EP0917168A1 - Federkraftantrieb für ein Schaltgerät, insbesondere für einen Lastschalter - Google Patents

Federkraftantrieb für ein Schaltgerät, insbesondere für einen Lastschalter Download PDF

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Publication number
EP0917168A1
EP0917168A1 EP98402807A EP98402807A EP0917168A1 EP 0917168 A1 EP0917168 A1 EP 0917168A1 EP 98402807 A EP98402807 A EP 98402807A EP 98402807 A EP98402807 A EP 98402807A EP 0917168 A1 EP0917168 A1 EP 0917168A1
Authority
EP
European Patent Office
Prior art keywords
tooth
retractable
clearance
predetermined direction
gear
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
EP98402807A
Other languages
English (en)
French (fr)
Other versions
EP0917168B1 (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
Publication of EP0917168A1 publication Critical patent/EP0917168A1/de
Application granted granted Critical
Publication of EP0917168B1 publication Critical patent/EP0917168B1/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
    • H01H3/3005—Charging means
    • 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

Definitions

  • European patent No. 0 294 561 A2 describes a drive mechanism of a similar type, coupled to a disconnector and the first tooth of the large gear wheel, which is located immediately after the release, is radially retractable against the stress of a compression spring. Yes this tooth abuts against the top of a tooth of the toothed pinion, at the beginning of the latching process, it retracts radially by compressing the spring associated with it. As a result, this tooth can slide without generating blocking on the edge of the corresponding tooth of the toothed pinion. When she has passed this edge, it engages in the hollow which follows the tooth of the pinion toothed.
  • the present invention proposes to remedy all of these disadvantages and remove the risk of malfunctions of these known mechanisms offering an effective solution, simple to carry out, little expensive and which can also be adapted by a transformation appropriate, to mechanisms of this type that are already in use.
  • said second clearance extends over a length slightly less than a whole number of gear steps and said second retractable tooth has flanks which join radially towards the exterior, on a common edge, and which have an inclined plane in its upper area adjacent to the edge.
  • said second clearance extends over a length approximately 116 less than a gear step to an integer gear pitch and preferably over an approximate length equal to 2 (5/6) of gear pitch.
  • said second tooth retractable is followed, in said predetermined direction of rotation, by a third clearance which extends over at least two gear pitches.
  • said third clearance is followed by a tooth whose the flanks join radially outwards, on a common edge, and which has an inclined plane in its upper zone adjacent to the edge.
  • said first clearance is followed, in the predetermined direction of rotation, of n teeth retractable axially against the spring stress, each of these retractable teeth being followed, in said predetermined direction of rotation, by a clearance extending over at least two gear steps.
  • said retractable teeth and the first non-retractable tooth following the last retractable tooth, in the predetermined direction of rotation have flanks which join radially towards the exterior, on a common edge, and which have an inclined plane in their upper area adjacent to the edge.
  • Said retractable teeth are advantageously separated from the two teeth neighboring retractable by a clearance extending over a length slightly less than a whole number of gear steps.
  • the spring drive mechanism 10 as shown intended to be coupled to a switching device, comprises a interlocking shaft 11, freely rotatable about its axis 12 and bearing on the one hand a large toothed wheel 13 and on the other hand a cam 14 whose function will be explained later.
  • An engagement spring 15, consisting by a tension spring, is coupled to the large toothed wheel 13 at a point attachment 16, via a chain 17, or any other means suitable, which passes over an angular pulley 18 in the example represented.
  • the large toothed wheel 13 meshes with a toothed pinion 19 which is coupled via a gear train 20 to an integral drive pinion 21 an output shaft 22 of a drive motor 23.
  • the engagement spring 15 exerts a traction on the chain 17 and causes the rotation of the large gear 13, in the predetermined direction indicated by arrow A, the attachment point 16 passing from a standby position slightly downstream from neutral 16a (in the predetermined direction of rotation A of the large toothed wheel), at a final position corresponding to a relaxation point 16b which is diametrically opposite to neutral 16a.
  • the engine 23 takes over to drive the drive shaft 11 rotating in the predetermined direction of rotation A. This movement is continues until the point of attachment of the interlocking spring again slightly exceeds the neutral point 16a and where this spring is armed.
  • a ratchet mechanism 24 which comprises a ratchet 25 actuated by an electromagnet 26 and a stop 27 mounted on one of the faces of the large wheel tooth 13, which cooperates with the pawl 25 to stop this wheel in the desired waiting position.
  • the mechanism 10 comprises a main shaft 30 which in particular carries an actuating lever 31 of a lever (not shown) of the switching device, a coupling lever 32 of this shaft to a trigger spring 33, a roller carrier lever 34 which carries a cam follower roller 34a which cooperates with the cam 14, a locking lever 35 which cooperates with a pawl 36 actuated by an electromagnet 37 and a braking lever which is coupled to a brake 38 constituted for example by an oil jack or the like.
