EP3508925A1 - Wiederholung mit beweglicher vorrichtung mit auskuppelbarer übertragung - Google Patents

Wiederholung mit beweglicher vorrichtung mit auskuppelbarer übertragung Download PDF

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Publication number
EP3508925A1
EP3508925A1 EP18150369.9A EP18150369A EP3508925A1 EP 3508925 A1 EP3508925 A1 EP 3508925A1 EP 18150369 A EP18150369 A EP 18150369A EP 3508925 A1 EP3508925 A1 EP 3508925A1
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EP
European Patent Office
Prior art keywords
primary
hours
gear
wheel
mobile
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP18150369.9A
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English (en)
French (fr)
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EP3508925B1 (de
Inventor
Christophe Bifrare
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.)
Montres Breguet SA
Original Assignee
Montres Breguet SA
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 Montres Breguet SA filed Critical Montres Breguet SA
Priority to EP18150369.9A priority Critical patent/EP3508925B1/de
Priority to US16/223,168 priority patent/US11275342B2/en
Priority to JP2018239151A priority patent/JP6797175B2/ja
Priority to CN201910001575.8A priority patent/CN110007583B/zh
Publication of EP3508925A1 publication Critical patent/EP3508925A1/de
Application granted granted Critical
Publication of EP3508925B1 publication Critical patent/EP3508925B1/de
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Anticipated expiration legal-status Critical

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Classifications

    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B21/00—Indicating the time by acoustic means
    • G04B21/02—Regular striking mechanisms giving the full hour, half hour or quarter hour
    • G04B21/12—Reiterating watches or clocks
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B11/00—Click devices; Stop clicks; Clutches
    • G04B11/006—Clutch mechanism between two rotating members with transfer of movement in only one direction (free running devices)
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B11/00—Click devices; Stop clicks; Clutches
    • G04B11/02—Devices allowing the motion of a rotatable part in only one direction
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B21/00—Indicating the time by acoustic means
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B21/00—Indicating the time by acoustic means
    • G04B21/02—Regular striking mechanisms giving the full hour, half hour or quarter hour
    • G04B21/04—Hour wheels; Racks or rakes; Snails or similar control mechanisms

Definitions

  • the invention relates to the field of watchmaking. It concerns, more precisely, a repetition mechanism for a timepiece with a striking ring, the expression "timepiece” preferably designating a watch (with a bracelet or gusset), but which can also designate a clock or a clock clock.
  • the repetitive mechanism (commonly simply called repetition) has the function, on command of the user (or carrier) exerting at any time a pressure on a pusher (or a bolt), to ring the time indicated at that moment by the needles of the timepiece.
  • Repetition is a horological complication of extreme refinement, whose mastery honors the watchmaker who is at the origin. Formerly intended to allow the knowledge of the hour in the darkness, the repetition team nowadays watches of great, even very great value.
  • the movement of the pusher (or bolt) causes a forced rotation (usually by means of a return spring called hours spring) of the hour room, initially locked in the rest position, to its reading position.
  • the release of the pusher (or bolt) is accompanied by the return of the hours coin (usually recalled by a mainspring, which generates a greater return torque to the resisting torque opposed by the spring of hours) to its rest position .
  • the hours room meshes (directly or indirectly) a hammer striking a timbre a number of times equal to the number of hours read on the snail and proportional to the angular travel traveled by the hours room between its two positions (reading , rest).
  • the striking frequency of the hammer is proportional to the speed of rotation of the hour coin. Therefore, if the hour room is left free, it undergoes, when returning to its rest position, an acceleration that increases the frequency of striking the hammer. This phenomenon, called runaway, makes the ringing inaudible when the number of hours to be tinkled increases.
  • the exhaust regulator has the disadvantage of being noisy, which Charles-Ami Barbezat-Baillot resolved in 1889 by replacing it with a centrifugal force regulator comprising a pair of mobile levers recalled by springs. .
  • This regulator - which is basically a flywheel - is described summarily by Lecoultre (op.cit., P.74 and Fig.23 Plate 19), and in detail by Barbezat-Baillot himself in his patent CH 334 .
