EP1094479B1 - Dispositif pour l' actionnement de circuits - Google Patents

Dispositif pour l' actionnement de circuits Download PDF

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Publication number
EP1094479B1
EP1094479B1 EP00118986A EP00118986A EP1094479B1 EP 1094479 B1 EP1094479 B1 EP 1094479B1 EP 00118986 A EP00118986 A EP 00118986A EP 00118986 A EP00118986 A EP 00118986A EP 1094479 B1 EP1094479 B1 EP 1094479B1
Authority
EP
European Patent Office
Prior art keywords
actuating
pawl
teeth
ratchet
shaft
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
EP00118986A
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German (de)
English (en)
Other versions
EP1094479A3 (fr
EP1094479A2 (fr
Inventor
Erwin Reichl
Werner Heinzelmann
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.)
Grid Solutions SAS
Original Assignee
Areva T&D SAS
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Publication date
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Publication of EP1094479A2 publication Critical patent/EP1094479A2/fr
Publication of EP1094479A3 publication Critical patent/EP1094479A3/fr
Application granted granted Critical
Publication of EP1094479B1 publication Critical patent/EP1094479B1/fr
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
    • H01H3/32—Driving mechanisms, i.e. for transmitting driving force to the contacts
    • H01H3/34—Driving mechanisms, i.e. for transmitting driving force to the contacts using ratchet
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H3/00—Mechanisms for operating contacts
    • H01H3/22—Power arrangements internal to the switch for operating the driving mechanism
    • H01H3/30—Power arrangements internal to the switch for operating the driving mechanism using spring motor
    • H01H3/3005—Charging means
    • H01H3/3021—Charging means using unidirectional coupling
    • 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
    • H01H3/3047—Power arrangements internal to the switch for operating the driving mechanism using spring motor adapted for operation of a three-position switch, e.g. on-off-earth

Definitions

  • the invention relates to an actuating device for actuating current paths according to the preamble of claim 1.
  • Such an actuating device is known from US-A-3,475,981 known.
  • actuating means between the drive shaft and the actuating shaft to a transmission.
  • Typical gear ratios of such transmissions amount to at least 1: 400 with motor operation and reach up to approx. 1: 2000, for manual operation approx. 1: 5 to 1: 100.
  • the switching operation of such a switching device may take less than one to several seconds.
  • the state of the art also includes actuators with planetary gears.
  • the provision of planetary gears is very costly and it also lacks the self-locking effect.
  • the present invention is therefore based on the object to propose an actuating device which has an extremely simple and therefore cost-reversible transmission.
  • the above-described disadvantages of the prior art to be remedied.
  • the invention solves this problem by an actuating device according to claim 1.
  • the object according to the invention has the advantage that such a pawl transmission in production and assembly is very inexpensive.
  • an initiated actuation of the switching operation can be reversed at any time before reaching the respective end position of the switching device. Due to the fact that when a rotating drive shaft in each case a pawl tip is engaged with the ratchet, it is excluded that a return of the ratchet wheel against the direction of rotation of the actuating shaft is possible.
  • the ratchet gear teeth on two opposing rows of teeth for receiving the respective engaging in the ratchet gear ratchet tips can also overlap.
  • the teeth must be designed to be acted upon on both sides.
  • the two eccentrics are arranged offset on the drive shaft preferably at an angle of 1800 to each other.
  • the double latches are configured symmetrically.
  • the pitch of the ratchet teeth is slightly smaller than twice the eccentric center eccentricity to the center axis of the drive shaft. It is assumed that only one ratchet wheel is present on the actuating shaft, or two identical, aligned Rinkenradfusionn.
  • a particularly preferred development of the invention is characterized in that the two double pawls are designed asymmetrically such that the tooth pitch of the ratchet wheel is slightly smaller than four times the eccentric center of the eccentric center to the central axis of the drive shaft.
  • Such asymmetrical double pawl has a short and a long half of the pawl.
  • the difference between a short and a long half of the catch is slightly more than half of the pitch of the ratchet wheel.
  • Another embodiment of the invention provides that on the actuating shaft two mutually parallel ratchet wheels are present, with a double pawl on the at least one drive shaft for engagement in each one Ratchet wheel is provided.
  • the two ratchet wheels are identical and are either offset from one another or aligned on the one actuating shaft.
  • a preferred embodiment of the invention provides that the two double pawls are designed symmetrically, that the rows of ratchet teeth of the two ratchet wheels are offset by half a pitch and that the pitch of the two ratchet wheels slightly smaller than four times the eccentricity of the eccentric center to the central axis the drive shaft is.
  • Such a configuration has the advantage that due to the mutually offset ratchet wheels in symmetrical double pawls, the tooth pitch is not slightly less than twice, but slightly smaller than four times the eccentric center of the eccentric center to the central axis of the drive shaft. Due to such a pitch, the teeth of the ratchet wheel are much more stable, which is particularly important for double-sided loading of the individual teeth of crucial importance.
  • Another preferred embodiment of the invention provides that the actuating device for Three-position switch is executed and has a current path closing, one the current path separating and a current path connecting to ground switching position.
  • Three-position switches have the advantage that only one movable switching element has two switching functions.
  • the three-position switch in the neutral position of the actuating shaft separates the current path that closed after a rotational angle of the actuating shaft of about 90 ° in one direction of rotation of the current path and from about 90 ° in the other direction, the current path to earth connected is.
  • Such an arrangement of the three-position switch has proven to be particularly advantageous in practice.
