EP2189995A2 - Steuerung eines elektrischen Hoch- oder Mittelspannungsgerätes mit einem verbesserten doppelten Einrastmechanismus und entsprechendes Bestückungsverfahren - Google Patents

Steuerung eines elektrischen Hoch- oder Mittelspannungsgerätes mit einem verbesserten doppelten Einrastmechanismus und entsprechendes Bestückungsverfahren Download PDF

Info

Publication number: EP2189995A2
Authority: EP; European Patent Office
Prior art keywords: closing; opening; spring; pinion; wheel
Prior art date: 2008-11-20
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.): Granted

Application number

EP09176296A

Other languages

English (en)

French (fr)

Other versions

EP2189995A3 (de

EP2189995B1 (de

Inventor

Romain Maladen

Antoine Vicaigne

Bruno Colin

Mathieu Marquet

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.)

Schneider Electric Energy France SAS

Original Assignee

Areva T&D SAS

Schneider Electric Energy France SAS

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.)

2008-11-20

Filing date

2009-11-18

Publication date

2010-05-26

2009-11-18 Application filed by Areva T&D SAS, Schneider Electric Energy France SAS filed Critical Areva T&D SAS

2010-05-26 Publication of EP2189995A2 publication Critical patent/EP2189995A2/de

2010-06-23 Publication of EP2189995A3 publication Critical patent/EP2189995A3/de

2012-02-08 Application granted granted Critical

2012-02-08 Publication of EP2189995B1 publication Critical patent/EP2189995B1/de

Status Not-in-force legal-status Critical Current

2029-11-18 Anticipated expiration legal-status Critical

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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
- H01H3/3042—Power arrangements internal to the switch for operating the driving mechanism using spring motor using a torsion spring