  • the regulator whether exhaust, centrifugal force or magnetic, can only perform its function properly if it is rotated at a very high speed (of the order of 1000 to 2000 rpm). This speed is achieved by means of a transmission train, which meshes on the one hand the hours part and on the other hand the regulator. The result is a technical problem because, when it reaches its rest position, the hour room stops dead. It then stops the regulator, via the transmission train. It can easily be understood that the regulator then undergoes a strong deceleration. Repeated deceleration induces in the regulator components mechanical fatigue detrimental to their long-term behavior.
  • a first object of the invention is, in a repetition, to minimize the mechanical fatigue of its moving components.
  • a second objective is, more precisely, to avoid the sudden decelerations of the regulator and the hammers generated in the room of the hours by its sudden stop at the end of the race.
  • the hours part when the hours part moves from its reading position to its rest position, it drives, via the transmission train whose primary mobile is in the engaged configuration, the rotor which regulates the angular speed and allows the tinkling of the current time at fixed frequency.
  • the primary mobile since the hours part stops in the rest position, the primary mobile, in disengaged configuration, allows the rotor to continue. its freewheeling rotation, which eliminates the shocks due to the stop of the hours room.
  • the epicyclic primary train comprises e.g. a primary sun gear rotatably secured to the primary output wheel, and one or more primary planet gears mounted on the primary input wheel and meshing with the primary sun gear.
  • the primary sun gear is advantageously symmetrically toothed, while the (or each) primary planet gear is asymmetrically toothed.
  • the primary satellite gears are eg. three in number.
  • the transmission train may further comprise a secondary mobile interposed between the primary mobile and the hours part, this secondary mobile comprising a secondary input gear rotatably mounted about a secondary axis and which meshes the toothed sector of the part. hours, and a secondary output wheel connected to the primary mobile.
  • the secondary mobile is preferably disengageable.
  • the secondary output wheel is e.g. movable in rotation relative to the secondary input gear
  • the secondary mobile comprises a secondary, unidirectional epicyclic gear, interposed between the secondary input gear and the secondary output gear.
  • the secondary epicyclic train comprises e.g. a secondary sun gear rotatably secured to the secondary input gear, and one or a plurality of secondary planet gears rotatably mounted on the secondary output wheel and meshing with the secondary sun gear.
  • the secondary sun gear is advantageously symmetrically toothed, while the (or each) secondary satellite gear is asymmetrically toothed.
  • the secondary satellite gears are e.g. three in number.
  • the transmission train further comprises an average mobile interposed between the primary mobile and the secondary mobile.
  • the average mobile includes e.g. a medium gear rotatably mounted about a mean axis, and a medium wheel integral in rotation of the middle gear and meshing with the primary gear.
  • the primary mobile advantageously comprises a primary gear, integral with the primary input wheel and meshing with the medium wheel.
  • a timepiece such as a watch, equipped with a repetition mechanism as presented above, is proposed.
  • the watch 1 comprises a middle part 2 which defines an internal volume 3.
  • the watch is designed for wearing on the wrist, and its middle comprises for this purpose horns 4 projecting on which is intended to be fixed a bracelet (not shown).
  • Watch 1 includes a watch movement designed to indicate at least hours and minutes.
  • the movement comprises a plate intended to be housed in the internal volume 3 defined by the middle part 2, being attached thereto.
  • the motion further comprises various functional components grouped by subsets.
  • a subset has a function other than displaying the hours, the minutes and, if necessary, the seconds, it is called "complication".
  • the timepiece that is to say the watch 1 illustrated is ringing, and includes, for the purpose of ringing the current time, a repetition mechanism, also called “repetitive complication” or, more simply (and as used hereinafter), “repetition” 5.
  • Repetition 5 comprises, in the first place, at least one snail 6 hours.
  • This snail 6 is rotatably mounted on an axis A1. It has a generally spiral shape and comprises on its periphery a succession of twelve angular sectors of decreasing distances to the axis A1.