  • At least two drive shafts which can be driven independently of one another are provided with eccentrics with double pawls disposed thereon, over which the Actuating shaft is actuated in the various switching positions. Due to the two independently driven drive shafts an unambiguous assignment of a drive shaft is achieved to a switching position. Switching through the actuator in all three switching positions by turning only one drive shaft is therefore excluded.
  • the ratchet wheels or the ratchet wheel each have only one row of teeth for engaging the double pawls of the respective actuated drive axle, so that a rotation of that drive shaft in the engagement region, the ratchet wheels or the ratchet wheel are not or is without Actuation of the actuating shaft is freely rotatable. This avoids that upon actuation of the one drive shaft, due to the actuation of the other drive shaft, a collision or a blocking state in the actuator is possible.
  • the actuating shaft can only be rotated by a little more than 90 ° and turned back. It is at a further rotation of the corresponding drive shaft, the actuating shaft is not further rotated. This is particularly advantageous if the drive is a drive motor, which travels after reaching the corresponding switch position, without this being allowed to influence the switch position.
  • a further preferred embodiment of the three-position switch actuator is characterized in that an engagement prevention device, in particular a rocker arm, to avoid simultaneous engagement of the double pawls of both drive shafts with simultaneous actuation of both drive shafts is present. This ensures that, in particular when the disconnector is switched off, simultaneous engagement of the pawls with simultaneous actuation of both drive shafts is precluded.
  • an engagement prevention device in particular a rocker arm
  • An embodiment of the invention provides that the present on the drive shafts double latches in each case engage in different arranged on the actuating shaft ratchet wheels.
  • this may be the case when four ratchet wheels are present on the actuating shaft, wherein two ratchet wheels are each offset by half a pitch in relation to each other and for engaging each of a drive shaft existing two double pawls serve.
  • the double pawls present on the drive shafts only engage in a ratchet wheel present on the actuating shaft.
  • the double pawls which are asymmetrical and each have a long and a short latch arm.
  • the ratchet wheel toothing of a ratchet wheel has different ratchet toothed sections with at least partially different rows of teeth for engaging the respective pawl tips of the corresponding double pawls.
  • Such Klinkenradveriereungsabitese are particularly needed if a plurality of independently operable double pawls on a ratchet come into engagement.
  • a variant of the invention provides that the teeth of the rows of teeth, which are acted upon from one side only by a pawl tip, have a beveled rear edge. On such a rear edge, the Run the latch tip well without operating the actuation shaft or damaging the latch tip.
  • Another preferred embodiment of the invention is characterized in that the teeth of the rows of teeth, which are acted upon by pawl tips from both sides, on both sides have a, in particular to the Klinkenradun approximately at right angles formed, attack surface for acting on the pawl tips.
  • Such a configuration of the corresponding teeth has proven to be particularly stable and therefore advantageous.
  • the ratchet wheel or the ratchet wheels only partially a ratchet gear teeth. In the areas in which no interference of pawl tips is provided on tooth flanks, so a Klinkenradvertechnikung can fail on the ratchet wheel. It is also conceivable that no full ratchet wheels, but only Klinkenradsegmente be used.
  • the force application of the pawl tip on the ratchet wheel or the ratchet wheels is largely tangential. This ensures the largest possible lever arm.
  • An easy to Ratchet wheel center directed force component ensures the secure engagement of the pawl tips on the corresponding ratchet wheel.
  • the spread angle between two pawl arms of a double pawl is so great that it is ensured that during the engagement of the pawl tip of a pawl arm between the other pawl and the ratchet wheel sufficient free play is present. For a certain reliability of the actuator is achieved.
  • an influence of the movement sequence of the double pawl due to the net mass of the double pawl is negligible by the friction clutch.
  • the otherwise labile behavior of the double pawls on the eccentrics is stabilized so far that an uncontrolled influence is excluded by the intrinsic masses of the double pawls.
  • a further embodiment of the invention provides that the guide elements on the double pawls or molded with corresponding rigid abutments corresponding cam tracks are.
  • the friction clutches because of their small friction torque, the double pawls only in the correct sequence for engagement on the bring desired side and to leave the unwanted side, if the pivoting movements of the double pawls are not hindered by external moments on the ratchet wheel. If one reverses, for example, in the course of actuation of a drive shaft, the direction of rotation of the drive shaft, the last engaging or pushing pawl half of a double paw could still be engaged in a high friction between pawl tip and engaging tooth engagement, while the opposite half working with the Double pawl already, in the opposite direction, comes into engagement.
  • the actuating shaft is held by means of locking elements in the switching positions. This avoids that Switch positions due to, for example, magnetic current forces or vibrations of the switching device can be changed.
  • a drive shaft drives the associated eccentric shaft via an existing between the drive shaft and the eccentric gear, in particular a spur gear.
  • a change in direction of the eccentric shaft relative to the drive shaft is achieved, which can be ensured that when turning the drive shaft a corresponding switch closed, and can be opened by turning to the left.
  • dashed lines A and B show two examples of typical electrical functions of branching off one particular medium-voltage switchgear, each with a different switch configuration.
  • the one-stroke scheme A shows a branch with a series connection of a circuit breaker 1 and a circuit breaker 2.
  • a grounding switch 3 is provided which grounds the branch when the circuit breaker 2 and disconnector 1.
  • a switching configuration presupposes that there is a lock which ensures that the circuit breaker 1 only in the de-energized state, ie. H. can be operated with open circuit breaker 2.
  • a further locking is necessary, which ensures that the earthing switch 3 can only be closed when the disconnector 1 is open. This prevents inadvertent grounding of the pantograph when the circuit breaker 1 is closed.
  • the circuit breaker has an actuating device for manual and / or motor drive.