Definitions

the invention relates to the field of control of electrical equipment high or medium voltage with at least one switch.
It relates to the controls which comprise a double latching mechanism whose disarming is capable of causing a closing / opening cycle of at least one operating switch of the electrical equipment.
the invention relates more particularly to the controls in which the double-hooking mechanism comprises two spiral springs whose disarming of one said opening spring is able to cause a maneuver opening the switch while the disarming of the other said closing spring is capable of causing a closing operation of the switch.
the object of the invention is to propose a new control of this type whose motorized rearming is improved and which still allows manual reset.
the double latching mechanisms can store energy to perform two operations of at least one switch of the electrical equipment which is provided with a closing maneuver and an opening maneuver.
a known type of double-hook mechanisms is that comprising two spiral springs, typically having a high stiffness for high or medium voltage application. They are compressed during a maneuver called “arming" that can be performed manually (with a lever) and / or motorized.
the mechanisms comprising two coaxial coil springs are preferred over those comprising one (or more) compression spring (s) because they make it possible on the one hand to design a compact system and on the other hand to obtain a ideal energy distribution since the torque supplied by each of the spiral springs is maximal at the beginning of the maneuver (when the spring is compressed to the maximum) and that it is always ideally oriented (zero radial force).
Such a double-hook mechanism with two spiral springs with high stiffness is known from the document EP 0186171 which discloses a control of a high-voltage circuit breaker in which there is provided a closing spiral spring 2 which in the compressed state exerts a torsion torque on a transmission shaft 4 on which its inner end is fixed, a spring in opening spiral 1 which in the compressed state exerts a torsion torque on a control shaft 3 on which its inner end is fixed.
the actuation of a drive motor 22 compresses the closing spring 2 by means of a belt 23.
the transmission shaft 4 is aligned with the control shaft 3 and coupling means comprising a star wheel 6 are arranged between them in order to couple them and thus allow the closing of the circuit breaker.
Such a coupling also simultaneously allows the compression of the opening spring 1 by the release of the closing spring 2.
the main disadvantage of the control disclosed in this document is that for an opening energy similar to the closing energy, it a closing spring 2 is required which can store twice as much energy as necessary for the actual closing maneuver, since the opening spring 1 is compressed by the expansion of the closing spring 2.
the torque needed to arm the closing spring 2 corresponds to the sum of the theoretical arming torques of a closing spring and an opening spring required only for a given cycle closing / opening with a completely dissociated operation.
the controls of this type may also optionally include a geared motor as a motorized means for rearming the two closing and opening springs when they are in the relaxed state and that they were thus used to perform a maneuver of closing and opening at least one high or medium voltage switch.
a geared motor as a motorized means for rearming the two closing and opening springs when they are in the relaxed state and that they were thus used to perform a maneuver of closing and opening at least one high or medium voltage switch.
the inventors have also been confronted with an additional problem that is not known to date for this type of control: they must design a control capable of making an opening and closing maneuver of at least one high or medium voltage switch with a total simultaneous arming torque of the two springs of the order of 120 Nm
the subject of the invention is a high or medium voltage switchgear control comprising a double-snap mechanism, an armature gearmotor of the double-snap mechanism and a transmission chain for transmitting the output torque of the gearmotor to an element of the double-snap mechanism.
the control according to the invention thus allows to be able to operate a switch of a high or medium voltage switchgear which requires a large operating torque of the order of 120 N.m.
the solution according to the invention can very well be applied for weaker couples and would thus reduce the power of the motor or geared motor by a factor of 2.
the basic idea of the solution consists, for a motorized maneuver, of compressing the two springs one after the other with the aid of the same gearmotor.
the motor provides a couple of times lower, which reduces its cost, dimensions and power consumption.
the torque supplied by the geared motor is of the order of 60 Nm
the solution presented allows, in manual operation, to arm the mechanism in a single operation (a single direction of maneuver) and thus to compress the two springs simultaneously.
the control according to the invention thus makes it possible to meet the normative conditions of manual arming.
the reduction ratios between the closing pinion and the third pinion and between the opening pinion and the fourth transmission pinion are identical and coupling means are provided for coupling the pinion closure and the wheel only after the opening spring has been compressed by the output torque of the gearmotor in one direction and the opening wheel has been engaged, the coupling between the closing pinion and the arming wheel permitting compressing the closing spring by the output torque of the gearmotor in the other direction and hooking the arming wheel while the opening spring remains in the same compressed state.
the coupling means comprise an axis fixed to the closing gear and a so-called arming finger able to disengage from the arming wheel at the end of the maneuver under the thrust action of the pin fixed to the pinion. closure.
the opening and closing wheels are each designed with a recess for respectively housing the opening and closing spring.
the closing pinion is removable, the interruption of the transmission chain being achieved by removal of said pinion closure.
the closing pinion is thus replaced by a manual cocking lever.
a control particularly targeted by the invention is that in which, in the uninterrupted state of the chain, the geared motor is able to provide an output torque of about 60 Nm to compress each of the two springs while, in the interrupted state of the chain, the two springs are able to be compressed simultaneously with a rearming torque of 120 Nm
the invention also relates to a manual cocking lever comprising a male portion adapted to be fitted in place of the closing pinion of the control described above, and a tab which has the same function as the axis of said pinion.
the control according to the invention 1 as shown first comprises a fixed frame not shown and a geared motor which only the output gear 2 is shown.
the control according to the invention further comprises a transmission chain 4 for transmitting the rotational movement of the output gear 2 of the geared motor in a rotational movement to the control shaft 30 and according to the different arming phases to one of the wheels 31, 32, 33 to compress the closing spring 34 and the opening spring 35.
the characteristics of the opening pinion 41 are identical to those of the closing pinion 40 so that the reduction ratios on the one hand between the closing pinion 40 and the transmission shaft 42 (pinion 43) and on the other hand between the pinion opening 41 and transmission shaft 42 (pinion 44) are identical.