  • the snail 6 hours is integral in rotation with a star 7 hours which includes twelve pointed teeth.
  • the repetition 5 also comprises a quarter snail 8, mounted in rotation about an axis A2.
  • the quarter lima 8 comprises four angular sectors of decreasing distances to the axis A2, separated by smooth junction faces.
  • the repetition 5 further comprises a snail 9 minutes, integral in rotation of the quarter snail 8 and which comprises four notched branches on their periphery, separated by smooth junction faces which extend in the extension of the junction faces of the snail 8 quarters.
  • the quarter snail 8 carries in the vicinity of its periphery a finger which, at each turn, comes to mesh a tooth of the star 7 hours to turn it of a twelfth of a turn representing an advance of one hour.
  • the repetition 5 comprises, secondly, a part 10 hours, mounted in rotation about an axis A3 and bearing a probe 11 hours.
  • the part 10 hours is rotated about its axis A3 between a rest position, in which the feeler 11 hours is angularly spaced snail 6 hours, and a reading position in which the probe 11 hours comes to Snail contact 6 hours.
  • the hour part comprises a toothed sector 12 coupled to a regulating device 13 (or regulator) via a gear train 14.
  • the regulator 13 comprises a rotor 15 rotatably mounted in a stator 16. The regulator 13 will be described in more detail below.
  • the part 10 hours comprises an outer arm 17 provided with a rake 18 hours consists of twelve protruding teeth.
  • the hour rake 18 actuates a hammer hours (not shown) which comes to strike a timbre of hours tuned to a predetermined acoustic frequency, possibly amplified by a structural part of the watch 1 (eg the middle part 2).
  • the hour hammer strikes the timbre of the hours a number of times (between one and twelve) equal to the number of teeth of the rake 18 which actuated it when returning the play 10 hours from its reading position to its position rest.
  • Repetition 5 comprises, fourthly, a spring 19 hours, which recalls the room 10 hours to its rest position.
  • the spring 19 hours is a spiral spring. It is advantageously fixed on the hour piece by an inner end, and on an integral axis of the plate by an outer end 21.
  • Repetition 5 comprises, in the example illustrated on the FIG.2 , a quarter-piece 22 bearing a quarter-feeler 23 and mounted in rotation about the axis A3 between a rest position, in which the quarter-feeler is angularly spaced apart from the quarter-lima 8, and a reading position in which the quarter feeler comes into contact with the quarter's snail.
  • the repetition further comprises, in the example illustrated on the FIG.2 a room 24 minutes bearing a minute sensor 25 and rotated about the axis A3 between a rest position, in which the minute sensor 25 is angularly spaced from the snail 9 minutes, and a reading position in which the minute feeler comes into contact with the minute snail.
  • Repetition 5 also includes a quarter spring 26 which recalls the quarter piece 22 towards its rest position, and a spring 27 of the minutes which recalls the coin 24 minutes to its rest position.
  • the room 24 minutes is provided, on an outer arm 28, a rake 29 minutes consisting of fourteen teeth protruding.
  • the minute rake actuates a minute hammer (not shown) which hits a minute timbre tuned to a different predetermined frequency (e.g. lower) than the acoustic frequency of the hour stamp.
  • the minute hammer strikes the timbre a number of times (between zero and fourteen) equal to the number of teeth of the minute rake that actuated it when returning the minute coin from its reading position to its position rest.
  • the quarter piece 22 is provided on an outer arm with a quarter rake 31 consisting of three sets of protruding teeth.
  • a quarter rake 31 consisting of three sets of protruding teeth.
  • the workpiece 10 of the hours, the workpiece 22 of the quarters and the workpiece 24 of the minutes, mounted in rotation on the same axis A3, are angularly offset relative to each other, so that, during their rotation solid around axis A3, the readings intervene successively in the following order: minutes; quarters; hours.
  • the ringing is however performed in the reverse order: hours; quarters; minutes.
  • the barrel shaft 33, the barrel drum 34 and the pulley 38 are all rotatably mounted about the barrel axis A4.