  • the one-stroke diagram B shows a branch with a series connection of a three-position switch 4 and a circuit breaker 2.
  • the three-position switch 4 has three switch positions, namely disconnector ON, disconnector OFF and EARTH. If the circuit-breaker 2 is switched on in the position of the switch EARTH, the feeder will be earthed.
  • the three-position switch 4 does not require a lock between the disconnect and ground functions. However, a lock must nevertheless be present between the circuit breaker 2 and the disconnector functions of the three-position switch 4, which ensures that the disconnector function of the three-position switch 4 can only be actuated in the de-energized state, ie when the circuit breaker 2 is open.
  • the three-position switch 4 has an actuating device 5 for manual and / or motor drive.
  • the invention particularly relates to actuators for those in the Fig. 1 Switching devices shown, namely circuit breaker 1 and three-position switch 4.
  • the actuators according to the invention have in common that they have reversibly driven gear, namely acting in two drive directions ratchet gear.
  • the switching elements of disconnectors or Three-position switches are positively and directly driven and generate their actuators neither leading nor retreating moments.
  • Fig. 2 is an actuator 6 according to the invention, namely shown for a circuit breaker in the front view.
  • the Fig. 3 shows the same actuator 6 in longitudinal section along the line AA.
  • the actuating device 6 in this case has an actuating shaft 7 driving a current path, on whose free end a lever 8 for the transmission of motion is arranged on a switching device.
  • the actuating shaft 7 is coupled via a pawl transmission with a drive shaft 9.
  • the drive shaft 9 is, as in Fig. 3 can be clearly seen, driven by a manually operable crank 11. According to the invention, however, it can also be provided that in addition to the hand crank 11, a drive motor is present.
  • the drive shaft 9 is formed as an eccentric shaft with two eccentrics 12 and 13.
  • the two eccentrics 12 and 13 are offset by an angle of 1800 arranged to each other and are respectively rotatably connected by means of a pin 16 and 17 to the drive shaft 9.
  • each Double pawl 18 and 19 conditionally arranged by means of a frictional friction clutch rotation.
  • the friction clutch is achieved by means of a defined clamping, namely a frictional engagement between an existing on the eccentrics 12 and 13 and flange 21 and 22 between the double pawls 18 and 19 and lock washers 23 and 24 spring washers, such as corrugated springs.
  • the double pawls 18 and 19 have two pawl arms 26, 27, 28 and 29 spread apart by a spread angle, the pawl arms 26, 27, 28 and 29 each having a pawl tip 31 on the side facing away from the drive shaft 9.
  • two ratchet wheels 32 and 33 are arranged rotationally fixed on the actuating shaft 7.
  • a rotatably connected to the actuating shaft 7 intermediate member 34 is present, on which the two ratchet wheels 32 and 33 are secured by means of fastening screws 36.
  • a friction clutch between the double pawls 18 and 19 and the eccentrics 12 and 13 is therefore necessary to ensure that z. B. in a clockwise rotation of Drive shaft 9 actually the right pawl arms 27 and 29 come to the ratchet wheels 32 and 33 for engagement and thus a right-handed drive torque is generated.
  • a frictional connection must be generated via the friction clutches. This frictional engagement must stabilize the otherwise labile behavior of the double pawls 18 and 19 on the eccentrics 12 and 13 to such an extent that an uncontrolled influence by the intrinsic masses of the double pawls 18 and 19 is excluded.
  • the ratchet wheels 32 and 33 have along their circumference a ratchet gear teeth 37, in which the pawl tips 31 of the double pawls 18 and 19 can engage.
  • the ratchet gear teeth 37 of in Fig. 2 clearly recognizable ratchet wheel 32 has three different Klinkenradveriereungsabête 41, 42 and 43.
  • the row of teeth associated with the ratchet gear portion 41 is engaged with the pawl tip 31 of the pawl arm 26 from only one side, and therefore has a bevelled trailing edge 44.
  • the teeth of the row of teeth of Klinkenradveriereungsabitess 42 are acted upon from both sides by the pawl tips 31 of the two pawl arms 26 and 27 of the double pawl 18 and therefore have a Klinkenradunde approximately at right angles trained attack surface 46 for bidirectional loading of the latch tips 31.
  • the teeth of the row of teeth of the Klinkenradveriereungsabitess 43 are acted upon only by the pawl tip 31 of the pawl arm 27 of the double pawl 18, and therefore have on its rear side a beveled edge 44.
  • the ratchet wheel 32 has, as in Fig. 2 clearly recognizable, an untoothed ratchet wheel 47 on. An engagement of a pawl tip 31 in this untoothed portion 47 is not possible, ie in this area a rotation of the actuating shaft 7 is not possible.
  • the ratchet wheel 33 which is arranged parallel to the ratchet wheel 32 and on which the pawl tips 31 of the double pawl 19 engage, corresponds in terms of the geometry of the ratchet teeth 37 to the ratchet wheel 32 and is offset by half a tooth pitch relative to the ratchet wheel 32 on the actuating shaft 7.
  • the teeth are much more stable due to the larger tooth pitch, which is particularly crucial for double-sided acted upon teeth of Klinkenradveriereungsabitess 42.
  • the double pawls 18 and 19, as in Fig. 2 can be clearly seen, designed symmetrically.
  • the double pawl movement of the two double pawls 18 and 19 with rotating drive shaft 9 is guided according to the invention by guide elements, namely of the double pawls 18 and 19 integrally formed cam tracks 51 and 52.
  • These cam tracks 51, 52 correspond to rigid abutments, namely with the two guide screws 53rd and 54. Due to the support of the cam tracks 51 and 52 on the guide screws 53 and 54 takes place with rotating drive shaft 9 always a forced levy of the respective pawl tip 31 from the ratchet teeth 37.
