EP0651409B1 - Spring drive for switchgear - Google Patents

Spring drive for switchgear 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)
French (fr)
Other versions
EP0651409A1 (en
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 EP93117797A priority Critical patent/EP0651409B1/en
Priority to DE59307350T priority patent/DE59307350D1/en
Priority to AT93117797T priority patent/ATE158105T1/en
Priority to US08/328,650 priority patent/US5595287A/en
Priority to JP29583494A priority patent/JP3605620B2/en
Publication of EP0651409A1 publication Critical patent/EP0651409A1/en
Application granted granted Critical
Publication of EP0651409B1 publication Critical patent/EP0651409B1/en
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.

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  • 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)

Abstract

The spring drive for an electrical switching device has a connection shaft to which a connection spring is eccentrically coupled and on which the large wheel (16) is seated in a rotationally fixed manner. A small wheel (20), which is driven in order to stress the connection spring, interacts with said large wheel (16). The tooth system (52) of the large wheel (16) has a gap (54) in order to decouple the pair of wheels (18) when the connection spring is stressed. In order to connect the switching device, the large wheel (16) is driven in the rotation direction (D), as a result of which the tooth system (52) engages with the small wheel (20) again. In order to prevent the wheels locking up when they engage in one another, the teeth (60) of the small wheel (20) are designed in such a manner that the edges (56,58) abut against one another, radially on the outside, at a common edge (62). <IMAGE>

Description

Die vorliegende Erfindung betrifft einen Federantrieb für ein Schaltgerät, insbesondere einen Leistungsschalter für Mittel- und Hochspannung, gemäss dem Oberbegriff des Anspruchs 1.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.

Ein Federantrieb dieser Art ist aus der EP-A-0 294 561 bekannt. Auf einer drehbar gelagerten Einschaltwelle sitzt drehfest ein Grossrad, an dem bezüglich der Drehachse der Einschaltwelle exzentrisch eine Lasche angelenkt ist, die andernends mit einem Hebel verbunden ist, der seinerseits mit einer als Torsionsstab ausgebildeten Einschaltfeder zusammenwirkt. Zum Spannen der Einschaltfeder kämmt das Grossrad mit einem Kleinrad, das von einem Antriebsorgan angetrieben ist, um die Einschaltwelle aus einer Ausgangslage, in der die Einschaltfeder mindestens teilweise entspannt ist, über eine Totpunktlage, in welcher die Wirklinie der Lasche durch die Drehachse verläuft, und in welcher die Einschaltfeder gespannt ist, in Drehrichtung anzutreiben. Eine Klinkenvorrichtung stützt die Einschaltwelle entgegen der Wirkung der gespannten Einschaltfeder in einer Abstützlage ab, die in Drehrichtung bezüglich der Totpunktlage um einen kleinen Winkel versetzt ist. Der Zahnkranz des Grossrades weist an jener Stelle eine Zahnlücke auf, die bei an der Klinkenvorrichtung abgestützter Einschaltwelle beim Kleinrad angeordnet ist. Dies um zu verhindern, dass das Grossrad bei gespannter Einschaltfeder vom Kleinrad her noch weiter angetrieben wird und dadurch zusätzlich die Klinkenvorrichtung belastet. Zum Einschalten des Schalters gibt die Klinkenvorrichtung die Einschaltwelle frei, welche unter der Kraft der Einschaltfeder in Drehrichtung angetrieben wird. Dabei kommt der Zahnkranz des Grossrades mit dem Kleinrad wieder in Eingriff. Um zu verhindern, dass der erste in Drehrichtung der Einschaltwelle der Lücke folgende Zahn des Grossrades auf der tangentialen Scheitelfläche eines Zahnes des Kleinrades ansteht, und so das Räderpaar am Weiterdrehen gehindert, und damit der Federantrieb blockiert wird, ist der genannte erste Zahn in radialer Richtung federnd zurückdrängbar ausgebildet. Stösst dieser Zahn zu Beginn des Einschaltens auf den Scheitel eines Zahnes des Kleinrades, kann er in Richtung zur Grossradmitte hin zurückweichen und so über die Scheitelfläche des betreffenden Zahnes des Kleinrades hinweggleiten. Er greift dann in die Lücke nach diesem Zahn des Kleinrades ein und synchronisiert so das Kleinrad mit dem Grossrad. Bei diesem bekannten Federantrieb besteht die Gefahr, dass der federnd zurückweichbar angeordnete Zahn das Kleinrad infolge Reibung mitnimmt. Der zweite der Lücke folgende ungefederte Zahn des Grossrades kann dann an der Scheitelfläche eines weiteren Zahnes des Kleinrades anstossen und so das Getriebe blockieren. Diese Gefahr ist insbesondere dann gegeben, wenn das Kleinrad mittels eines Freilaufs vom Antriebsorgan entkoppelt ist und sich deshalb sehr leicht drehen lässt. Weiter ist die Herstellung des Grossrades mit einem gefederten Zahn aufwendig.A spring drive of this type is known from EP-A-0 294 561. On a rotatably mounted switch-on shaft sits 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. To tension the closing spring, 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. To switch on of the switch, 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. In order to prevent the first tooth of the large wheel following in the direction of rotation of the engagement shaft of the gap from contacting the tangential apex surface of a tooth of the small wheel, and thus preventing the pair of wheels from turning further and thus blocking the spring drive, 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. In this known spring drive there is a risk that the tooth, which is arranged to be resiliently retractable, will take the small wheel with it as a result of friction. The second unsprung tooth of the large wheel following the gap can then abut the apex surface of another tooth of the small wheel and thus block the transmission. This danger is particularly present when the small wheel is decoupled from the drive element by means of a freewheel and can therefore be rotated very easily. The manufacture of the large wheel with a spring-loaded tooth is also complex.