  • the pulley defines a peripheral cam path 39.
  • the repetition 5 comprises, sixthly, a chain 40 able to partially wind up on the pulley 38. More specifically, the chain 40 is able to partially wind up on the path 29 of the cam. This chain is hooked, by a proximal end 41, on the pulley 38 and, by a distal end 42, on the piece 10 hours.
  • the chain 40 comprises a plurality of links 43 articulated with respect to each other.
  • the link located at the proximal end 41 of the chain 40 is fixed on a pin 44 integral with the pulley 38.
  • the link located at the distal end 42 of the chain 40 is fixed to a pin (not visible). integral with the arm 17 outside the room 10 hours.
  • the repetition 5 comprises a return bearing 45 on which the chain 40 passes between the ringer barrel 32 and the hour piece.
  • This bearing 45 of return is advantageously in the form of a bearing (eg ball).
  • the barrel drum 34 carries, on its periphery, a ring gear 46 toothed asymmetrically, and the repetition 5 comprises a locking pawl 47 engaged with the ring gear 46, to block the rotation of the barrel drum in the direction of course of the chain 40.
  • the rack 48 has a hook shape.
  • This rack is provided with a bore 51 through which it is mounted on its axis A5.
  • the rack includes a lever 52 carrying at its end a button 53 (which, in the example illustrated, is attached and driven into a hole formed in the end of the lever), and a arm 54 bent in which is formed the toothed sector 49.
  • the rack is rotated about its axis A5 between a rest position ( FIG.4 ) and a complete arming position.
  • the turn gear 50 comprises an input pinion 55 meshing with the rack 48, and an output pinion 56 integral with the rotation of the barrel shaft 33.
  • the ring gear train 50 further comprises a gear 57 multiplier (partially torn off the FIG.4 ) rotatably connected to the input gear 55 and meshing with the output gear 56.
  • the rack 48 is advantageously provided, at the free end of the toothed sector 49, with a stop stop 58, which is here in the form of a driven insert, and which, in the fully armed position of the rack, is wedged against the input pinion 55 which thus forms a limit stop for it.
  • the watch 1 is equipped with a pusher 59.
  • This pusher 59 is mounted in translation relative to the middle part 2 between a disarmed position, in which the pusher does not exert a driving torque on the rack 48, and a position d arming in which the pusher exerts on the rack a thrust (indicated by the white arrow in the lower left on the FIG.4 ) generating a motor torque which rotates the shaft 33 of the barrel via the wheel gear 50.
  • the actuation of the repetition 5 is effected by pressing the finger on the pusher 59.
  • the pusher pushes the button 53, which via the lever 52 rotates the rack 48 about its axis A5.
  • the rack drives in rotation, by meshing with its toothed sector 49, the input pinion 55, rotation that the multiplier pinion 57, integral with the latter, transmits to the output pinion 56, which drives in its rotation the shaft 33 of barrel (in the direction of the arrow X2 on the FIG.3 ) and the pulley 38 which is integral with it.
  • the chain 40 drawn (in the direction of the arrow Y2 on the FIG.3 ) at the distal end 42 thereof by the hour piece 10, which itself is rotated (in the direction of the arrow Z2 on the FIG.3 ) to its reading position by spring 19 hours, unwind pulley 38.
  • the room 10 hours is stopped, while, where appropriate, the room 22 of the quarters and the room 24 minutes can continue their rotation, respectively biased towards their reading positions by the spring 26 of the quarters and the spring 27 of the minutes, until the feeler 23 of the quarters and the feeler 25 minutes come into contact, respectively, snail 8 quarters and snail 9 minutes.
  • the pulley 38 tows (in the direction indicated on the FIG.3 by the arrow Y1) the chain 40 which is wound therein by driving with it the part of the hours in rotation about its axis A3, in the direction indicated on the FIG.3 by the arrow Z1, until the hours room reaches its rest position, which it reaches by abutting against the bearing 45 of return, which blocks the repetition 5.
  • the room 10 hours, the room 22 of the quarters and the room 24 minutes have, together (and in the manner explained above) sounded the time displayed.
