the pawl device 34 by the driven or leaking small wheel 20 is avoided. For the sake of completeness, it should be mentioned that the drive motor 22 is switched off when the switch-on spring 28 is tensioned via generally known switching means.
  • the closing spring 28 accelerates the closing shaft 14 in the direction of rotation D.
  • the first tooth 72 following the gap 54 runs Large wheel 16 on the flank 58 of the tooth 60 of the small wheel 20 protruding rearmost into the movement path of the tooth 72, viewed in the direction of rotation A, whereby this is accelerated and meshes with the toothing 52 of the large wheel 16.
  • flank 58 of the teeth 60 of the small wheel 20 ensures that the leading flank 76 of the tooth 72 always acts on a region of the flank 58 which is approximately parallel to the flank, regardless of the rotational position of the small wheel 20 76 runs or encloses a very small acute angle with it.
  • the flank part 74 prevents a tooth 60 of the small wheel 20 from blocking the pair of wheels 18 against the tooth 72, since its flank part 74 is approximately parallel to the radially outer end region of the flank 56 of the tooth 60 in question of the small wheel 20 runs.
  • the design of the large wheel 16, in which the first tooth 72 following the gap is designed to be pushed back in the radial direction, ensures a smooth, jerk-free intermeshing of the toothing 52 of the large wheel 16 with the small bike 20.
  • the closing shaft 14 is brought back into the rest position 50 while turning the small wheel 20 and turning on the circuit breaker 12.
  • the roller lever 42 is non-rotatably seated on a drive shaft 86 which is also rotatably mounted on the frame 30, the longitudinal axis 86 'of which runs parallel to the axis 14' and which can be pivoted from a switch-off position "O" shown in solid lines to a switch-on position "I" and back again.
  • An output lever 88 which is seated in a rotationally fixed manner on the drive shaft 86, is dash-dotted indicated linkage 90 connected to the moving switching contact piece 12 'of the circuit breaker 12.
  • a switch-off spring 92 designed as a compression spring is supported on the frame 30, the other end of which cooperates with a switch-off chain 94 which is guided around a deflection wheel 96 which is fixedly mounted on the frame 30 to a switch-off lever 98 which is seated in a rotationally fixed manner on the drive shaft 86.
  • the switch-off lever 98 on which the switch-off chain 94 is articulated, is in the switch-on position "I" of the drive shaft 86 in a position approximately at right angles to the switch-off chain 94, whereas the switch-off lever 98 in switch-off position "O" and the switch-off chain 94 enclose an obtuse angle in this way that the switch-off spring 92 holds the drive shaft 86 in the switch-off position "O", which is defined by a stop in a brake element 100, against which the brake piston 100 'connected to the drive shaft 86 via a brake lever 102 bears in the switch-off position "0".
  • a switch-off pawl device 104 is arranged on the frame 30, which is of the same design as the pawl device 34, but cooperates with a support lever 106 which is seated on the drive shaft 86 in a rotationally fixed manner. If the drive shaft 86 is in the switch-on position "I", the support lever 106 is supported against the force of the switch-off spring 92 on the switch-off pawl 108, which, driven by an electrical switch-off magnet 110, releases the drive shaft 86 to switch off the circuit breaker 12.
  • the cam track 40 ' has a first section 114 with a radius increasing counter to the direction of rotation D.
  • This first section 114 extends over an angular range that is slightly smaller than the angle through which the switch-on shaft 14 travels from the support position 48 into the rest position 50 when it is switched on. In this rotation range of the switch-on shaft 14, the first section 114 cooperates with the roller lever 42 in order to pivot the drive shaft 86 from the switch-off position "O" to the switch position "I".
  • the first section 114 is followed by an abruptly falling second section 116 which, with the switch-on shaft 14 in the rest position 50, allows the roller 112 to move from the switch-on position "I" to the switch-off position "O" without touching the cam disk 40. to move.
  • the second section 116 is followed by a third section 118, which extends as far as the first section 114 and which runs approximately coaxially to the axis 14 'and has a radius such that when the switch-on shaft 14 is rotated from the rest position 50 in the support position 48, the drive shaft 86, which may be in the off position "O", remains in its rotational position.
  • the drive shaft 86 Shortly before the switch-on shaft 14 reaches the rest position 50, the drive shaft 86 is pivoted into the switch-on position "I” and the support lever 106 is gripped by the switch-off pawl device 104, so that the drive shaft 86 remains in the switch-on position "I” when the first section 114 is off Roll 112 has expired and the switch-on shaft 114 is in the rest position 50.
  • the circuit breaker 12 that is switched on can be switched off at any time by energizing the opening magnet 110, since when the drive shaft 86 was turned on, the opening spring 92 was also tensioned and its energy is now available for switching off.
  • the drive motor 22 is switched on in order to rotate the switch-on shaft 14 via the meshing pair of wheels 18 from the rest position 50 beyond the dead center position 44 and to simultaneously tension the switch-on spring 28, so that after the lift has taken place the switch-on shaft 14 is again in the support position 48 ready for the next switch-on.
  • the drive motor 22 is switched off again, which, now that the pair of wheels 18 is disengaged, can run out without stressing the pawl device 34. Is caused by excitation of the Switch-off pawl device 104 of the circuit breaker 12 driven by the switch-off spring 92 is switched off, the spring drive 10 is immediately ready for reclosing the circuit breaker and simultaneously tensioning the switch-off spring 92.
  • the energy stored in the closing spring 28 is dimensioned such that after the circuit breaker 12 is switched on and the opening spring 92 is simultaneously tensioned, a sufficient excess of energy remains to ensure that the rest position 50 is reached or exceeded.
  • any excess energy is recuperated in the closing spring. It is therefore necessary to connect the small wheel 20 to the reduction gear 24 via a freewheel acting in the drive direction A, so that the drive motor 22 and the reduction gear 24 are operatively connected only for driving the closing shaft 14 and tensioning the closing spring 28. If the large wheel 16 drives the small wheel 20 during a switch-on, it is decoupled from the drive motor 22 and reduction gear 24, so that only the small wheel 20 can be synchronized and moved with the large wheel 16, which leads to small forces due to the low mass .
  • the spring force drive 10 according to the invention is particularly suitable for driving medium and voltage switching devices.
  • the teeth 60, 72, 84 can be removed and chamfered by grinding.
  • the teeth 60 of the small wheel 20 and the first and possibly second tooth 72, 84 of the large wheel 16 trailing the gap 54 after the beveling, i. Production of the flank plane 64 or the flat flank part 74, hardened by the surface layer.
  • the pair of wheels 18 consists of spur gears. It is of course also conceivable to use different types of gears.