Die US-Patentschrift Nr. 3,890,853 offenbart ein Getriebe zum blockierfreien Erzeugen einer periodischen Ausgangsdrehbewegung aus einer Eingangsdrehbewegung. Das angetriebene Grossrad eines Räderpaares ist als Ringrad mit einer eine Lücke aufweisenden Innenverzahnung ausgebildet. Die Flanken der Zähne des mit dem Grossrad zusammenwirkenden Kleinrades stossen radial aussen in einer gemeinsamen Kante aneinander. Der erste in Drehrichtung des Grossrades der Lücke folgende Zahn weist ein asymmetrisches spitzes Profil auf und seine Zahnhöhe ist grösser als die der übrigen Zähne des Grossrades.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.

Es ist deshalb eine Aufgabe der vorliegenden Erfindung, einen gattungsgemässen Federantrieb zu schaffen, der durch einfache Massnahmen am Blockieren gehindert ist.It is therefore an object of the present invention to provide a generic spring drive which is prevented from blocking by simple measures.

Diese Aufgabe wird bei einem gattungsgemässen Federantrieb durch die Merkmale im Kennzeichen des Anspruchs 1 gelöst.This object is achieved in a generic spring drive by the features in the characterizing part of claim 1.

Da die Flanken der Zähne des Kleinrades radial aussen in einer gemeinsamen Kante aneinanderstossen, weisen die Zähne keine tangentialen Scheitelflächen auf, an welchen der erste der Lücke des Grossrades folgende Zahn anstossen könnte. Es wird auch verhindert, dass ein Zahn des Kleinrades auf der tangentialen Scheitelfläche des ersten der Lücke des Grossrades folgenden Zahnes anstehen kann. Dieser, wenn auch wenig wahrscheinliche Fall, könnte bei vorhandener Scheitelfläche eintreten, wenn unmittelbar nach dem Spannen der Einschaltfeder, wenn das Kleinrad sich noch im Auslauf befindet, die Klinkenvorrichtung die Einschaltwelle zum Einschalten freigibt.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.

Die Reibungsverluste sind dadurch minim, dass die Zähne des zum Spannen der Einschaltfeder angetriebenen Kleinrades auf der belasteten, in Drehrichtung gesehen vorlaufenden Flanke, eine Evolventenform aufweisen. Eine zu einer radialen Geraden geneigte Flankenebene kann auf einache Art und Weise, beispielsweise durch Schleifen, hergestellt werden. Diese Ausbildungsform des Kleinrades ermöglicht die Verwendung eines handelsüblichen Zahnrades mit Evolventenverzahnung, bei dem durch Erzeugung der geneigten Flankenebene die tangentiale Scheitelfläche entfernt ist.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.

Eine weitere bevorzugte Ausbildungsform des erfindungsgemässen Federantriebs gemäss Anspruch 4 ermöglicht die Verwendung eines Grossrades mit Evolventenverzahnung, welches einzig zum Bilden der Lücke und Anbringen des geneigten ebenen Flankenteils am ersten der Lücke folgenden Zahn nachzubearbeiten ist.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.

Eine weitere ebenfalls bevorzugte Ausbildungsform des erfindungsgemässen Federantriebs ist im Anspruch 5 definiert. Sie ist in der Herstellung eher aufwendig, führt aber zu einer äusserst hohen Zuverlässigkeit des Federantriebs.Another also preferred embodiment of the spring drive according to the invention is defined in claim 5. It is rather complex to manufacture, but leads to an extremely high reliability of the spring drive.

Besonders bevorzugte Verfahren zur Herstellung des Klein- und Grossrades sind in den Ansprüchen 6 bis 8 angegeben.Particularly preferred methods for producing the small and large wheel are specified in claims 6 to 8.

Die vorliegende Erfindung wird nun anhand der in der Zeichnung dargestellten Ausführungsbeispiele näher erläutert. Es zeigen rein schematisch:

Fig. 1
in perspektivischer Darstellung stark vereinfacht, einen erfindungsgemässen Federantrieb;
Fig. 2
in Ansicht ein Räderpaar des in der Fig. 1 gezeigten Federantriebs, wobei das auf einer Einschaltwelle drehfest sitzende und mit einer Einschaltfeder verbundene Grossrad sich in Abstützlage befindet, in welcher die Einschaltfeder gespannt und die Einschaltwelle an einer Klinkenvorrichtung abgestützt ist; und
Fig. 3
gegenüber Fig. 2 vergrössert das Kleinrad in einer ersten Ausführungsform und einen Teil des Grossrades.
Der in der Fig. 1 gezeigte Federantrieb 10 für einen schematisch angedeuteten Leistungsschalter 12 weist eine in allgemein bekannter Art und Weise an einem nur andeutungsweise gezeigten Gestell 30 frei drehbar gelagerte Einschaltwelle 14, deren Drehachse mit 14' bezeichnet ist, auf. Auf ihr sitzt drehfest an einem Ende ein Grossrad 16 eines Räderpaares 18, dessen Kleinrad 20 mit einem elektrischen Antriebsmotor 22 über ein Untersetzungsgetriebe 24 verbunden ist.The present invention will now be explained in more detail with reference to the exemplary embodiments shown in the drawing. It shows purely schematically:
Fig. 1
greatly simplified in perspective view, a spring drive according to the invention;
Fig. 2
in view a pair of wheels of the spring drive shown in Figure 1, wherein the on a Einschaltwelle non-rotatably seated and connected to an engagement spring is in a support position in which the engagement spring is tensioned and the engagement shaft is supported on a ratchet device. and
Fig. 3
2, the small wheel in a first embodiment and a part of the large wheel are enlarged.
The spring drive 10 shown in FIG. 1 for a schematically indicated circuit breaker 12 has a switch-on shaft 14 which is freely rotatably mounted on a frame 30, which is only indicated, in a generally known manner, the axis of rotation of which is designated by 14 '. A large wheel 16 of a pair of wheels 18, whose small wheel 20 is connected to an electric drive motor 22 via a reduction gear 24, sits on it at one end in a rotationally fixed manner.

