CH714537A2 - Repetition to mobile disengageable transmission. - Google Patents

Abstract

The invention relates to a repetition mechanism comprising: - a part (10) hours rotated between a rest position and a reading position; - a device (13) for regulating the angular speed of the workpiece (10) hours, which comprises a rotor (15) and a system (60) for braking the rotor; and a gear train (14) for transmitting between the hours part and the rotor (15), said work train comprising a disengageable primary gear (69) capable of adopting two configurations: a) an engaged configuration in which the primary gear (69) couples the rotor hour piece (10) (15) as long as the hour coin moves from its reading position to its home position; b) a disengaged configuration in which the mobile (69) primary uncouples the rotor (15) of the room (10) hours when it stops in the rest position.

Description

Description

Technical Field [0001] 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.

TECHNOLOGICAL BACKGROUND [0002] The repetitive mechanism (commonly referred to simply as repetition) has the function, on command of the user (or wearer) exerting at any moment a pressure on a pusher (or a bolt), to ring the bell. time indicated at this moment by the hands of the timepiece.

[0003] 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.

[0004] A repetition conventionally comprises: a snail of the hours; - A part of the hours provided with a toothed sector and bearing a feeler hours, the hour part being rotated between a fixed rest position, wherein the hours feeler is angularly spaced from the hour snail, and a position of reading in which the feeler of the hours comes in contact with the snail of the hours.

In the absence of action of the wearer, the hour room is in its rest position.

The displacement of the pusher (or the bolt) causes a forced rotation (usually by means of a return spring called spring hours) of the hour room, initially locked in the rest position, to its position of reading.

The release of the pusher (or the bolt) is accompanied by the return of the hour part (usually recalled by a mainspring, which generates a greater return torque to the resisting torque against the spring hours) to its rest position.

[0008] On the way, the hour coin meshes (directly or indirectly) a hammer striking a stamp a number of times equal to the number of hours read on the snail and proportional to the angular stroke traveled by the hour piece 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.

It is therefore understood that, to tinkle the hours fixed frequency, it is necessary to slow down the hour piece to regulate the angular velocity and thus prevent its runaway.

This problem, known for a long time, was first solved by means of an exhaust regulator, described in particular by C.-A. Reymondin et al in Theory of Horology, Federation of Technical Schools, 2015, p. 222 and by F. Lecoultre in Complicated Watches, ed. Simonin, fifth edition, 2013, p. 74 and FIG. 22, Plate 19.

But, as Lecoultre says, 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 levers recalled by springs. This regulator - which is basically a steering wheel of inertia - is summarily described by Lecoultre (op.cit., Pp. 74 and Fig. 23 Plate 19), and in detail by Barbezat-Baillot himself in his patent CH 334 .

The Breguet manufacture was then to perfect this regulator by associating a magnetic brake, which allowed the miniaturiser (European Patent EP 2487 547).

However, 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. It can also be noted that the abrupt stop of the regulator produces, conversely, a counter-blow which is transmitted to the hours coin via the transmission train which amplifies it. This counter-blow (also called hammer) is reflected, on the hour part, by shocks on its sector toothed. Repeated, these shocks induce in the toothed sector mechanical fatigue detrimental to its long-term operation.

A first object of the invention is, in a repetition, to minimize the mechanical fatigue of its moving components.

A second objective is, more specifically, to avoid sudden decelerations of the regulator and water hammers generated in the room hours by its sudden stop at the end of the race. SUMMARY OF THE INVENTION [0017] It is proposed, firstly, a repetition mechanism for a striking timepiece, which comprises: - a snail of the hours; - A part of the hours provided with a toothed sector and bearing a feeler hours, the hour part being rotated between a fixed rest position, wherein the hours feeler is angularly spaced from the hour snail, and a position of reading in which the feeler of the hours comes in contact with the snail of the hours; a device for regulating the angular velocity of the hours part, which comprises a rotor and a braking system of the rotor; - A transmission train interposed between the hour and the rotor, and which comprises a disengageable primary mobile can adopt two configurations: - an engaged configuration in which the primary mobile coupling the hour and rotor part as the hours room moves from its reading position to its rest position; and - a disengaged configuration in which the primary mobile uncouples the rotor and the hours part when it stops in the rest position.