  • the ringing prefferably performed at a predetermined fixed frequency that the repetition 5 is provided with the regulation device 13 the angular velocity of the room 10 hours, hereinafter more simply referred to as "regulator".
  • the regulator 13 comprises, as we have seen, a rotor 15, here in the form of a perforated disc rotatably mounted about an axis A6, and a braking system 60 of the rotor 15.
  • the braking system 60 is combined. More precisely, the braking system 60 is of the magneto-inertial type, that is to say that it comprises an inertial subsystem 61 and a magnetic subsystem 62.
  • the inertial subsystem 61 comprises a pair of flyweights 63 mounted articulated on the rotor 15 between a contracted configuration (adopted when the angular velocity of the rotor 15 is zero, FIG.7 to FIG.10 ), wherein the weights are close to each other and oppose the rotation of the rotor 15 a relatively low inertia, and an expanded configuration (adopted when the angular velocity of the rotor 15 is non-zero) in which, under the effect of the centrifugal force, the weights 63 are spaced from each other and oppose the rotation of the rotor 15 higher inertia and thus contribute to the braking ( FIG.11 to FIG.14 ).
  • One (or more) spring (s) 64 hooked (s) to the weights recalls (s) to their contracted position.
  • the magnetic subsystem 62 comprises the stator 16, which generates an alternating stationary magnetic field in which the rotor 15 and the flyweights 63 are immersed.
  • the stator 16 is provided with a cage 65 carrying, on its periphery, a first series of permanent magnets 66 with alternating polarities, and, fixed on the cage 65, a flange 67 carrying, on its periphery, a second series of permanent magnets 68 with alternating polarities arranged opposite the magnets of the first series, so as to form magnetic field lines which extend in a loop of each pair of magnets 66, 68 facing each neighboring pair.
  • the weights 63 are made of a ferromagnetic material. When the flyweights are rotated in the alternating stationary magnetic field, the latter generates in the flyweights eddy currents which induce a Laplace counter-electromotive force which slows down their rotation (and therefore that of the rotor 15).
  • the rotor 15 is rotated by the workpiece 10 hours during part of its stroke from its reading position to its rest position.
  • the repetition 5 is further provided with a gear train 14, interposed between the part 10 hours and the rotor 15.
  • the gear 14 provides a transmission with gear ratio whose report will be discussed below.
  • the primary planetary gear train 72 comprises a primary sun gear 73, rotationally fixed to the primary output wheel 71, and one (or more: three in the illustrated example) pinion (s) 74 satellite (s) ) primary (s) mounted on the primary input wheel 70 and meshing the wheel 73 primary planetary.
  • the primary sun gear 73 is symmetrically toothed 75
  • the (or each) primary satellite pinion 76 is asymmetrically toothed 76.
  • each tooth of the toothing 76 of the primary satellite gear 74 has a curved front flank 77 and a right posterior flank 78.
  • the primary output wheel 71 is partially torn off at its center to show the primary planetary gear 72.
  • the gear train 14 comprises a secondary mobile 79 interposed between the mobile 69 primary and the room 10 hours.
  • the secondary mobile 79 comprises a secondary input pinion 80 rotatably mounted about a secondary axis A8 and which meshes with the toothed sector 12 of the hour part 10 and a secondary output wheel 81 connected to the mobile 69 primary.
  • the mobile 79 secondary is disengageable.
  • the secondary output wheel 81 is rotatable relative to the secondary input pinion 80, and the secondary mobile 79 comprises a secondary unidirectional epicyclic train 82 interposed between the pinion secondary entrance and the secondary exit wheel.
  • the secondary epicyclic gear 82 comprises a secondary planetary gear 83, rotatably connected to the secondary input pinion 80, and one (or more: three in the illustrated example) pinion (s) 84 satellite ( s) secondary rotatably mounted on the secondary output wheel 81 and meshing with the secondary sun gear.
  • the secondary sun gear 83 is symmetrical toothing 85
  • the (or each) secondary satellite gear 84 is with asymmetrical toothing 86.