  • the Fig. 2 shows the two pawl arms 18 and 19 in a neutral center position, in which none of the pawl tips 31 is in engagement with the ratchet wheel 32 or 33.
  • a neutral center position does not occur with rotating drive shaft 9, since due to the friction clutch of the double pawls 18 and 19 with the eccentrics 12 and 13 always a force component is present, which causes each a pawl tip 31 is in engagement with the ratchet 37 , As a result, a return of the ratchet wheel 32 or 33 against the direction of rotation of the actuating shaft 7 is excluded in particular.
  • the in the Fig. 2 shown neutral center position of the pawl arms 18 and 19 is, however, go through when changing direction of rotation of the drive shaft 9.
  • the actuator 6, the in Fig. 2 and Fig. 3 is shown is also surrounded by two housing walls 56 and 57, which are mounted by means of four mounting screws 61 with associated spacers 62.
  • the actuating shaft 7 can be rotated back by a output angle of slightly more than 180 ° in one direction and again.
  • the toothed portion of the ratchet wheel 32 extends over slightly more than 270 ° to allow half a revolution of the actuating shaft 7.
  • the teeth of the ratchet wheels 32 and 33 deliberately not led beyond the maximum required area to cause about the lack of further intervention at the same time a Abtriebswinkelbegrenzung, which is just then very advantageous if the drive shaft 9 is driven by a motor and a motor after-run, eg ., May cause no further rotation of the actuating shaft 7 due to the engine flywheel.
  • the drive shaft 9 and the actuating shaft 7 is secured by means of lock washers 63 on the housing 56 and 57.
  • Fig. 4 is the double pawl 18 with the two pawl arms 26 and 27 shown in engagement with the ratchet wheel 32.
  • four different positions of the double pawl 18 are shown at a direction indicated by the arrow 66 clockwise rotation of the eccentrically mounted double pawl 18.
  • the eccentric center moves in a circular path over the four points A, B, C, D.
  • the eccentric center moves from position A to B.
  • This has a movement of the pawl tip 31 of the pawl arm 27 of the position A to the position B result, ie the pawl arm 27 is lifted out of its engaged position, which is effected in particular due to the expiring on the guide screw 53 cam track 51.
  • FIG. 5 is shown another embodiment of an actuator 71 according to the invention, namely for a three-position switch, which connects a branch 72 with a busbar 73 or with an earthing contact 74. It must be provided that each of the two switching operations can be performed by hand from a separate, distinctive drive device. In addition, at the same time an inadmissible switching through, for. B. from the position disconnector ON via the center position disconnector OFF in the position of grounding to be prevented.
  • the actuator 71 has four ratchet wheels 76, 77, 78 and 79, which are arranged parallel to each other on an actuating shaft 81 rotatably.
  • One or more (eg, three) switching elements 82 are connected to the actuating shaft 81, which (in the position shown) separates the branch 72 from the earth contact 74 as well as the busbar 73.
  • FIG. 5 chosen a representation as if the switching element 82 is mounted directly on the actuating shaft 81.
  • the disconnecting switch of the three-position switch 71 is closed and the branch 72 is connected to the busbar 73.
  • the branch 72 is connected to the earth contact 74.
  • the total operating angle of the actuating shaft 81 is in this embodiment at a little more than 180 ° and is generated by the fact that two actuators according to the Fig. 2 and 3 equipped with a modified toothed area and set to the common operating shaft 81. Their initial and final positions are each suitably coordinated with each other, such as in Fig. 5 is shown.
  • This three-position switch actuator 71 after Fig. 5 has two drive shafts 83 and 84 which are independently drivable by means of a hand crank or by a drive motor.
  • On the drive shaft 83 two double pawls 86 and 87 are arranged via two eccentrics, via which the two ratchet wheels 76 and 77 which are arranged offset one half pitch to each other on the actuating shaft 81, are driven. Due to the corresponding Tooth pitch of the ratchet wheels 76 and 77, the operating shaft 81 can be rotated by rotation of the drive shaft 83 only by an angle of slightly more than 90 °, namely in the selected representation of the shown, neutral center position of the switching element 82 to the connection of the switching element 82 with the Earth contact 74.
  • two double pawls 88 and 89 are each disposed on the eccentric on the drive shaft 84.
  • the two left ratchet wheels 78 and 79 are, according to the ratchet wheels 76 and 77, also offset by half a pitch on the actuating shaft 81.
  • the toothing of the two ratchet wheels 78 and 79 is such that via a rotation of the drive shaft 84, the actuating shaft 81 by an angle of only slightly more than 90 ° from the neutral center position of the switching element 82 for closing the circuit breaker, d. H. for connection of the switching elements 82 with the busbar 73, can be rotated.
  • the ratchet wheels 76, 77, 78 and 79 with the corresponding teeth, in which the double pawls 86, 87, 88 and 89 engage, are arranged so that, except for the center position of the actuating shaft 81, the actuating shaft 81 can be driven only by one of the two drive shafts 83 or 84 in each case.
  • the respective non-active drive shaft 83 or 84 then engages with their double pawls 86, 87 or 88, 89 either on edentulous portions of the corresponding ratchet wheel 76, 77, 78 or 79 or on flattened back sides, whereby no rotation of the actuating shaft 81 by the non-active Drive shaft 83 or 84 can be done.
  • FIG. 6 to 10 Another embodiment of an actuator 96 for a three-position switch according to the invention is shown.