Am Grossrad 16 ist bezüglich der Achse 14' exzentrisch und auf der der Einschaltwelle 14 abgewandten Seite das Ende einer Kette 26 angelenkt, die um ein ebenfalls am Gestell 30 frei drehbar gelagertes Umlenkrad 27 und durch eine als Schraubendruckfeder ausgebildete Einschaltfeder 28 hindurchgeführt ist. Mit ihrem diesseitigen Ende ist die Kette 26 am freien Ende der andernends am Gestell 30 abgestützten Einschaltfeder 28 befestigt.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.

Weiter ist auf der Stirnseite des Grossrades 16 an diesem eine Stützrolle 32 drehbar gelagert, die zum Zusammenwirken mit einer am Gestell 30 angeordneten Klinkenvorrichtung 34 bestimmt ist. Diese weist eine am Gestell 30 schwenkbar gelagerte Einschaltklinke 36 auf, die mittels eines elektrischen Einschaltmagneten 38 aus einer in der Fig. 1 gezeigten, mit der Stützrolle 32 zusammenwirkenden Arbeitsstellung in eine ausserhalb der Bewegungsbahn der Stützrolle 32 gelegene Lösestellung und wieder zurück gebracht werden kann.Furthermore, 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.

Auf der Einschaltwelle sitzt weiter drehfest eine Kurvenscheibe 40, die zum Einschalten des Leistungsschalters 12 mit einem Rollenhebel 42 zusammenwirkt.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.

Mit einer von der Achse 14' ausgehenden strichpunktierten Radiallinie 44 ist eine Totpunktlage der Einschaltwelle 14 angedeutet, in welcher sich die Anlenkung der Kette 26 am Grossrad 16 bei 44' befindet, die Einschaltfeder 28 maximal gespannt ist und die Wirklinie der Kette 26 durch die Achse 14' verläuft. In der Fig. 1 befindet sich die Einschaltwelle 14 in Abstützlage, welche in durch Pfeile angedeuteter Drehrichtung D der Totpunktlage 44 folgt und bezüglich dieser um einen vorzugsweise einige Grad messenden Winkel versetzt ist. In Abstützlage, durch die strichpunktierte Linie 48 angedeutet, wirkt die gespannte Einschaltfeder 28 in Drehrichtung D auf die Einschaltwelle 14, wobei diese am Drehen durch das Abstützen der Stützrolle 32 an der Einschaltklinke 36 gehindert wird.With a dash-dotted radial line 44 starting from the axis 14 ', 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. 1, 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. In the support position, indicated by the dash-dotted line 48, 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.

Mit einer weiteren gestrichelten Linie ist eine Ruhelage 50 der Einschaltwelle 40 angedeutet, die der Totpunktlage 44 diametral gegenüberliegt und in welcher die Einschaltfeder 28 mindestens teilweise entspannt ist.With another dashed line is a rest position 50 of the switch-on shaft 40, which is diametrically opposite the dead center position 44 and in which the switch-on spring 28 is at least partially relaxed.

Fig. 2 zeigt das Räderpaar 18, wobei sich die Einschaltwelle 14 in Abstützlage 48 befindet. Ebenfalls gezeigt ist der diesseitige Endbereich der Kette 26 mit ihrer Anlenkung 46 am Grossrad 16. Die Verzahnung 52 des Grossrades 16 weist an jener Stelle eine Lücke 54 auf, die bei sich in Abstützlage 48 befindender Einschaltwelle 14 beim Kleinrad 20 angeordnet ist. Die Lücke 54 hat eine so grosse Ausdehnung, dass in Abstützlage 48 das Kleinrad 20 gegenüber dem Grossrad 16 frei drehen kann.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.

In der Fig. 3 wird ein Teil des Grossrades 16 mit der Lücke 54 der Verzahnung 52 und das Kleinrad 20 vergrössert gezeigt. Die Flanken 56 und 58 der Zähne 60 des Kleinrads 20 stossen radial aussen in einer zur Drehachse 20' parallel verlaufenden Kante 62 aneinander. Zum Spannen der Einschaltfeder 28 wird das mit der Verzahnung 52 kämmende Kleinrad 20 mittels des Antriebsmotors 22 in Antriebsrichtung A angetrieben, wodurch das Grossrad 16 in der Richtung D gedreht wird. Die dabei belastete, in Antriebsrichtung A gesehen vorlaufende Flanke 56 der Zähne 60 des Kleinrades 20, weist bis zur Kante 62 hin Evolventenform auf. Die beim Spannen der Einschaltfeder 28 unbelastete, in Antriebsrichtung A gesehen nachlaufende Flanke 58 der Zähne 60 weist eine Flankenebene 64 auf, die bei der Kante 62 an die Flanke 56 anstösst und bezüglich einer radialen Geraden 66 durch die Mitte des betreffenden Zahnes 60 um einen Winkel α von vorzugsweise 45° geneigt ist. Anschliessend an die Flankenebene 64 weist die Flanke 58 jeweils bis zum Grund 68 hin den verbleibenden Teil einer Evolvente auf.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 ′. To tension the closing spring 28, 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 α 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.