Thus, when the hour part moves from its reading position to its rest position, it drives, via the gear train whose primary mobile is in the engaged configuration, the rotor which regulates the angular speed and allows the ringing of the current time at a fixed frequency. On the other hand, as soon as the hour-piece stops in the rest position, the primary wheel, in the disengaged configuration, allows the rotor to continue to rotate freely, which eliminates shocks due to the stoppage of the workpiece. hours.

According to a particular embodiment, the primary mobile comprises: - a primary input wheel rotatably mounted about a primary axis and connected to the hour piece; a primary output wheel rotatable relative to the input primary wheel and connected to the rotor; and a primary, unidirectional epicyclic gear train interposed between the primary input wheel and the primary output wheel.

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 symmetrical toothing, while the (or each) primary satellite 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 hours part, and a secondary output wheel connected to the primary mobile.

The secondary mobile is preferably disengageable. In this case, the secondary output wheel is e.g. movable in rotation relative to the secondary input gear, and 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 more secondary planet gears rotatably mounted on the secondary output wheel and meshing with the secondary sun gear.

The secondary sun gear is advantageously symmetrical toothing, while the (or each) secondary satellite gear is asymmetrically toothed. The secondary satellite gears are e.g. three in number.

According to one embodiment, 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, secured to the primary input wheel and meshing with the average wheel.

It is proposed, secondly, a timepiece, such as a watch, equipped with a repetition mechanism as presented above.

BRIEF DESCRIPTION OF THE FIGURES [0029] Other objects and advantages of the invention will emerge in the light of the description of an embodiment, given below with reference to the accompanying drawings in which: FIG. 1 is a perspective view partially showing a watch equipped with a replay mechanism; fig. 2 is a perspective view of the repetition mechanism alone, on a larger scale; fig. 3 is a perspective view of the rehearsal mechanism, partially stripped for clarity on its operation; fig. 4 is a perspective view of the mechanism of FIG. 3, according to another angle of view; fig. 5 is an exploded perspective view showing the hour room, the control device and the transmission train, with, in the detail medallion in the lower left, a close-up on the disengageable primary mobile; fig. 6 is an exploded perspective view showing the components of FIG. 5 from another angle of view; fig. 7 is a bottom plan view showing the hour room, the transmission train and the rotor in the rest position of the hours room, before it is actuated; fig. 8 is a plan view from above of the components of FIG. 7; fig. 9 and FIG. 10 are similar views respectively in FIG. 7 and in fig. 8, illustrating the actuation of the hour room, which moves to its reading position; fig. 11 and FIG. 12 are similar views respectively in FIG. 9 and in fig. 10, illustrating the inverse movement of the hour room, and its return towards its rest position; fig. 13 and FIG. 14 are similar views respectively in FIG. 11 and in fig. 12, illustrating the abrupt stoppage of the hours room returned to its rest position.

Detailed Description of the Invention [0030] In FIG. 1 is partially shown a timepiece, in this case a watch 1. The watch 1 comprises a middle part 2 which defines an internal volume 3. In the illustrated example, 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).

The 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 movement further comprises various functional components grouped by subsets. When a subset has a function other than displaying the hours, the minutes and, if necessary, the seconds, it is called "complication".

Thus, 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 "repetition complication Or, more simply (and as used hereinafter), "repetition" 5.

The repetition 5 comprises, in the first place, at least one limaçon 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.

In the illustrated example, the repetition 5 also includes 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 rotation of the snail 8 quarters and which comprises four notched branches on their periphery, separated by smooth junction faces which extend in the extension of the faces of junction of the snail 8 quarters.

The snail 8 quarters carries near its periphery a finger which, at each turn, meshes with a tooth of the star 7 hours to turn it a twelfth of a turn representing a step forward. one o'clock.

Repetition 5 comprises, secondly, a room 10 hours, mounted in rotation about an axis A3 and bearing a probe 11 hours.

The room 10 hours is rotated about its axis A3 between a rest position, wherein the feeler 11 hours is angularly spaced snail 6 hours, and a reading position in which the probe 11 of hours comes in contact with snail 6 hours.