  • the three-position switch actuator 96 has, as in Fig. 6 can be seen well, two drive shaft 98 and 99, each with a hand crank 101, being turned off by turning the drive shaft 98 of the earth or turned off by turning left and turned right turn the drive shaft 99 of the separator or turned off in left turn.
  • a position indicator 102 is shown on an actuating shaft 103 in the switch position disconnector OFF, earth OFF.
  • the drive shaft 98 clockwise, the actuating shaft 103 is rotated with the position indicator 102 to the switch position Erder ON.
  • the switching element 102 By clockwise rotation of the drive shaft 99, the switching element 102 is set to the switch position isolator ON.
  • a connected to the actuating shaft 103 via the drive lever 105 linkage 110 leads to the actuated switching elements.
  • Fig. 7 is a section along the line YZ after Fig. 6 shown, wherein the position indicator 102 is rotated by 180 °.
  • the actuating shaft 103 and the rotationally fixed to the actuating shaft 103 connected position indicator 102 can be clearly seen.
  • On the actuating shaft 103 is also a ratchet wheel 104 via Fixing screws 106 rotatably arranged, wherein the ratchet 104 consists of two identical, on the actuating shaft 103 in alignment ratchet wheels 107 and 108 consists. It is obvious in the practical application, instead of the two Klinkenradecheiben 107 and 108 to use an integrally formed, solid ratchet wheel.
  • Fig. 8 is a section through the three-position shift actuator 96 after Fig. 6 shown along the line EF.
  • the drive shaft 98 is formed as an eccentric shaft on which two eccentrics 113 are offset by 180 ° to each other.
  • a double pawl 116 and 117 is formed on the eccentrics 113 by means of a friction clutch conditionally rotatably arranged.
  • a spur gear 118 is arranged, which is an eccentric 119th driving further spur gear 121 meshes.
  • two eccentric 113 are arranged with arranged thereon double pawls 122 and 123 corresponding to the drive shaft 98.
  • the existing between the drive shaft 99 and the eccentric shaft 119, consisting of the two spur gears 118 and 121 gear causes a default is met, which requires that a switch is closed by clockwise rotation of a drive shaft and opened by turning to the left.
  • Fig. 9 is a section of the three-part switch 96 of Fig. 7 shown along the line AB.
  • the ratchet wheel 107 can be clearly seen with the associated ratchet gear.
  • On the ratchet teeth of the ratchet wheel 104 and the two ratchet wheels 107 and 108 is in the description of the Fig. 11 received closer.
  • Fig. 9 are the two ratchet wheel 107 driving double pawls 117 and 123 clearly visible on the respective eccentrics 113.
  • the eccentricity of the eccentric 113 is slightly more than the fourth part of a tooth pitch of the ratchet wheel 104. This ensures that in one revolution of the drive shaft 98 or 99, the ratchet wheel 104 is moved by a tooth pitch and the double pawls 117 and 123 can engage with certainty in the teeth of the ratchet wheel 104.
  • the double pawls 117 and 123 have the peculiarity that they are designed asymmetrically and each have a long pawl arm 126 and a short latch arm 127.
  • the latch arms of the double pawls 117 and 123 are advantageously designed so that the difference between the length of a long pawl arm 126 to a short latch arm 127 is half the pitch of the ratchet wheel 104.
  • Fig. 10 which shows a section through the Fig. 8 is shown along the line CD
  • the double pawls 122 and 116 are configured in accordance with the double pawls 123 and 117, wherein the double pawls 122, 123 and 116, 117 laterally mounted on the eccentric shaft 119 and the drive shaft 98 are mounted.
  • a maximum offset of about 1.2 times a pitch and in the Nachhol ein a game with half the difference between tooth length and 4facher Exzenterhub thus a secure engagement of the double pawls 122, 123 and 116, 117 Even under high load and thus any associated elastic deformations is guaranteed even after a certain wear.
  • One revolution of the drive shaft 98 or 99 thereby gives the actuating shaft 103 a rotation which corresponds to the angle of a tooth pitch. Due to the use of long latch arms 126 and correspondingly short latch arms 127, an offset of the rows of teeth on the ratchet 104, as he according to the embodiments of Fig. 2 and 3 such as Fig. 5 was present, be avoided.
  • Advantage of in the Fig. 6 to 10 illustrated embodiment of the invention is that only a ratchet 104 is used to implement a three-position switch actuator 96.
  • the ratchet wheel 104 and the two ratchet wheels 107 and 108 have a recess 132 along which the Actuating shaft 103 facing away from the border on rotation of the actuating shaft 103, a pin member 133 runs.
  • the pin element 133 is pressed against the ratchet wheel 104 or the ratchet wheel disks 107 and 108 via a flat plate 135 by means of a spring 134.
  • the recess 132 has in the switching positions locking bays 136, in which the pin member 133 engages upon reaching the switching position, whereby the actuating shaft 103 is held in the corresponding switching positions.
  • the pin member 133 is engaged in a latching bay 136. This ensures that magnetic current forces, vibrations or other external forces can not cause a change in the switching position.
  • the pin member 133 is lifted out of the latching bay 136 against the spring force of the spring 134, due to the geometric configuration of the recess 132.
  • rocker arm 137 is clearly shown, which is provided to avoid simultaneous engagement of the double pawls 116, 117 and 122, 123 with simultaneous actuation of the two drive shafts 98 and 99.
  • the rocker arm 137 is rotatably mounted about an axis 138.
  • the function of rocker lever 137 is added in the description of the figures Fig. 12 explained.
  • Fig. 12 In the Fig. 12 are the two identical, aligned parallel and ratchet wheel discs 107 and 108 of the ratchet 104 after the Fig. 7 shown on the actuating shaft 103. Also visible are the double pawls 122 and 116, which are provided for engagement with the ratchet wheel 108, and the double pawls 123 and 117, which cooperate with the ratchet wheel 107.