Das in der Fig. 3 gezeigte Kleinrad 20 ist aus einem handelsüblichen Zahnrad mit Evolventenverzahnung gefertigt. Davon wird an jedem Zahn vorzugsweise durch Schleifen ein strichpunktiert angedeuteter Teil 70 beim Bilden der Flankenebene 64 entfernt. Die dabei entstehende Kante 62 befindet sich im Bereich des Uebergangs der Flanke 56 in die tangentiale Stirnfläche 70' der Evolventenverzahnung.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.

Auch die Verzahnung 52 des Grossrades 16 besitzt Evolventenform, wobei am ersten in Drehrichtung D der Lücke 54 nachlaufenden Zahn 72 ein ebener Flankenteil 74, ebenfalls vorzugsweise durch Schleifen, angeformt ist, so dass die Flanken 76 und 78 dieses Zahnes 72 in einer gemeinsamen, zur Achse 14' parallel verlaufenden Zahnkante 80 aneinanderstossen. Dabei weist die in Drehrichtung D vorlaufende Flanke 76 bis zur Zahnkante 80 hin Evolventenform auf. Bei der Zahnkante 80 stösst der ebene Flankenteil 74 der nachlaufenden Flanke 78 an die Flanke 76 an, wobei der ebene Flankenteil 74 um einen Winkel β um vorzugsweise etwa 60° zu einer radialen Geraden 72' durch die Mitte des Zahnes 72 geneigt ist.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. At 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 β by approximately 60 ° to a radial straight line 72 ′ through the center of the tooth 72.

Bei der Herstellung des Grossrades 16 kann ebenfalls ein Zahnrad mit Evolventenzahnung verwendet werden. Beispielsweise mittels Schleifen werden die benötigte Anzahl Zähne zum Bilden der Lücke 54 entfernt. Weiter wird in gleicher Art und Weise wie weiter oben anhand des Kleinrades 20 beschrieben, am Zahn 72 der ebene Flankenteil 74 angeformt.A gearwheel with involute teeth can also be used in the manufacture of the large wheel 16. For example, the number of teeth required to form the gap 54 is removed by grinding. Furthermore, in the same manner as described above with reference to the small wheel 20, the flat flank part 74 is formed on the tooth 72.

Als weitere Ausbildungsform des Grossrades 16 ist es möglich, den Zahn 72 wie mit dem Pfeil 82 angedeutet, im Körper des Grossrades 16 federnd zurückdrängbar anzuordnen. In diesem Fall ist vorzugsweise am zweiten der Lücke 54 nachlaufenden Zahn 84 ebenfalls ein ebener Flankenteil 74 angeformt, wie dies weiter oben anhand des Zahnes 72 beschrieben ist.As a further embodiment of the large wheel 16, it is possible, as indicated by the arrow 82, to arrange the tooth 72 in the body of the large wheel 16 so as to be resiliently pushed back. In this case, 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.

Ausgehend von der in der Fig. 1 angedeuteten Ruhelage 50 der Einschaltwelle 40 wird zum Spannen der Einschaltfeder 28 das Grossrad mittels des Antriebsmotors 22 über das Untersetzungsgetriebe 24 und das mit der Verzahnung 52 des Grossrades 16 kämmende Kleinrad 20 in Drehrichtung D angetrieben. Sobald die Totpunktlage 44 überschritten ist, wirkt die gespannte Einschaltfeder 28 ebenfalls in Drehrichtung D auf die Einschaltwelle 14 antreibend. Diese wird aber durch das Auflaufen der Stützrolle 32 auf die sich in Ruhestellung befindende Einschaltklinke 36 am Weiterdrehen gehindert. Nach dem Ueberschreiten der Totpunktlage 44 und vor Erreichen der Abstützlage 48 gelangt das Kleinrad 20 ausser Eingriff mit der Verzahnung 52 des Grossrades 16, da sich die Lücke 54 in den Bereich des Kleinrades 20 bewegt hat. Dadurch wird die Klinkenvorrichtung 34 einzig durch die von der Einschaltfeder 28 erzeugte Kraft belastet. Infolge der nahe bei der Totpunktlage 44 sich befindenden Abstützlage 48, ist diese Abstützkraft selbst bei mit grosser Kraft gespannter Einschaltfeder 28 klein. All dies erlaubt die Klinkenvorrichtung 34 für geringe Kräfte zu dimensionieren. Die dadurch kleine zu bewegende Masse der Klinkenvorrichtung 34 erlaubt die Reaktionszeit des Federantriebs 10 zu verringern. Eine zusätzliche Belastung der Klinkenvorrichtung 34 durch das angetriebene oder auslaufende Kleinrad 20 ist vermieden. Der Vollständigkeit halber sei erwähnt, dass über allgemein bekannte Schaltmittel der Antriebsmotor 22 bei gespannter Einschaltfeder 28 abgeschaltet wird.Starting from the rest position 50 of the switch-on shaft 40 indicated in FIG. 1, 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. As soon as the dead center position 44 is exceeded, the tensioned closing spring 28 also drives the closing shaft 14 in the direction of rotation D. However, this is prevented by the support roller 32 from running on the pawl 36 which is in the rest position. After the dead center position 44 has been exceeded and before the support position 48 has been reached, 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. As a result, 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.