  • the trigger spring 33 is preferably identical or similar to the engagement spring 15 and is connected by means of a chain 39 guided by an angle deflection pulley 40 to the coupling lever 32.
  • the cam follower roller 34a is resting against the cam 14 mounted on the engagement shaft 11.
  • This cam controls the movement of the lever 34 between two positions 41a and 41b which correspond respectively to the positions l and O of the actuating lever 31.
  • the pawl 36 ensures the locking of the locking lever 35 in a position which corresponds to the position l of the actuating lever 31.
  • Figure 2 shows, on an enlarged scale, part of the Ferris wheel toothed 13 and the toothed pinion 19.
  • the teeth 50 of the pinion 19 have a particular geometry which corresponds to a point size.
  • the flanks of these teeth join radially outward on an edge common and present, on the flank of attack, a developing and on the opposite flank, a plane starting from the edge and which is inclined with respect to a radial straight line passing through the middle of the corresponding tooth.
  • the large toothed wheel 13 comprises, in the predetermined direction of rotation A, a discontinuity in the toothing 51, this discontinuity generating a first clearance 52a which constitutes an area without teeth.
  • a first tooth retractable 53a is arranged in this clearance. It is integral with a partially hollowed socket 54a which is housed in a recess 55a substantially cylindrical, formed in the thickness of the large gear.
  • a compression spring 56a is mounted in the closed space delimited between the cavity of the hollowed-out sleeve 54a and the recess 55a of the wheel, this spring tending to push tooth 53a radially outward from the wheel.
  • a stop plate 57a is fixed to the bottom of the first clearance 52a so as to partially close the recess 55a.
  • This stop plate is fixed by means of at least one and preferably two locking screws 58a. Thanks to this assembly, the tooth 53a can partially retract inside of recess 55a, contrary to the constraint exerted by the spring of compression 56a.
  • the large wheel 13 has a second clearance 52b which is generated by a discontinuity complementary to the toothing 51 of this wheel.
  • This second release extends over at least two gear pitches. According to one embodiment preferred, this clearance extends over a length slightly less than one whole number of gear steps and advantageously on a whole number, for example three gear steps reduced by 1/6 gear step.
  • the tooth 53b of the toothing of the large toothed wheel, which follows said second clearance 52b, is also retractable under the constraint of a spring compression 56b.
  • the tooth 60 which follows the second retractable tooth 53b, after a third clearance 52c which extends over a length equal to one whole number of gear steps, includes, as well as each of the teeth retractable, sides which join radially outwards on a common edge.
  • the flank opposite the leading flank has an inclined plane in its upper part adjacent to the edge of the tooth.
  • the two retractable teeth 53a and 53b may be prominent compared to the other teeth 51 of the teeth of the large gear wheel, this which has the advantage of reducing the probability that the tip of said others teeth comes into contact with the tip of a pinion tooth 19.
  • Figures 3A to 3H illustrate what happens in the absence of a collision between the teeth 50 of the pinion 19 and the teeth of the large gear wheel 13.
  • the instant initial is represented by figures 3A and 3B, this last figure representing the coming into contact of a tooth of the pinion 19 and the first retractable tooth 53a of the large gear wheel 13.
  • Figures 3C and 3D show the relative position of the sprocket teeth relative to the teeth 51 missing, shown in broken lines, of the large gear wheel 13.
  • FIG. 3E illustrates in broken lines the primitive shape of a tooth 61 pinion 19 not cut appropriately. We see in this figure that if this shape were maintained, it would automatically cause a collision with the second retractable tooth 53b of the large toothed wheel.
  • the following figures 3F, 3G and 3H illustrate the relative positions of the teeth 50 of the pinion 19 and 53a, 53b and 60 of the large gear 13.
  • FIGS 4A to 4H illustrate what happens when the tip of a tooth 50 pinion 19 meets the tip of the retractable tooth 53a of the ferris wheel toothed 13.
  • the initial instant of this contact between the two teeth 50 and 53a is shown in Figure 4B.
  • Point-to-point contact causes tooth retraction 53a.
  • FIG. 4E illustrates the contact between a teeth 50 of the pinion 19 with the second retractable tooth 53b.
  • the number of retractable teeth is not limited to two and may extend to three or n axially retractable teeth against the constraint of a thrust spring, each of these teeth being followed by a clearance as defined above.

Landscapes

  • Transmission Devices (AREA)
  • Gears, Cams (AREA)
  • Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)
  • Gear Transmission (AREA)
  • Push-Button Switches (AREA)
  • Lock And Its Accessories (AREA)
  • Mechanisms For Operating Contacts (AREA)
EP98402807A 1997-11-13 1998-11-13 Federkraftantrieb für ein Schaltgerät, insbesondere für einen Lastschalter Expired - Lifetime EP0917168B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9714223 1997-11-13
FR9714223A FR2770929B1 (fr) 1997-11-13 1997-11-13 Mecanisme d'entrainement a ressort pour un appareil de commutation, en particulier un disjoncteur

Publications (2)

Publication Number Publication Date
EP0917168A1 true EP0917168A1 (de) 1999-05-19
EP0917168B1 EP0917168B1 (de) 2004-10-06

