EP0917168B1 - 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
EP0917168B1
EP0917168B1 EP98402807A EP98402807A EP0917168B1 EP 0917168 B1 EP0917168 B1 EP 0917168B1 EP 98402807 A EP98402807 A EP 98402807A EP 98402807 A EP98402807 A EP 98402807A EP 0917168 B1 EP0917168 B1 EP 0917168B1
Authority
EP
European Patent Office
Prior art keywords
wheel
tooth
retractable
gap
teeth
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
EP98402807A
Other languages
English (en)
French (fr)
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EP0917168A1 (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 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 AG filed Critical GEC Alsthom 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

  • a shape of the teeth of said toothed pinion whose flanks join, radially outward, on a common edge and have, on the leading flank, an involute shape and, on the opposite flank, a flank plane starting from the edge and which is inclined relative to a radial straight line passing through the middle of the tooth, and, a shape of the tooth of the large toothed wheel which occurs after the release, in said predetermined direction, the sides of which join radially outward on a common edge and which has an inclined plane in its upper zone adjacent to the fish bone.
  • 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 beyond 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.
  • This goal is achieved by the mechanism as defined in the preamble and characterized in that said first clearance provided at the periphery of said large the toothed wheel is followed, in said predetermined direction of rotation, by a first radially retractable tooth against the constraint of a spring of compression, in that said first retractable tooth is followed, in said predetermined direction of rotation, from a second clearance provided at the periphery of this large gear wheel, generated by a discontinuity complementary to the teeth, this second clearance extending over at minus two gear steps, and in that the tooth that immediately follows said second clearance is a second radially retractable tooth against the stress of a compression spring.
  • said second clearance extends over a length slightly less than an integer 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 zone 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 outward, 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 zone 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 a drive pinion 21 integral 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 where the interlocking spring is attached 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 angular 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 41 a and 41 b which correspond respectively to the positions l and O of the actuating lever 31.
  • the pawl 36 ensures the locking lever 35 is locked in a position which corresponds to 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 form and on the opposite flank, a plane starting from the edge and which is inclined relative 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 having tendency to push tooth 53a radially to the outside of the wheel.
  • a stop plate 57a is fixed to the bottom of the first clearance 52a so partially closing the recess 55a.
  • This stop plate is fixed to the 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 a number whole gear pitch, 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 can 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.
  • Figures 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.
  • Figures 4C and 4D illustrate the teeth of the pinion and those of the big gear have relative positions which are illustrated by Figures 4C and 4D.
  • Figure 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)

Claims (9)