Wird nun zum Einschalten des Leistungsschalters 12 die Einschaltklinke 36 aus ihrer in der Fig. 1 gezeigten Ruhestellung mittels des Einschaltmagneten 38 in die Lösestellung zurückgezogen, beschleunigt die Einschaltfeder 28 die Einschaltwelle 14 in Drehrichtung D. Dadurch läuft der erste der Lücke 54 folgende Zahn 72 des Grossrades 16 auf die Flanke 58 des in Drehrichtung A gesehen hintersten in die Bewegungsbahn des Zahnes 72 vorstehenden Zahnes 60 des Kleinrades 20 auf, wodurch dieses beschleunigt wird und in kämmenden Eingriff mit der Verzahnung 52 des Grossrades 16 gelangt. Durch die weiter oben beschriebene besondere Form der Flanke 58 der Zähne 60 des Kleinrades 20 wird erzielt, dass die vorlaufende Flanke 76 des Zahnes 72 unabhängig von der Drehlage des Kleinrades 20 immer auf einen Bereich der Flanke 58 zur Einwirkung kommt, der ungefähr parallel zur Flanke 76 verläuft oder mit dieser einen sehr kleinen spitzen Winkel einschliesst. Sollte das Kleinrad 20 beim Lösen der Klinkenvorrichtung 34 mit einer wesentlich grösseren Umfangsgeschwindigkeit drehen als das Grossrad 16 erreicht, wenn der erste der Lücke 54 nachlaufende Zahn 72 in den Zusammenwirkbereich mit dem Kleinrad 20 einläuft, verhindert der Flankenteil 74, dass ein Zahn 60 des Kleinrades 20 das Räderpaar 18 blockierend am Zahn 72 anstehen kann, da dessen Flankenteil 74 in etwa parallel zum radial äusseren Endbereich der Flanke 56 des betreffenden Zahnes 60 des Kleinrades 20 verläuft.If the closing pawl 36 is now retracted from its rest position shown in FIG. 1 into the release position by means of the closing magnet 38 in order to switch on the circuit breaker 12, the closing spring 28 accelerates the closing shaft 14 in the direction of rotation D. As a result, 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. The special shape of the flank 58 of the teeth 60 of the small wheel 20 described above 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. If the small wheel 20 rotates when the ratchet device 34 is released, the circumferential speed is much greater than the large wheel 16 reaches when the first tooth trailing the gap 54 72 enters the cooperation area with the small wheel 20, 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.

Sollte bei gespannter Einschaltfeder 28, beispielsweise infolge eines Fehlers der Antriebsmotor 22 nicht abgestellt werden, gewährleistet die Ausbildungsform des Grossrades 16, bei welcher der der Lücke folgende erste Zahn 72 in radialer Richtung zurückdrängbar ausgebildet ist, ein sanftes ruckfreies Ineinandergreifen der Verzahnung 52 des Grossrades 16 mit dem Kleinrad 20.If the drive motor 22 is not switched off when the closing spring 28 is tensioned, for example as a result of a fault, 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.

Durch die Kraft der Einschaltfeder 28 wird die Einschaltwelle 14 unter Mitdrehen des Kleinrades 20 und Einschalten des Leistungsschalters 12 in die Ruhelage 50 zurück verbracht.Due to the force of the closing spring 28, 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.

Anhand der Fig. 1 wird nun der der Einschaltwelle 14 nachgeschaltete Teil des Federantriebs 10 beschrieben. Der Rollenhebel 42 sitzt drehfest auf einer ebenfalls am Gestell 30 drehbar gelagerten Antriebswelle 86, deren Längsachse 86' parallel zur Achse 14' verläuft und die von einer mit ausgezogenen Linien gezeigten Ausschaltstellung "O" in eine Einschaltstellung "I" und wieder zurück verschwenkbar ist. Ein auf der Antriebswelle 86 drehfest sitzender Abgangshebel 88 ist über ein strichpunktiert angedeutetes Gestänge 90 mit dem bewegten Schaltkontaktstück 12' des Leistungsschalters 12 verbunden.The part of the spring drive 10 connected downstream of the switch-on shaft 14 will now be described with reference to FIG. 1. 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.

Am Gestell 30 ist eine als Druckfeder ausgebildete Ausschaltfeder 92 abgestützt, deren anderes Ende mit einer Ausschaltkette 94 zusammenwirkt, die um ein am Gestell 30 ortsfest gelagertes Umlenkrad 96 zu einem auf der Antriebswelle 86 drehfest sitzenden Ausschalthebel 98 geführt ist. Der Ausschalthebel 98, an dem die Ausschaltkette 94 angelenkt ist, befindet sich in Einschaltstellung "I" der Antriebswelle 86 in einer etwa rechtwinklig zur Ausschaltkette 94 verlaufenden Lage, wogegen der Ausschalthebel 98 in Ausschaltstellung "O" und die Ausschaltkette 94 einen stumpfen Winkel einschliessen derart, dass die Ausschaltfeder 92 die Antriebswelle 86 in Ausschaltstellung "O" hält, die durch einen Anschlag in einem Bremselement 100 definiert ist, an dem in Ausschaltstellung "0" der über einen Bremshebel 102 mit der Antriebswelle 86 verbundene Bremskolben 100' anliegt.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".

Weiter ist am Gestell 30 eine Ausschaltklinkenvorrichtung 104 angeordnet, die gleich ausgebildet ist wie die Klinkenvorrichtung 34, aber mit einem auf der Antriebswelle 86 drehfest sitzenden Stützhebel 106 zusammenwirkt. Befindet sich die Antriebswelle 86 in Einschaltstellung "I", ist der Stützhebel 106 entgegen der Kraft der Ausschaltfeder 92 an der Ausschaltklinke 108 abgestützt, die durch einen elektrischen Ausschaltmagneten 110 angetrieben zum Ausschalten des Leistungsschalters 12 die Antriebswelle 86 freigibt.Furthermore, 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.