Family

ID=9513322

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98402807A Expired - Lifetime EP0917168B1 (de) 1997-11-13 1998-11-13 Federkraftantrieb für ein Schaltgerät, insbesondere für einen Lastschalter

Country Status (9)

Country Link
US (1) US6066820A (de)
EP (1) EP0917168B1 (de)
JP (1) JP4143191B2 (de)
CN (1) CN1096092C (de)
AT (1) ATE279015T1 (de)
CA (1) CA2251271A1 (de)
DE (1) DE69826809T2 (de)
FR (1) FR2770929B1 (de)
RU (1) RU2156004C2 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1369886A1 (de) * 2002-06-06 2003-12-10 Alstom Mechanischer Federantrieb für Hoch- oder Mittelspannungsschalter, mit einem Zahnrad/Ritzel-Getriebe
US9431186B2 (en) 2012-09-24 2016-08-30 China Xd Electric Co., Ltd Clutch device of gear transmission system of circuit breaker spring operating mechanism

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100325408B1 (ko) * 1999-10-26 2002-03-04 이종수 회로차단기용 접점개폐장치
FR2819626B1 (fr) * 2001-01-12 2003-02-21 Alstom Sectionneur a haute tension a isolation dans l'air
FR2821696B1 (fr) * 2001-03-01 2003-04-25 Alstom Disjoncteur haute tension ayant une commande a ressorts avec un ressort additionnel de recuperation d'energie
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
GB0502557D0 (en) * 2005-02-08 2005-03-16 Patel Hitesh D Gear means
US7319203B1 (en) * 2007-01-10 2008-01-15 Eaton Corporation Circuit interrupter and operating mechanism therefor
JP5951262B2 (ja) * 2012-01-11 2016-07-13 株式会社東芝 開閉装置および開閉装置操作機構
CN102881474B (zh) * 2012-10-15 2014-12-24 上海思源高压开关有限公司 弹簧储能控制模块及其操动机构和断路器
RU2676466C2 (ru) * 2014-10-27 2018-12-29 Хамзат Исхакович Геграев Агрегатный привод выключателя нагрузки
DE102016215888A1 (de) 2016-08-24 2018-03-01 Siemens Aktiengesellschaft Koppeleinrichtung und Verfahren zum Koppeln und Entkoppeln eines Spanngetriebes eines Leistungsschalters
DE102017122008B4 (de) * 2017-09-22 2020-11-05 Lisa Dräxlmaier GmbH Elektrischer schalter
CN110486447A (zh) * 2019-09-19 2019-11-22 广东电网有限责任公司 一种非全圆被动齿轮

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0294561A2 (de) * 1987-05-13 1988-12-14 Mitsubishi Denki Kabushiki Kaisha Antriebsmechanismus für einen Schalter
EP0651409A1 (de) * 1993-11-03 1995-05-03 GEC Alsthom T&D AG Federantrieb für ein Schaltgerät

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4095676A (en) * 1976-11-23 1978-06-20 Howe-Yin Research Co., Inc. Stored energy operation for breakers
JPS61161844U (de) * 1985-03-25 1986-10-07
EP0320614B1 (de) * 1987-12-14 1992-09-09 Sprecher Energie AG Federkraftspeicherantrieb für einen Hochspannungsschalter
DE59304319D1 (de) * 1993-12-13 1996-11-28 Gec Alsthom T & D Ag Antriebsvorrichtung für einen Leistungsschalter

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0294561A2 (de) * 1987-05-13 1988-12-14 Mitsubishi Denki Kabushiki Kaisha Antriebsmechanismus für einen Schalter
EP0651409A1 (de) * 1993-11-03 1995-05-03 GEC Alsthom T&D AG Federantrieb für ein Schaltgerät

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1369886A1 (de) * 2002-06-06 2003-12-10 Alstom Mechanischer Federantrieb für Hoch- oder Mittelspannungsschalter, mit einem Zahnrad/Ritzel-Getriebe
FR2840726A1 (fr) * 2002-06-06 2003-12-12 Alstom Commande mecanique a ressort pour disjoncteur haute ou moyenne tension, comprenant une roue dentee cooperant avec un pignon
US6809279B2 (en) 2002-06-06 2004-10-26 Alstom Spring loaded mechanical control mechanism for a circuit breaker comprising a toothed wheel cooperating with a cog wheel
US9431186B2 (en) 2012-09-24 2016-08-30 China Xd Electric Co., Ltd Clutch device of gear transmission system of circuit breaker spring operating mechanism

Also Published As

Publication number Publication date
CA2251271A1 (fr) 1999-05-13
FR2770929B1 (fr) 2000-01-28
DE69826809T2 (de) 2005-11-17
RU2156004C2 (ru) 2000-09-10
CN1230758A (zh) 1999-10-06
EP0917168B1 (de) 2004-10-06
JPH11224573A (ja) 1999-08-17
US6066820A (en) 2000-05-23
CN1096092C (zh) 2002-12-11
FR2770929A1 (fr) 1999-05-14
DE69826809D1 (de) 2004-11-11
JP4143191B2 (ja) 2008-09-03
ATE279015T1 (de) 2004-10-15

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