spiral springs 34 and 35 are identical.
both spiral springs 34 and 35 remain in a compressed state or in other words pre-compressed (pre-compressed to a given level, necessary only for operation).
the closing wheel 31 comprises a recess which forms a cage in which the closing spiral spring 34 is housed.
the opening wheel 33 is recessed and the cage thus formed houses the spiral spring 35 opening.
the two spiral springs 34, 35 are pre-compressed and thus support the arming wheel 32, and the opening wheel 33 resting on the column 36 (FIG. Figure 1A ).
the closure wheel 31 is, in turn, retained by a hooking means (not shown) coming to hook the recess 310 of the wheel 31.
the arming maneuver thus consists in compressing the two spiral springs 34, 35 by their inner end.
the total torque required for a combined opening / closing operation of the switch of the apparatus is such that a motorized arming of the closing spring 34 and then of the opening spring 35 is provided.
the gearmotor realizes the compression of the two spiral springs 35 opening and closure 34 but that it provides only the torque required for the compression of a single spring 34 or 35, being of the order of 60 Nm
Phase 1 ( Figure 2A ) : The output gear 2 of the gearmotor rotates counter-clockwise on a first rotational stroke.
the closing pinion 40 then meshes with the transmission pinion 43 at the end of the transmission shaft 42 closest to the output pinion 2 of the geared motor. But the axis 400 attached to the transmission pinion 40 is on this free rotation stroke of any contact: the transmission pinion 43 therefore causes no part.
the arming wheel 32 and the control shaft 30 to which it is attached are therefore immobile.
the opening wheel 33 is rotated in the same counterclockwise direction by meshing via the transmission gear 44 at the end of the transmission shaft 42 farthest from the output gear 2 of the geared motor.
the spiral spring opening 35 is thus compressed by its outer end as fixed to the opening wheel 33.
the inner end of the opening spring 35 remains stationary as it is fixed to the control shaft 30 immobile.
the geared motor thus provides the torque (about 60 Nm at the end of the race Figure 2C ) for the arming of a single spring, namely here the opening spring 35.
Phase 2 ( Figure 2B ) : The output gear 2 of the gearmotor continues to rotate in the same anti-clockwise direction.
the axis 400 fixed to the closing pinion 40 then bears on the cocking finger 320 which moves apart to let it pass.
the cocking pin 320 comes into its disengaged position from the cocking wheel 32.
the rotation of the opening pinion 41, the opening wheel 33 which is connected thereto continues: the spring Opening spiral 35 then continues to compress.
Phase 3 ( Figure 2C ) : The closing pinion 40 has reached a position such that the pin 400 fixed to said pinion 40 has brought the cocking pin 320 into its engaged position with the cocking wheel 32.
the pin arming 320 is closed on the axis 400 which is wedged between the cocking pin 320 and the cocking wheel 32.
the geared motor is then stopped.
the opening wheel 33 is at the same time hooked by the means not shown: the opening spring 35 is thus maintained in the compressed state.
the mechanical assembly constituted by the arming wheel 32, the opening gear 41, the traversing shaft 42 with its pinions 43, 44 and the opening wheel 33 hooked is therefore equivalent to a mechanical assembly rigid. It does not generate any resisting torque on the geared motor.
Phase 4 ( 2D figure ) : The direction of rotation of the gearmotor is reversed: the output gear 2 of the gearmotor rotates clockwise.
the aforementioned mechanical assembly (arming wheel 32, the opening pinion 41, the traversing shaft 42 with its pinions 43, 44 and the opening wheel 33 hooked) remains rigid, the opening spring 35 is therefore kept compressed.
the compression opening spring 35 is not modified by this inversion of the direction of rotation of the geared motor.
the rotation of the geared motor in the clockwise direction therefore causes rotation in the same direction of the closing wheel 31 and therefore of the control shaft 30 to which it is attached.
the closing spring 34 whose inner end is fixed to the control shaft 30 is then compressed because the other end (outer end) fixed to the closing wheel 31 is stationary, the latter being hooked by means of appropriate hooking not shown.
the geared motor still provides only the necessary torque to arm only one spring, the closing spring 34 (about 60 Nm at the end of rearming).
Phase 5 ( Figure 2 E) A system (not shown) makes it possible to disengage the cocking finger 320 from the cocking wheel 32 and thus to disengage or otherwise disengage the closing pinion 40 from the cocking wheel 32. Moreover, the wheel opening 33 is in this position bearing on the column 36. The arming wheel 32 is then rotated by a locking system (not shown) which was set up automatically at the end of armament maneuver.
the double latching mechanism 3 is now in the armed position, the two spiral springs respectively opening 35 and closure 34 being compressed and the opening pinion 40 being free.
the opening / closing operation can be carried out conventionally either manually by means of a push button or automatically, in the event of an electrical fault detected on the electrical line on which the electrical equipment provided with the control is implanted, under the action of an electric trip coil.
the control according to the invention 1 meets the normative conditions which impose a manual arming of the two spiral springs 34 and 35 with a lever from outside the control and in a single direction of rotation.
the double hook mechanism 3 is initially disarmed and the various parts of the mechanism 3 are found in the position of the Figure 1A .
Phase 1 ( figure 3A ) : The closing pinion 40 being removable, it is previously removed from the end of the control shaft 30 in which it is fitted.
the lever 5 comprises a male part 50 which is engaged in place of the closing pinion 40 and a tab 500 which has the same function as the axis 400 of the transmission pinion 40.
the tab 500 is thus wedged between the arming finger 320 and the arming wheel 32. In other words, the arming finger 320 is closed on the leg 500.
the closure wheel 31 is hooked by its recess 310 and held in position.
the opening wheel 33 is in turn resting on the column 36.
Phase 2 ( figure 3B ) : The operator rotates clockwise lever 5 which is supported on the cocking pin 320 and wedged between it and the cocking wheel 32: the cocking wheel 32 is then rotated.
the cocking wheel 32 is rotatably connected to the control shaft 30 and the respective closing and opening wheels 33 being locked in rotation (the first 31 by the hooking and the other 33 by its support on the column 36), the two spiral springs respectively opening 35 and closure 34 are then compressed simultaneously by their inner end as fixed to the control shaft 30.
the arming wheel 32 is hooked by the attachment means not shown: the two respectively aperture spring 35 and closure 34 are compressed (total torque 120 Nm) and maintained in this state.
the double latching mechanism 3 has therefore been manually armed.
Phase 3 ( figure 3C ) : Before an opening / closing cycle can be carried out, just like the motorized armament, a disengagement or disengagement between the arming lever 5 and the command 1 is carried out.
This clutch is made at the end of manual arming, that is to say after hooking of the arming wheel 32.
the operator continues to turn the cocking lever 5 clockwise, which causes the release of the cocking finger 320 of the cocking wheel 32 under the thrust action of the axis 500.
the lever 5 can then be released by disengaging it from the end 301 of the control shaft 30.