Am freien Ende des Rollenhebels 42 ist eine mit der Kurvenbahn 40' der Kurvenscheibe 40 zusammenwirkende Rolle 112 frei drehbar gelagert. Die Kurvenbahn 40' weist einen ersten Abschnitt 114 mit entgegen der Drehrichtung D zunehmendem Radius auf. Dieser erste Abschnitt 114 erstreckt sich über einen Winkelbereich, der geringfügig kleiner ist als der Winkel, den die Einschaltwelle 14 beim Einschalten aus der Abstützlage 48 in die Ruhelage 50 durchläuft. In diesem Drehbereich der Einschaltwelle 14 wirkt der erste Abschnitt 114 mit dem Rollenhebel 42 zusammen, um die Antriebswelle 86 von der Ausschaltstellung "O" in die schaltstellung "I" zu verschwenken. Entgegen der Drehrichtung D gesehen, folgt dem ersten Abschnitt 114 ein abrupt abfallender zweiter Abschnitt 116, der bei sich in Ruhelage 50 befindender Einschaltwelle 14 der Rolle 112 erlaubt, sich ohne Berühren der Kurvenscheibe 40 aus der Einschaltstellung "I" in die Ausschaltstellung "O" zu bewegen. Entgegen der Drehrichtung D gesehen, folgt dem zweiten Abschnitt 116 ein dritter Abschnitt 118, der sich bis zum ersten Abschnitt 114 hin erstreckt und der in etwa koaxial zur Achse 14' verläuft und einen derartigen Radius aufweist, dass beim Drehen der Einschaltwelle 14 aus der Ruhelage 50 in die Abstützlage 48 die sich allenfalls in Ausschaltstellung "O" befindende Antriebswelle 86 in ihrer Drehlage verbleibt.At the free end of the roller lever 42 is one with the cam track 40 'of the cam plate 40 cooperating roller 112 is freely rotatable. 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". Contrary to the direction of rotation D, 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. Contrary to the direction of rotation D, 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.

In der Fig. 1 ist mit ausgezogenen Linien die Situation gezeigt, bei welcher sich die Einschaltwelle 14 bei gespannter Einschaltfeder 28 in Abstützlage 48 befindet und die Antriebswelle 86 bei mindestens teilweise entspannter Ausschaltfeder 92 in die Ausschaltstellung "O" gedreht ist. Dabei ist der Leistungsschalter 12 geöffnet. Zum Auslösen eines Einschaltvorgangs wird nun der Einschaltmagnet 38 erregt, wodurch die Klinkenvorrichtung 34 die Einschaltwelle 14 freigibt. Diese beginnt sich unter der Kraft der Einschaltfeder 28 in Drehrichtung D zu drehen, wodurch nun einerseits, wie weiter oben beschrieben, die Verzahnung 52 des Grossrades 16 mit dem Kleinrad 20 in Eingriff gelangt und andererseits durch den ersten Abschnitt 114 der Kurvenscheibe 40 die Antriebswelle 86 aus ihrer Ausschaltstellung "O" im Gegenuhrzeigersinn in Richtung gegen die Einschaltstellung "I" verschwenkt wird. Kurz bevor die Einschaltwelle 14 die Ruhelage 50 erreicht, ist die Antriebswelle 86 in die Einschaltstellung "I" verschwenkt und der Stützhebel 106 von der Ausschaltklinkenvorrichtung 104 untergriffen, so dass die Antriebswelle 86 in Einschaltstellung "I" verbleibt, wenn der erste Abschnitt 114 von der Rolle 112 abgelaufen ist und sich die Einschaltwelle 114 in Ruhelage 50 befindet. Nun kann der eingeschaltene Leistungsschalter 12 jederzeit durch Erregen des Ausschaltmagneten 110 ausgeschaltet werden, da beim Einschalten mit dem Drehen der Antriebswelle 86 auch die Ausschaltfeder 92 gespannt wurde und deren Energie nun zum Ausschalten zur Verfügung steht. Sobald die Einschaltwelle 14 die Ruhelage 50 erreicht hat, wird der Antriebsmotor 22 eingeschaltet, um die Einschaltwelle 14 über das miteinander kämmende Räderpaar 18 aus der Ruhelage 50 über die Totpunktlage 44 hinaus zu drehen und gleichzeitig die Einschaltfeder 28 zu spannen, so dass nach erfolgtem Aufzug sich die Einschaltwelle 14 wieder zur nächsten Einschaltung bereit in Abstützlage 48 befindet. Nach Ueberschreiten der Totpunktlage 44 wird der Antriebsmotor 22 wieder ausgeschaltet, welcher nun, da das Räderpaar 18 ausser Eingriff gelangt, auslaufen kann, ohne die Klinkenvorrichtung 34 zu beanspruchen. Wird durch Erregen der Ausschaltklinkenvorrichtung 104 der Leistungsschalter 12 durch die Ausschaltfeder 92 angetrieben ausgeschaltet, ist der Federantrieb 10 sofort für eine Wiedereinschaltung des Leistungsschalters und gleichzeitigem Spannen der Ausschaltfeder 92 bereit.1, the situation is shown in solid lines in which the switch-on shaft 14 is in the support position 48 when the switch-on spring 28 is tensioned and the drive shaft 86 is turned to the switch-off position "O" with the switch-off spring 92 at least partially relaxed. The circuit breaker 12 is open. The switch-on magnet is now used to trigger a switch-on process 38 excited, whereby the pawl device 34 releases the switch-on shaft 14. This begins to rotate in the direction of rotation D under the force of the closing spring 28, as a result of which, on the one hand, as described above, the toothing 52 of the large wheel 16 engages with the small wheel 20 and, on the other hand, the drive shaft 86 through the first section 114 of the cam disk 40 from its switch-off position "O" in the counterclockwise direction towards the switch-on position "I". 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. Now 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. As soon as the switch-on shaft 14 has reached the rest position 50, 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. After the dead center position 44 has been exceeded, 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.