  • each tooth of the toothing 86 of the secondary planet gear has a curved front flank 87 and a right posterior flank 88.
  • the secondary input gear 80 is (with the secondary sun gear 83 integral with it) driven by a relative rotation by relative to the secondary output wheel 81 such that the toothing 85 of the secondary sun gear impinges on the toothing 86 of each secondary satellite gear 84 on the side of the posterior flanks 88 (detail medal below on the FIG.12 ), the toothing 86 (and thus the secondary satellite gear 84) engages the toothing 85 of the secondary sun gear, which rotatably secures it and the secondary output wheel: the secondary wheel 79 adopts then an engaged configuration.
  • the gear train 14 also includes an average mobile 89 interposed between the mobile 69 primary and the mobile 79 secondary.
  • the average mobile 89 comprises a mean pinion 90 rotatably mounted about an average axis A9, and a medium wheel 91 integral in rotation with the average pinion 90 and meshing with the wheel 70 of primary input of the mobile 69 primary.
  • the average wheel 91 does not directly mesh with the primary input wheel 70.
  • the primary mobile 69 comprises a primary pinion 92 integral in rotation with the primary input wheel. It is this primary gear 92 that meshes with the average wheel 91, possibly (as illustrated) with the interposition of an inverter gear 93 rotatably mounted about an inversion axis A10.
  • connection between the primary output wheel 71 and the rotor 15 is via a pinion of rotor 94, integral in rotation with the rotor and meshing with the primary output wheel.
  • the rotation of the workpiece 10 hours causes, through the ring gear 12 which meshes the pinion 80 of secondary input, the rotation thereof, with the secondary gear 83 secondary wheel which is integral (arrow F2, FIG.9 and FIG.10 ).
  • the toothing 85 of the secondary sun gear 83 attacks the toothing 86 of the secondary planet gears on the side of its front flank 87 on which the toothing 85 slides, thus causing in rotation the secondary satellite gears freewheeling (arrow F3, detail medallion at the bottom of the FIG.10 ) without driving the secondary output wheel 81.
  • the secondary mobile 79 is then in its disengaged configuration, so that the rotation of the hours part 10 is not transmitted to the rotor 15 which, like the secondary output wheel 81, the average mobile 89 and the primary mobile 69, remain motionless.
  • the secondary mobile 79 is then in its engaged configuration, so that it transmits the rotation of the 10 hours piece to the average mobile 89 (arrow F7, FIG.11 and FIG.12 ), which transmits it via the inverter pinion 93 (arrow F8, FIG.11 ) to the primary gear 92 of the primary mobile 69, and therefore to the primary input wheel 70 which is integral therewith (arrow F9, FIG.11 and FIG.12 ).
  • the primary output wheel 71 engages the rotor pinion 94, which is rotated in the opposite direction (arrow F12, FIG.11 ).
  • the rotor 15, integral in rotation with the pinion 94 of the rotor, is driven with it (arrow F13, FIG.11 and FIG.12 ).
  • the rotor 15 is braked. Indeed, the flyweights 63 pivot to their deployed position (arrow F14, FIG.11 and FIG.12 ) under the effect of the centrifugal force generated by the rotation of the rotor 15.
  • the resulting increase in inertia, and the Laplace force generated by the eddy currents induced by the rotation of the weights 15 in the electromagnetic field alternate stationary prevailing in the stator 16, combine to brake the rotor 15, whose angular velocity is capped at a so-called nominal angular speed, here 2300 rpm.
  • the capping of the angular speed of the rotor 15 is communicated, via the gear train 14, to the workpiece 10 of hours whose angular velocity is thus controlled during its movement from its reading position to its rest position.
  • the secondary output wheel 81 may continue to rotate (arrow F6, FIG.13 and FIG.14 ), because the sprockets 84 satellites, driven with this wheel, then attack the secondary sun gear 83 (stopped) on the side of the front flank 87 of their toothing 86.
  • the planet gears are then rotated in freewheel around their own axis (arrow F15, FIG.14 ).