  • the double pawl 122 and 123 is disposed on the eccentric shaft 119 via a respective eccentric 113, which are arranged offset 180 ° to each other. Accordingly, the two double pawls 116 and 117 are arranged on the drive shaft 98.
  • Fig. 12 In the Fig. 12 is the pawl tip of the short ratchet arm of the double pawl 123 engaged with a tooth edge 154 of the ratchet wheel 107.
  • a rocker lever 137 along the axis of rotation 138 between the respective short latch arms 127 of the two double pawls 123 and 116 is arranged.
  • the neutral center position of the ratchet wheel discs 107 and 108 may be in the in Fig. 12 shown embodiment, only the short pawl arms 127 of the two double pawls 123 and 116 engage tooth flanks on the ratchet wheel 107 and 108, respectively.
  • the long pawl arms 126 of the two double pawls 117 and 122 can not engage in the ratchet wheel teeth 107 and 108 due to lack of tooth flanks in their thrust positions and can thus cause no rotation of the two ratchet wheel disks 107 and 108, respectively. For this reason, a rocker arm 137 is sufficient to avoid the simultaneous engagement of the double pawls 116 and 126 between the short pawl arms 127 of the two double pawls 116 and 123.
  • pins 155 are provided which cooperate with the rocker arm 137 in such a way that only one latch arm can come into engagement with the ratchet wheel disk 107 or 108 on account of the respective rocker arm position.
  • the rocker lever 137 allows for an either-or-engagement. This intervention prevention is required only in the exact center position of the actuator 96. Basically, in this middle position, alternatively, the disconnector or the earthing switch must be able to be operated.

Landscapes

  • Transmission Devices (AREA)
  • Lock And Its Accessories (AREA)
  • Multiple-Way Valves (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Claims (27)

  1. Dispositif d'actionnement (6, 71, 96) destiné à actionner des voies de courant, comportant un arbre d'actionnement (7, 81, 103) actionnant une voie de courant, comportant au moins un arbre d'entraînement (9, 83, 84, 98, 99) commandé par un entraînement et couplé à l'arbre d'actionnement (7, 81, 103) par le biais d'un engrenage, l'entraînement pouvant être une manivelle (11, 101) pouvant être actionnée manuellement et étant en relation d'entraînement avec l'arbre d'entraînement (9, 83, 84, 98, 99) et/ou pouvant être un moteur d'entraînement, l'engrenage étant un engrenage à rochet présentant au moins une roue à rochet (32, 33, 76 - 79, 104, 107, 108) avec une denture de roue à rochet (37) et au moins deux cliquets doubles (18, 19, 86 - 89, 116, 117, 122, 123), la au moins une roue à rochet (32, 33, 76 - 79, 104, 107, 108) étant agencée sur l'arbre d'actionnement (7, 81, 103) de manière à résister à la torsion, l'arbre d'entraînement (9, 83, 84, 98, 99) étant réalisé sous la forme d'un arbre à excentriques ayant au moins deux excentriques (12, 13, 113), les cliquets doubles (18, 19, 86 - 89, 116, 117, 122, 123) présentant deux bras de cliquet (26 - 29) écartés selon un angle d'écartement, les bras de cliquet (26, 27, 28, 29) présentant sur chaque côté orienté à l'opposé de l'arbre d'entraînement (9, 83, 84, 98, 99) une pointe de cliquet (31) ménagée de manière à pouvoir s'engager dans les dentures de roue à rochet (37) de la roue à rochet (32, 33, 104, 107, 108), une pointe de cliquet (31) étant toujours engagée dans la denture de roue à rochet (37) lorsque l'arbre d'entraînement (9, 83, 84, 98, 99) est en rotation, et des éléments de guidage étant présents pour guider le mouvement des cliquets doubles lorsque l'arbre d'entraînement (9, 83, 84, 98, 99) est en rotation, caractérisé en ce qu'il est agencé un cliquet double (18, 19, 86 - 89, 116, 117, 122, 123) sur chacun des au moins deux excentriques (12, 13, 113) de manière résistante à la torsion au moyen d'un accouplement à friction.
  2. Dispositif d'actionnement (6, 71, 96) selon la revendication 1, caractérisé en ce que la denture de roue à rochet (37) présente deux rangées de dents (41, 43) orientées à l'opposé l'une de l'autre afin de recevoir les pointes de cliquet (31) s'engageant dans la denture de roue à rochet (37), les deux rangées de dents (41, 43) pouvant aussi être imbriquées.
  3. Dispositif d'actionnement (6, 71, 96) selon les revendications 1 ou 2, caractérisé en ce que les deux excentriques (12, 13, 113) sont agencés sur l'arbre d'entraînement (9, 83, 84, 98, 99) de manière décalée l'un par rapport à l'autre de préférence selon un angle de 180°.
  4. Dispositif d'actionnement (6, 71) selon l'une des revendications précédentes, caractérisé en ce que les cliquets doubles (18, 19, 86 - 89) sont disposés de façon symétrique et en ce que le pas de dents de la denture de roue à rochet (37) est légèrement inférieur au double de l'excentricité du point central d'excentrique par rapport à l'axe médian de l'arbre d'entraînement (9, 83, 84).
  5. Dispositif d'actionnement (96) selon l'une des revendications 1 à 3, caractérisé en ce que les cliquets doubles (116, 117, 122, 123) sont disposés de manière asymétrique de sorte que le pas de dents de la roue à rochet (104) est légèrement inférieur à quatre fois l'excentricité (98, 99) du point central d'excentrique par rapport à l'axe médian de l'arbre d'entraînement.