Landscapes

  • Mechanisms For Operating Contacts (AREA)
  • Gear Processing (AREA)
  • Gears, Cams (AREA)
  • Arrangement And Mounting Of Devices That Control Transmission Of Motive Force (AREA)
  • Push-Button Switches (AREA)
  • Vehicle Body Suspensions (AREA)
  • Electronic Switches (AREA)
EP93117797A 1993-11-03 1993-11-03 Federantrieb für ein Schaltgerät Expired - Lifetime EP0651409B1 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
DE59307350T DE59307350D1 (de) 1993-11-03 1993-11-03 Federantrieb für ein Schaltgerät
EP93117797A EP0651409B1 (de) 1993-11-03 1993-11-03 Federantrieb für ein Schaltgerät
AT93117797T ATE158105T1 (de) 1993-11-03 1993-11-03 Federantrieb für ein schaltgerät
US08/328,650 US5595287A (en) 1993-11-03 1994-10-25 Spring drive for a switching apparatus
JP29583494A JP3605620B2 (ja) 1993-11-03 1994-11-04 スイッチ装置用のばね駆動装置及びこれに使用する歯車の製造方法

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP93117797A EP0651409B1 (de) 1993-11-03 1993-11-03 Federantrieb für ein Schaltgerät

Publications (2)

Publication Number Publication Date
EP0651409A1 EP0651409A1 (de) 1995-05-03
EP0651409B1 true EP0651409B1 (de) 1997-09-10