Selbstverständlich ist die in der Einschaltfeder 28 gespeicherte Energie derart bemessen, dass nach dem Einschalten des Leistungsschalters 12 und dem gleichzeitigen Spannen der Ausschaltfeder 92 ein genügender Energieüberschuss verbleibt, um sicherzustellen, dass die Ruhelage 50 erreicht oder überschritten wird.Of course, 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.

Allfällige überschüssige Energie wird in der Einschaltfeder rekuperiert. Es ist daher notwendig, das Kleinrad 20 über einen in Antriebsrichtung A wirkenden Freilauf mit dem Untersetzungsgetriebe 24 zu verbinden, so dass der Antriebsmotor 22 und das Untersetzungsgetriebe 24 einzig zum Antreiben der Einschaltwelle 14 und Spannen der Einschaltfeder 28 wirkverbunden sind. Ist dann während eines Einschaltens das Grossrad 16 für das Kleinrad 20 antreibend, ist dieses vom Antriebsmotor 22 und Untersetzungsgetriebe 24 entkoppelt, so dass einzig das Kleinrad 20 mit dem Grossrad 16 zu synchronisieren und zu bewegen ist, was infolge der geringen Masse zu kleinen Kräften führt.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 .

Anstelle des Antriebsmotors 22 kann selbstverständlich auch eine Handkurbel oder ein anderes Antriebsmittel verwendet werden. Der erfindungsgemässe Federkraftantrieb 10 eignet sich insbesondere zum Antrieb von Mittel- und spannungsschaltgeräten.Instead of the drive motor 22, a hand crank or another drive means can of course also be used. The spring force drive 10 according to the invention is particularly suitable for driving medium and voltage switching devices.

Das Entfernen und Anschrägen der Zähne 60,72,84 kann durch Schleifen erfolgen. Vorzugsweise werden die Zähne 60 des Kleinrades 20 und der erste und gegebenenfalls zweite der Lücke 54 nachlaufende Zahn 72,84 des Grossrades 16 nach erfolgter Anschrägung, d.h. Herstellung der Flankenebene 64 bzw. des ebenen Flankenteils 74, randschichtgehärtet.The teeth 60, 72, 84 can be removed and chamfered by grinding. Preferably, 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.

In dem gezeigten Ausführungsbeispiel besteht das Räderpaar 18 aus Stirnrädern. Es ist selbstverständlich auch denkbar, andersartige Zahnräder zu verwenden.In the exemplary embodiment shown, the pair of wheels 18 consists of spur gears. It is of course also conceivable to use different types of gears.

Claims (8)

  1. A spring drive for a switching apparatus, especially a power circuit breaker for medium voltage and high voltage, having a switch-on spring (28) which is coupled eccentrically to a rotatably mounted switch-on shaft (14) for driving the switch-on shaft (14) in a rotation direction (N) to switch-on the switching apparatus (12), having a large wheel (16) which is connected to the switch-on shaft (14), and a small wheel (20) which interacts with said large wheel and can be driven by means of a drive device (22), in order to stress the switch-on spring (28) by rotation of the switch-on shaft (14) in the rotation direction (N) from an initial position (50), in which the switch-on spring (28) is at least partially relieved of stress, via a deadpoint position (44) in which the switch-on spring (28) is stressed, having a latching device (34) which supports the switch-on shaft (14) in a supported position (48) which follows the deadpoint position (44) in the rotation direction (N) and releases the switch-on shaft (14) to switch-on the switching apparatus, having a gap (54) in a tooth system (52) on the large wheel (16) at a point which is arranged adjacent to the small wheel (20) when the switch-on shaft (14) is supported on the latching device (34), and having means for preventing mutual blocking of a wheel pair (18) after release of the switch-on shaft (14) by the latching device (34), wherein flanks (56, 58) of teeth (60) on the small wheel (20) abut against one another radially on an outer side at a common edge (62) and the teeth (60) have an involute shape on the flank (56) which is loaded in order to stress the switch-on spring (14), and the flank (58), which is unloaded during stressing the switch-on spring, has a flank plane (64) which abuts the common edge (62) and is inclined with respect to a radial straight line (66) through a center of the tooth, and wherein the flanks (76, 78) of the first tooth system (72) following the gap (54) in the direction of rotation (D) on the large wheel (16) abut against one another radially on an outer side at a common edge (80), and the tooth height of said tooth (72) is at the most as big as the tooth height of the rest of the teeth of the tooth system (52) on the large wheel (16).
  2. A spring drive as claimed in claim 1, wherein the flank plane (64) of the teeth (60) on the small wheel (20) is inclined at an angle of approximately 45° with respect to the radial straight line (66).
  3. A spring drive as claimed in any one of claims 1 or 2, wherein the small wheel (20) and the large wheel (16) are spur gears having outer tooth systems.
  4. A spring drive as claimed in any one of claims 1 to 3, wherein the first tooth (72) trailing behind the gap (54) has an involute shape on the flank (76) which is loaded during switch-on, and the flank (78) which is unloaded during switch-on has a flat flank part (74) which extends from the tooth edge (80) and is inclined preferably of approximately 60°, with respect to a radial straight line (72') through a center of the tooth.
  5. A spring drive as claimed in claim 3 or 4, wherein the first tooth (72) trailing behind the gap (54) is constructed such that it can be forced back in a sprung manner in a radial direction (82) and the second tooth (82) trailing behind the gap (54) has an involute shape on the flank (76) which is loaded during switch-on, and the flank (78) which is unloaded during switch-on has a flat flank part (74) which abuts the tooth edge (80) and is inclined preferably of approximately 60°, with respect to a radial straight line through the tooth center.
  6. A method for providing a small wheel and a large wheel for a spring drive as claimed in any one of claims 1 to 5, wherein the teeth (60) are inclined on one side on a small wheel (20) having an involute tooth system, so that the tooth flanks (56, 58) abut against one another radially on the outside at a common edge (62) and a flank plane (64) extends from said edge (62) and is inclined with respect to a radial straight line (66) through a center of the tooth and wherein teeth are removed from the continuous tooth system (52) on a large wheel (16) having an involute tooth system, in order to form a gap (54), and the first teeth and optionally the second teeth (72, 84) which trail behind the gap (54) in the rotation direction (D) are inclined on one side.
  7. A method as claimed in claim 6, wherein inclining and removal of the teeth (60, 72, 84) is carried out by grinding.
  8. A method as claimed in claim 6 or 7, wherein the teeth (60) on the small wheel (20) and the first tooth and optionally the second tooth (72, 84), trailing behind the gap (54), on the large wheel (16) are hardened on the edge layer after inclining has been carried out.
EP93117797A 1993-11-03 1993-11-03 Spring drive for switchgear Expired - Lifetime EP0651409B1 (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP93117797A EP0651409B1 (en) 1993-11-03 1993-11-03 Spring drive for switchgear
DE59307350T DE59307350D1 (en) 1993-11-03 1993-11-03 Spring drive for a switching device
AT93117797T ATE158105T1 (en) 1993-11-03 1993-11-03 SPRING DRIVE FOR A SWITCHING DEVICE
US08/328,650 US5595287A (en) 1993-11-03 1994-10-25 Spring drive for a switching apparatus
JP29583494A JP3605620B2 (en) 1993-11-03 1994-11-04 SPRING DRIVE FOR SWITCH DEVICE AND METHOD OF MANUFACTURING GEAR USED FOR THE SAME