  6. Dispositif d'actionnement (6, 71) selon l'une des revendications précédentes, caractérisé en ce que, sur l'arbre d'actionnement (7, 81), il y a au moins deux roues à rochet (32, 33, 76 - 79) agencées parallèlement l'une à l'autre, un cliquet double (18, 19, 86 - 89) étant prévu sur le au moins un arbre d'entraînement (9, 83, 84) pour s'engager dans chaque roue à rochet (32, 33, 76 - 79).
  7. Dispositif d'actionnement (6, 71) selon la revendication 6, caractérisé en ce que les deux cliquets doubles (18, 19, 86 - 89) sont disposés de manière symétrique, en ce que les rangées de dents des dentures de roue à rochet (37) des deux roues à rochet (32, 33, 76 - 79) sont agencées de manière décalée d'un demi pas de dents et en ce que le pas de dents des deux roues à rochet (32, 33, 76 - 79) est légèrement inférieur à quatre fois l'excentricité du point central d'excentrique par rapport à l'axe médian de l'arbre d'entraînement (9, 83, 84).
  8. Dispositif d'actionnement (71, 96) selon l'une des revendications précédentes, caractérisé en ce que le dispositif d'actionnement (71, 96) est réalisé sous la forme d'un dispositif d'actionnement à commutateur à trois positions et présente une position de commutation fermant la voie de courant, une position de commutation coupant la voie de courant et une position de commutation reliant la voie de courant à une prise de terre.
  9. Dispositif d'actionnement (71, 96) selon la revendication 8, caractérisé en ce que, dans la position neutre de l'arbre d'actionnement (81, 103), la voie de courant est coupée, en ce que, dans un angle de rotation de l'arbre d'actionnement (81, 103) d'environ 90° dans un sens de rotation, la voie de courant est fermée, et d'environ 90° dans l'autre sens, la voie de courant est reliée à la terre.
  10. Dispositif d'actionnement (71, 96) selon les revendications 8 ou 9, caractérisé en ce qu'il y a au moins deux arbres d'entraînement (83, 84, 98, 99) pouvant être commandés indépendamment l'un de l'autre avec, agencés dessus, des excentriques (113) et des cliquets doubles (86 - 89, 116, 117, 122, 123), par le biais desquels l'arbre d'actionnement (81, 103) peut être actionné dans les différentes positions de commutation.
  11. Dispositif d'actionnement (71, 96) selon l'une des revendications 8 à 10, caractérisé en ce que les roues à rochet (76 - 79) ou la roue à rochet (104) présentent chacune seulement un segment de rangée de dents pour l'engagement des cliquets doubles de l'arbre d'entraînement actionné (83, 84, 98, 99), de sorte qu'une rotation de l'arbre d'entraînement concerné (83, 84, 98, 99) dans la zone d'engagement duquel les roues à rochet (76 - 79) ou la roue à rochet (104) ne sont pas ou n'est pas peut être réalisée librement sans actionnement de l'arbre d'actionnement (81, 103).
  12. Dispositif d'actionnement (71, 96) selon l'une des revendications 8 à 11, caractérisé en ce que, par la rotation d'un arbre d'entraînement (83, 84, 98, 99), l'arbre d'actionnement (81, 103) ne peut être à chaque fois tourné que d'environ 90° dans un sens et dans l'autre.
  13. Dispositif d'actionnement (96) selon l'une des revendications 8 à 12, caractérisé en ce qu'il y a un dispositif d'empêchement d'engagement, en particulier un levier à bascule (137), afin d'empêcher un engagement simultané des cliquets doubles (116, 117, 122, 123) des deux arbres d'entraînement (98, 99) en cas d'actionnement simultané des deux arbres d'entraînement (98, 99).
  14. Dispositif d'actionnement (71) selon l'une des revendications 8 à 13, caractérisé en ce que les cliquets doubles (86 - 89) présents sur les arbres d'entraînement (83, 84) s'engagent chacun dans différentes roues à rochet (76 - 79) agencées sur l'arbre d'actionnement (81).
  15. Dispositif d'actionnement (96) selon l'une des revendications 8 à 14, caractérisé en ce que les cliquets doubles (116, 117, 122, 123) présents sur les arbres d'entraînement (98, 99) ne s'engagent que dans une roue à rochet (104) agencée sur l'arbre d'actionnement (103).
  16. Dispositif d'actionnement (6, 71, 96) selon l'une des revendications précédentes, caractérisé en ce que la denture de roue à rochet (37) d'une roue à rochet (32, 33, 76 - 79, 104) présente divers segments de denture de roue à rochet (41, 42, 43) avec des rangées de dents au moins partiellement différentes pour l'engagement des différentes pointes de cliquet (31) des cliquets doubles concernés (18, 19, 86 - 89, 116, 117, 122, 123).
  17. Dispositif d'actionnement (6, 71, 96) selon l'une des revendications précédentes, caractérisé en ce que les dents (153) des rangées de dents qui ne sont sollicitées que d'un côté par des pointes de cliquet (31), présentent un flanc arrière biseauté.
  18. Dispositif d'actionnement (6, 71, 96) selon l'une des revendications précédentes, caractérisé en ce que les dents (153) des rangées de dents qui sont sollicitées des deux côtés par des pointes de cliquet (31) présentent des deux côtés une surface d'attaque, en particulier réalisée de manière à peu près orthogonale par rapport au pourtour de roue à rochet, pour la sollicitation des pointes de cliquet (31).