Family

ID=8213391

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93117797A Expired - Lifetime EP0651409B1 (de) 1993-11-03 1993-11-03 Federantrieb für ein Schaltgerät

Country Status (5)

Country Link
US (1) US5595287A (ja)
EP (1) EP0651409B1 (ja)
JP (1) JP3605620B2 (ja)
AT (1) ATE158105T1 (ja)
DE (1) DE59307350D1 (ja)

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Publication number Priority date Publication date Assignee Title
US5944305A (en) * 1997-01-30 1999-08-31 Canon Kabushiki Kaisha Drive transmitting device, sheet feeding device and image forming apparatus
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
US6160234A (en) * 1999-04-29 2000-12-12 Eaton Corporation Reduced drag ratchet
FR2805921B1 (fr) * 2000-03-02 2002-11-29 Alstom Dispositif pour mecanisme de commande d'un appareillage electrique et mecanisme de commande equipe d'un tel dispositif
FR2846779B1 (fr) * 2002-10-30 2005-01-28 Alstom Disjoncteur comprenant un ensemble de commande et une chambre de coupure, son procede d'assemblage et organe auxiliaire pour cet assemblage
WO2005034156A1 (de) * 2003-09-13 2005-04-14 Abb Technology Ag Vorrichtung zur betätigung eines elektrischen schaltgerätes
US7581463B2 (en) * 2004-07-30 2009-09-01 Xerox Corporation Gear modification that enables direct off-center engagement
FR2919957B1 (fr) 2007-08-08 2009-10-30 Areva T & D Ag Dispositif de commutation de type a tois phases sous enveloppe metallique a encombrement et forces de trasmission par phase reduits
FR2925210B1 (fr) 2007-12-17 2010-01-15 Areva T&D Ag Commande compacte pour appareillage electrique moyennes et hautes tensions
FR2925211B1 (fr) 2007-12-17 2010-01-15 Areva T & D Ag Commande compacte et robuste pour appareillage electrique moyennes et hautes tensions
CN102148101B (zh) * 2011-04-20 2013-10-09 常熟开关制造有限公司(原常熟开关厂） 转换开关装置
CN102867663B (zh) * 2012-09-24 2014-12-24 中国西电电气股份有限公司 一种断路器弹簧操动机构的齿轮传动系统的离合装置
CN103996565A (zh) * 2013-02-20 2014-08-20 张亚宇 一种高压断路器的弹簧操作机构
FR3046260B1 (fr) * 2015-12-29 2018-07-27 Systemes Moteurs Dispositif de transmission de mouvement par engrenage et systeme d'actionnement le comprenant
DE102016214544B4 (de) * 2016-08-05 2020-01-09 Siemens Aktiengesellschaft Getriebe zwischen einem bewegbaren Schaltkontakt und einem Antrieb eines Leistungsschalters sowie ein Leistungsschalter mit einem solchen Getriebe
CN112201490B (zh) * 2020-09-25 2023-07-18 国网山东省电力公司烟台供电公司 一种用于柱上开关电动操作绝缘杆

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US3072763A (en) * 1960-02-15 1963-01-08 Allis Chalmers Mfg Co Spring actuated contact opening and closing mechanism
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JPS5590752A (en) * 1978-12-28 1980-07-09 Isuzu Motors Ltd Asymmetric gear apparatus
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FR2558986B1 (fr) * 1984-01-30 1986-11-21 Merlin Gerin Dispositif de commande d'un disjoncteur electrique
US4653340A (en) * 1986-03-03 1987-03-31 Pitney Bowes Inc. Beveled spur gear
JPH0693338B2 (ja) * 1987-05-13 1994-11-16 三菱電機株式会社 遮断器の操作機構

Also Published As

Publication number Publication date
US5595287A (en) 1997-01-21
JPH07211176A (ja) 1995-08-11
ATE158105T1 (de) 1997-09-15
EP0651409A1 (de) 1995-05-03
JP3605620B2 (ja) 2004-12-22
DE59307350D1 (de) 1997-10-16

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