  • the secondary mobile 79 is then in disengaged configuration, and the secondary output wheel 81 rotates freely.
  • the average wheel 91 (and with it the average pinion 90 which is secured thereto and is engaged by the secondary output wheel 81) also continues to rotate freely (arrow F7, FIG.13 and FIG.14 ).
  • the rotation of the average wheel 91 is transmitted to the primary gear 92 (arrow F9, FIG.13 ) via the inverter gear 93 (arrow F8, FIG.13 ).
  • the rotor 15 continues to rotate (arrow F13, FIG.13 and FIG.14 ), and the decrease in its rotational speed is less than the decrease in the rotational speed of the average wheel 91.
  • the primary output wheel 71 which meshes with the rotor pinion 94 (itself secured to the rotor 15), rotates faster (arrow F11, FIG.13 and FIG.14 ) that the primary input wheel 70, integral with the primary pinion 92 which meshes the average wheel 91 (via the gear 93 inverter).
  • the primary output wheel is driven relative rotational relative to the primary input wheel.
  • the primary sun wheel 73 integral in rotation with the primary output wheel (arrow F10 FIG.14 ), drives the primary satellite gears 74 (mounted on the primary input wheel 70) on the side of the anterior flank 77 of their toothing 76 and thus drives them in freewheeling rotation (arrow F16, detail locket at the top on the FIG.14 ), which allows the disengagement in rotation of the primary output wheel 71 and the primary input wheel 70, placing the primary mobile 69 in disengaged configuration.
  • the secondary output wheel 81 (and with it the mobile 89 medium and the primary input wheel 70) can continue its freewheeling rotation despite the immobility of the room 10 hours.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Transmission Devices (AREA)
  • Electromechanical Clocks (AREA)
  • Measurement Of Unknown Time Intervals (AREA)
EP18150369.9A 2018-01-04 2018-01-04 Wiederholung mit beweglicher vorrichtung mit auskuppelbarer übertragung Active EP3508925B1 (de)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP18150369.9A EP3508925B1 (de) 2018-01-04 2018-01-04 Wiederholung mit beweglicher vorrichtung mit auskuppelbarer übertragung
US16/223,168 US11275342B2 (en) 2018-01-04 2018-12-18 Repeater with disengageable transmission mobile
JP2018239151A JP6797175B2 (ja) 2018-01-04 2018-12-21 係合解除可能な伝達可動部を有するリピーター
CN201910001575.8A CN110007583B (zh) 2018-01-04 2019-01-02 具有可脱离接合的传动运动装置的问时器

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Application Number Priority Date Filing Date Title
EP18150369.9A EP3508925B1 (de) 2018-01-04 2018-01-04 Wiederholung mit beweglicher vorrichtung mit auskuppelbarer übertragung

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EP3508925A1 true EP3508925A1 (de) 2019-07-10
EP3508925B1 EP3508925B1 (de) 2021-12-08

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US (1) US11275342B2 (de)
EP (1) EP3508925B1 (de)
JP (1) JP6797175B2 (de)
CN (1) CN110007583B (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4071561A1 (de) * 2021-04-07 2022-10-12 Patek Philippe SA Genève Repetitionsuhr

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3502794B1 (de) * 2017-12-22 2020-10-21 Montres Breguet S.A. Repetierwerk mit einer auf einer nocke aufgerollten kette
CH716878A1 (de) * 2019-12-02 2021-06-15 Bucherer Ag Schlagwerk, Armbanduhr und Regulator.

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0451339A1 (de) * 1990-04-13 1991-10-16 Iwc International Watch Co. Repetieruhr
DE4120886A1 (de) * 1990-04-13 1993-01-14 Int Watch Co Iwc Repetieruhr
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JP6797175B2 (ja) 2020-12-09
CN110007583A (zh) 2019-07-12
US20190204785A1 (en) 2019-07-04
JP2019120692A (ja) 2019-07-22
CN110007583B (zh) 2021-02-19
EP3508925B1 (de) 2021-12-08

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