  19. Dispositif d'actionnement (6, 71, 96) selon l'une des revendications précédentes, caractérisé en ce que la roue à rochet (104) ou les roues à rochet (32, 33, 76 - 79) présentent une denture de roue à rochet (37) uniquement par endroits.
  20. Dispositif d'actionnement (6, 71, 96) selon l'une des revendications précédentes, caractérisé en ce que l'application de force des pointes de cliquet (31) a lieu de façon largement tangentielle sur la roue à rochet (32, 33, 76 - 79, 104).
  21. Dispositif d'actionnement (6, 71, 96) selon l'une des revendications précédentes, caractérisé en ce que l'angle d'écartement entre deux bras de cliquet (26 - 29, 126, 127) d'un cliquet double (18, 19, 86 - 89, 116, 117, 122, 123) est d'une grandeur telle qu'il garantit que, pendant l'engagement de la pointe de cliquet (31) d'un bras de cliquet, il y a un jeu suffisant entre l'autre bras de cliquet et la roue à rochet (32, 33, 76 - 79, 104).
  22. Dispositif d'actionnement (6, 71, 96) selon l'une des revendications précédentes, caractérisé en ce que l'accouplement à friction fait que l'influence du déroulement du mouvement du cliquet double, en particulier en raison du poids propre du cliquet double (18, 19, 86 - 89, 116, 117, 122, 123), est négligeable.
  23. Dispositif d'actionnement (6, 71, 96) selon l'une des revendications précédentes, caractérisé en ce que les éléments de guidage sont des chemins incurvés formés sur ou dans les cliquets doubles (18, 19, 86 - 89, 116, 117, 122, 123) et coïncidant avec des butées rigides correspondantes (53, 54, 129).
  24. Dispositif d'actionnement (6, 71, 96) selon la revendication 23, caractérisé en ce que, du fait de l'appui des chemins incurvés (51, 52, 128) sur les butées (53, 54, 129), il se produit en permanence un soulèvement forcé des pointes de cliquet concernées (31) hors de la denture de roue à rochet (37) et, le cas échéant, le soulèvement du cliquet double concerné est commandé par le biais du levier à bascule selon la revendication 13.
  25. Dispositif d'actionnement (96) selon l'une des revendications précédentes, caractérisé en ce que l'arbre d'actionnement (103) est maintenu dans les positions de commutation au moyen d'éléments d'arrêt (133, 136).
  26. Dispositif d'actionnement (6, 71, 96) selon l'une des revendications précédentes, caractérisé en ce que la rotation à droite de l'arbre d'entraînement concerné (9, 83, 84, 98, 99) ferme la position de commutation et la rotation à gauche l'ouvre.
  27. Dispositif d'actionnement (6, 71, 96) selon la revendication précédente, caractérisé en ce qu'un arbre d'entraînement (99) entraîne l'arbre à excentriques associé (119) par le biais d'un engrenage présent entre l'arbre à excentriques (119) et l'arbre d'entraînement (99), en particulier un engrenage à roues droites (118, 121).
EP00118986A 1999-10-23 2000-09-01 Dispositif pour l' actionnement de circuits Expired - Lifetime EP1094479B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19951130 1999-10-23
DE19951130A DE19951130B4 (de) 1999-10-23 1999-10-23 Betätigungseinrichtung zur Betätigung von Strombahnen

Publications (3)

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EP1094479A2 EP1094479A2 (fr) 2001-04-25
EP1094479A3 EP1094479A3 (fr) 2002-12-11
EP1094479B1 true EP1094479B1 (fr) 2009-04-29

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EP00118986A Expired - Lifetime EP1094479B1 (fr) 1999-10-23 2000-09-01 Dispositif pour l' actionnement de circuits

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AT (1) ATE430372T1 (fr)
DE (2) DE19951130B4 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102184800A (zh) * 2011-01-07 2011-09-14 无锡市锡山湖光电器有限公司 用于真空断路器的复合棘轮
DE102011006277B4 (de) 2011-03-28 2012-10-18 Schneider Electric Sachsenwerk Gmbh Einrichtung zur Betätigung von Strombahnen
DE102011081288B4 (de) * 2011-08-19 2019-10-02 Schneider Electric Sachsenwerk Gmbh Leistungsschalter zum Schalten von Mittelspannung und Verfahren zum Betreiben eines solchen Leistungsschalters
DE202012103605U1 (de) 2012-09-20 2014-01-07 Allgäuer Überlandwerk GmbH Mittelspannungs-Schalteinrichtung
DE102012108877B4 (de) 2012-09-20 2015-01-08 Allgäuer Überlandwerk GmbH Mittelspannungs-Schalteinrichtung
GB2556449B (en) * 2017-10-16 2018-10-24 William Hackett Lifting Products Ltd Dual pawl having two pawl arms rotatable about a common axis
CN110161451B (zh) * 2019-06-21 2024-03-12 国网福建省电力有限公司 接表座多表型仓储切换机构及其工作方法

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3475981A (en) 1967-11-20 1969-11-04 Powell Electric Mfg Co Motor operator for load break switch
JPS59189519A (ja) * 1983-04-12 1984-10-27 富士電機株式会社 しや断器操作用蓄勢器の駆動装置
DE19605711C2 (de) * 1996-02-16 2000-03-16 Alstom Sachsenwerk Gmbh Antriebseinrichtung für ein Schaltgerät

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DE19951130A1 (de) 2001-04-26
ATE430372T1 (de) 2009-05-15
EP1094479A3 (fr) 2002-12-11
DE50015632D1 (de) 2009-06-10
DE19951130B4 (de) 2005-09-15
EP1094479A2 (fr) 2001-04-25

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