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP93117797A EP0651409B1 (en) 1993-11-03 1993-11-03 Spring drive for switchgear

Publications (2)

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

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP93117797A Expired - Lifetime EP0651409B1 (en) 1993-11-03 1993-11-03 Spring drive for switchgear

Country Status (5)

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US (1) US5595287A (en)
EP (1) EP0651409B1 (en)
JP (1) JP3605620B2 (en)
AT (1) ATE158105T1 (en)
DE (1) DE59307350D1 (en)

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US5944305A (en) * 1997-01-30 1999-08-31 Canon Kabushiki Kaisha Drive transmitting device, sheet feeding device and image forming apparatus
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FR2770929B1 (en) * 1997-11-13 2000-01-28 Alsthom Gec SPRING DRIVE MECHANISM FOR A SWITCHING APPARATUS, IN PARTICULAR A CIRCUIT BREAKER
US6160234A (en) * 1999-04-29 2000-12-12 Eaton Corporation Reduced drag ratchet
FR2805921B1 (en) * 2000-03-02 2002-11-29 Alstom DEVICE FOR CONTROL MECHANISM OF ELECTRICAL APPARATUS AND CONTROL MECHANISM PROVIDED WITH SUCH A DEVICE
FR2846779B1 (en) * 2002-10-30 2005-01-28 Alstom CIRCUIT BREAKER COMPRISING A CONTROL ARRANGEMENT AND A CUTTING CHAMBER, ITS ASSEMBLY METHOD AND AUXILIARY ARM FOR THIS ASSEMBLY
US8035329B2 (en) * 2003-09-13 2011-10-11 Abb Technology Ag Apparatus for actuating an electrical switching device
US7581463B2 (en) * 2004-07-30 2009-09-01 Xerox Corporation Gear modification that enables direct off-center engagement
FR2919957B1 (en) 2007-08-08 2009-10-30 Areva T & D Ag METALLIC ENCLOSURE METALLIC ENCLOSURE TYPE SWITCHING DEVICE WITH REDUCED PHASE TRASMISSION FORCES AND REDUCED PHASE TRASMISSION FORCES
FR2925211B1 (en) 2007-12-17 2010-01-15 Areva T & D Ag COMPACT AND ROBUST CONTROL FOR MEDIUM AND HIGH VOLTAGE ELECTRICAL EQUIPMENT
FR2925210B1 (en) 2007-12-17 2010-01-15 Areva T&D Ag COMPACT CONTROL FOR MEDIUM AND HIGH VOLTAGE ELECTRICAL EQUIPMENT
CN102148101B (en) * 2011-04-20 2013-10-09 常熟开关制造有限公司(原常熟开关厂） Change-over switch gear
CN102867663B (en) * 2012-09-24 2014-12-24 中国西电电气股份有限公司 Clutch device of gear transmission system of breaker spring operating mechanism
CN103996565A (en) * 2013-02-20 2014-08-20 张亚宇 Spring operating mechanism of high-voltage circuit breaker
FR3046260B1 (en) * 2015-12-29 2018-07-27 Systemes Moteurs GEAR MOVEMENT TRANSMISSION DEVICE AND ACTUATING SYSTEM COMPRISING SAME
DE102016214544B4 (en) * 2016-08-05 2020-01-09 Siemens Aktiengesellschaft Transmission between a movable switch contact and a drive of a circuit breaker and a circuit breaker with such a transmission
CN112201490B (en) * 2020-09-25 2023-07-18 国网山东省电力公司烟台供电公司 Be used for post switch electrically operated insulator spindle

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Also Published As

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

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