  1. Feder-Antriebsmechanismus (10) für eine Leistungsschaltvorrichtung, insbesondere für einen Leistungsschalter für mittlere und hohe Spannung und insbesondere einen Unterbrecher-Schalter, wobei dieser Mechanismus umfasst:
    eine Schaltfeder (15),. die exzentrisch mit einer Schaltwelle (11) gekoppelt ist, welche frei um ihre Achse drehbar ist, wobei die Feder so angeordnet ist, dass sie einerseits die Schaltwelle in einer vorbestimmten Drehrichtung (A) antreiben kann, um ein Einschalten der Schaltvorrichtung zu bewerkstelligen, und andererseits ein großes, an der Schaltwelle (11) angebrachtes Zahnrad (13) sowie ein Zahnritzel (19), das mit dem großen Zahnrad in Eingriff steht und mit einem Antriebselement (23) zum Antreiben des großen Zahnrads über das Zahnritzel und die Schaltwelle in der vorbestimmten Richtung, um die Schaltfeder in Hinblick auf das Einschalten der Schaltvorrichtung unter Spannung zu setzen, wobei die Schaltwelle so angeordnet ist, dass sie von einer Position (16b), in der die Schaltfeder zumindest teilweise entspannt ist, über eine Totpunktposition (16a), in der die Schaltfeder unter Spannung steht, hinausgeht,
    einen Klinkenmechanismus (24), der so angeordnet ist, dass er gegen das große Zahnrad (13) in einer Anlageposition, die über die Totpunktposition in der vorbestimmten Drehrichtung (A) hinausgeht, anliegt, und dass die Schaltwelle (11) für das Einschalten der Schaltvorrichtung freigegeben wird,
    eine erste Ausnehmung (52a), die am Umfang des großen Zahnrads eingebracht ist und von einer Diskontinuität in der Verzahnung (51) dieses großen Zahnrads erzeugt wird, wobei diese Ausnehmung in einer Zone der Verzahnung angeordnet ist, die sich nahe dem Zahnritzel (19) befindet, wenn die Schaltwelle gegen den Klinkenmechanismus anliegt, und
    Mittel zum Verhindern der gegenseitigen Blockierung des großen Zahnrads (13) und des Zahnritzels (19) nach der Freigabe der Schaltwelle durch den Klinkenmechanismus, wobei diese Mittel umfassen:
    eine Form der Zähne (50) des Zahnritzels (19), deren Flanken sich radial nach außen auf einem gemeinsamen Grat verbinden und an der Angriffs- bzw. Anstiegsflanke eine Evolventenform und an der entgegengesetzten Flanke eine Flankenebene aufweist, die von dem Grat ausgeht und in Bezug auf eine durch die Mitte des Zahns passierende radiale Gerade geneigt ist, und
    eine Form des Zahns des großen Zahnrads (13), die sich nach der Ausnehmung in der vorbestimmten Richtung präsentiert, deren Flanken sich radial nach außen auf einem gemeinsamen Grat verbinden, und die eine geneigte Ebene in ihrer oberen Zone angrenzend an den Grat umfasst,
       dadurch gekennzeichnet, dass der ersten Ausnehmung (52a), die am Umfang des großen Zahnrads (13) eingebracht ist, in der vorbestimmten Drehrichtung (A) ein erster Zahn (53a) folgt, der gegen die Spannung einer Druckfeder (56a) radial zurückziehbar ist, dass dem ersten zurückziehbaren Zahn in der vorbestimmten Drehrichtung (A) eine zweite Ausnehmung (52b) folgt, die am Umfang dieses großen Zahnrads (13) eingebracht ist, und die durch eine komplementäre Diskontinuität der Verzahnung erzeugt ist, wobei diese zweite Ausnehmung sich mindestens über zwei Zahnteilungen erstreckt, und dass der Zahn, der unmittelbar der zweiten Ausnehmung (52b) folgt, ein zweiter Zahn (53b) ist, der gegen die Spannung der Druckfeder (56b) zurückziehbar ist.
  2. Mechanismus nach Anspruch 1, dadurch gekennzeichnet, dass sich die zweite Ausnehmung (52b) über eine Länge erstreckt, die geringfügig kleiner ist als eine ganze Zahl von Zahnteilungen, und dass der zweite zurückziehbare Zahn (53b) Flanken aufweist, die sich radial nach außen auf einem gemeinsamen Grat verbinden und die eine Ebene umfassen, die in ihrer oberen Zone angrenzend an den Grat geneigt ist.
  3. Mechanismus nach Anspruch 2, dadurch gekennzeichnet, dass sich die zweite Ausnehmung (52b) über eine Länge erstreckt, die um etwa 1/6 einer Zahnteilung geringer ist als eine ganze Zahl an Zahnteilungen.
  4. Mechanismus nach Anspruch 3, dadurch gekennzeichnet, dass die zweite Ausnehmung sich über eine Länge erstreckt, die in etwa gleich 2 (5/6) Zahnteilungen ist.
  5. Mechanismus nach Anspruch 1, dadurch gekennzeichnet, dass dem zurückziehbaren Zahn (53b) in der vorbestimmten Drehrichtung (A) eine dritte Ausnehmung (52c) folgt, die sich über mindestens zwei Zahnteilungen erstreckt.
  6. Mechanismus nach Anspruch 5, dadurch gekennzeichnet, dass der dritten Ausnehmung (52c) ein Zahn (60) folgt, dessen Flanken sich radial nach außen auf einem gemeinsamen Grat verbinden und der eine geneigte Ebene in seiner oberen Zone angrenzend an den Grat aufweist.
  7. Mechanismus nach Anspruch 1, dadurch gekennzeichnet, dass der ersten Ausnehmung (52a) in der vorbestimmten Drehrichtung (A) mehrere axial gegen die Spannung einer Feder zurückziehbare Zähne folgen, wobei jedem dieser zurückziehbaren Zähne in der vorbestimmten Drehrichtung (A) eine Ausnehmung folgt, die sich über mindestens zwei Zahnteilungen erstreckt.
  8. Mechanismus nach Anspruch 7, dadurch gekennzeichnet, dass die zurückziehbaren Zähne und der erste nichtzurückziehbare Zahn nach dem letzten zurückziehbaren Zahn in der vorbestimmten Drehrichtung (A) Flanken aufweisen, die sich radial nach außen an einem gemeinsamen Grat verbinden und die eine geneigte Ebene in ihrer oberen Zone angrenzend an den Grat aufweisen.
  9. Mechanismus nach Anspruch 8, dadurch gekennzeichnet, dass die zurückziehbaren Zähne von den benachbarten zurückziehbaren Zähnen durch eine Ausnehmung getrennt sind, die sich über eine Länge erstreckt, die geringfügig kleiner ist als eine ganze Zahl von Zahnteilungen.
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 EP0917168A1 (de) 1999-05-19
EP0917168B1 true EP0917168B1 (de) 2004-10-06

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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)

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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
FR2840726B1 (fr) * 2002-06-06 2004-11-12 Alstom Commande mecanique a ressort pour disjoncteur haute ou moyenne tension, comprenant une roue dentee cooperant avec un pignon
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
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
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

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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
JPH0693338B2 (ja) * 1987-05-13 1994-11-16 三菱電機株式会社 遮断器の操作機構
EP0320614B1 (de) * 1987-12-14 1992-09-09 Sprecher Energie AG Federkraftspeicherantrieb für einen Hochspannungsschalter
ATE158105T1 (de) * 1993-11-03 1997-09-15 Gec Alsthom T & D Ag Federantrieb für ein schaltgerät
DE59304319D1 (de) * 1993-12-13 1996-11-28 Gec Alsthom T & D Ag Antriebsvorrichtung für einen Leistungsschalter

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
EP0917168A1 (de) 1999-05-19
CN1230758A (zh) 1999-10-06
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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