Landscapes

Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
Mechanisms For Operating Contacts (AREA)
Control Of Ac Motors In General (AREA)
Arrangements For Transmission Of Measured Signals (AREA)
Transmission Devices (AREA)
Control Of Electric Motors In General (AREA)

EP09176296A 2008-11-20 2009-11-18 Steuerung eines elektrischen Hoch- oder Mittelspannungsgerätes mit einem verbesserten doppelten Einrastmechanismus und entsprechendes Bestückungsverfahren Not-in-force EP2189995B1 (de)

Applications Claiming Priority (1)

Application Number	Priority Date	Filing Date	Title
FR0857898A FR2938692B1 (fr)	2008-11-20	2008-11-20	Commande d'appareillage electrique haute ou moyenne tension a mecanisme a double accrochage ameliore et procede d'armement associe.

Publications (3)

Publication Number	Publication Date
EP2189995A2 true EP2189995A2 (de)	2010-05-26
EP2189995A3 EP2189995A3 (de)	2010-06-23
EP2189995B1 EP2189995B1 (de)	2012-02-08

Family

ID=40765635

Family Applications (1)

Application Number	Title	Priority Date	Filing Date
EP09176296A Not-in-force EP2189995B1 (de)	2008-11-20	2009-11-18	Steuerung eines elektrischen Hoch- oder Mittelspannungsgerätes mit einem verbesserten doppelten Einrastmechanismus und entsprechendes Bestückungsverfahren

Country Status (4)

Country	Link
EP (1)	EP2189995B1 (de)
AT (1)	ATE545143T1 (de)
ES (1)	ES2379218T3 (de)
FR (1)	FR2938692B1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
WO2015162534A1 (en) *	2014-04-24	2015-10-29	Eaton Corporation	Circuit breakers with clock spring drives and/or multi-lobe drive cams and related actuators and methods
US9472359B2 (en)	2014-04-24	2016-10-18	Eaton Corporation	Trip latch assemblies for circuit breakers and related circuit breakers
CN114458744A (zh) *	2020-11-10	2022-05-10	施耐德电器工业公司	开关单元的带有可移除安全元件的控制齿轮马达组件

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
FR3089049B1 (fr) *	2018-11-26	2020-11-06	Schneider Electric Ind Sas	Mécanisme pour la commande de fermeture et d’ouverture d’un dispositif de coupure de courant pour appareil électrique interrupteur
FR3148864A1 (fr) *	2023-05-19	2024-11-22	Schneider Electric Industries Sas	Mécanisme de commande d'un dispositif de coupure du courant

Citations (1)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
EP0186171A2 (de)	1984-12-28	1986-07-02	Asea Ab	Antriebsvorrichtung für einen Leistungsschalter

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
US4578551A (en) *	1985-04-10	1986-03-25	S&C Electric Company	Operating mechanism for electrical switches

2008
- 2008-11-20 FR FR0857898A patent/FR2938692B1/fr not_active Expired - Fee Related
2009
- 2009-11-18 AT AT09176296T patent/ATE545143T1/de active
- 2009-11-18 EP EP09176296A patent/EP2189995B1/de not_active Not-in-force
- 2009-11-18 ES ES09176296T patent/ES2379218T3/es active Active

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
EP0186171A2 (de)	1984-12-28	1986-07-02	Asea Ab	Antriebsvorrichtung für einen Leistungsschalter

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
WO2015162534A1 (en) *	2014-04-24	2015-10-29	Eaton Corporation	Circuit breakers with clock spring drives and/or multi-lobe drive cams and related actuators and methods
US9373456B2 (en)	2014-04-24	2016-06-21	Eaton Corporation	Circuit breakers with clock spring drives and/or multi-lobe drive cams and related actuators and methods
US9472359B2 (en)	2014-04-24	2016-10-18	Eaton Corporation	Trip latch assemblies for circuit breakers and related circuit breakers
CN114458744A (zh) *	2020-11-10	2022-05-10	施耐德电器工业公司	开关单元的带有可移除安全元件的控制齿轮马达组件

Also Published As

Publication number	Publication date
EP2189995A3 (de)	2010-06-23
FR2938692B1 (fr)	2010-12-24
FR2938692A1 (fr)	2010-05-21
ES2379218T3 (es)	2012-04-23
EP2189995B1 (de)	2012-02-08
ATE545143T1 (de)	2012-02-15

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