As illustrated in FIG. 3, the hour part 10 comprises a toothed sector 12 coupled to a regulating device 13 (or regulator) via a gear train 14. In the example illustrated, the regulator 13 comprises a rotor 15 rotatably mounted in a stator 16. The regulator 13 will be described in more detail below.

The room 10 hours comprises an outer arm 17 provided with a rake 18 hours consists of twelve protruding teeth. When returning the hours room from its reading position to its rest position, 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. In the illustrated example, 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.

The repetition 5 comprises, in the example illustrated in 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 from the quarter-lima 8, and a reading position in which the quarter feeler comes into contact with the quarter limaçon.

The repetition further comprises, in the example illustrated in 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.

The repetition 5 also includes a spring 26 quarter which remembers the room 22 quarters to its rest position, and a spring 27 minutes reminding the room 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. When returning the play 24 minutes from its reading position to its rest position, 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 part 22 of the quarters is provided on an outer arm, a rake 31 'quarters consisting of three sets of teeth protruding. When the quarterpiece returns from its reading position to its rest position, the quarter rake almost simultaneously operates the hour hammer and the minute hammer to generate a close sequence of two notes. The hour hammer and the minute hammer hit their respective timbres a number of times (between zero and three) equal to the number of tooth series of the rake of the quarters that actuated them when returning from the quarter 22 of the quarters. reading position at its rest position.

As seen in FIG. 2, the room 10 hours, the room 22 quarters and the room 24 minutes, mounted in rotation on the same axis A3, are angularly offset relative to each other, so that when they rotational solidarity around the 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 repetition 5 comprises, fifthly, a barrel 32 ringing. This ringer barrel is rotatably mounted about a cylinder axis A4. The ringer barrel is a subset that includes several components, among which: - a barrel shaft 33; a barrel drum 34; - A barrel spring 35 having an inner end 36 integral with the barrel shaft 33 and an outer end 37 is integral with the drum 34; and - a pulley 38.

The shaft 33 of the barrel, the barrel 34 and the pulley 38 are all rotatably mounted about the barrel axis A4. According to a preferred embodiment, the pulley defines a peripheral cam path 39.

The repetition 5 comprises, sixthly, a chain 40 adapted to partially wind on the pulley 38. More specifically, the chain 40 is able to partially wind on the path 29 of 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.

According to an embodiment illustrated in FIGS. 2 and fig. 3, 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).

As illustrated in FIGS. 2 and fig. 3, the barrel drum 34 carries, on its periphery, a toothed crown 46 with asymmetrical teeth, and the repetition 5 comprises a locking pawl 47 in engagement with this toothed crown 46, to block the rotation of the barrel drum in the direction unwinding of the chain 40.

As shown in FIG. 4, the repetition 5 comprises, seventh place: - a rack 48 rotatably mounted about a fixed rack axis A5, and provided with a sector 49 toothed; and a ring gear train 50 in gear relationship on the one hand with the rack 48 and on the other hand with the barrel shaft 33.

The rack 48 has a hook shape. This rack is provided with a bore 51 through which it is mounted on its axis A5. On either side of this bore, 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 rotatably mounted about its axis A5 between a rest position (FIG 4) and a complete cocking position.

According to an embodiment illustrated in FIG. 4, the ring gear train 50 comprises an input pinion 55 meshing with the rack 48, and an output pinion 56 integral in rotation with the barrel shaft 33.

In the example shown, the ring gear train 50 further comprises a multiplier pinion 57 (partially broken away in FIG 4) integral in rotation with the input pinion 55 and meshing with the output pinion 56.

As can also be seen in FIG. 4, the rack 48 is advantageously provided, at the free end of the toothed sector 49, with an abutment stop 58, which is here in the form of a driven insert, and which, in the fully armed position, the rack, is wedged against the input pinion 55 which thus forms a limit stop for it.

As illustrated in FIG. 1, 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 motor torque on the rack 48, and a position arming device in which the pusher exerts on the rack a thrust (indicated by the white arrow on the bottom left in Fig. 4) generating a motor torque which rotates the barrel shaft 33 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 (in the direction of the arrow X2 in Fig. 3) and the pulley 38 secured thereto. The forced rotation of the rack 48 and the parts that it drives is made against the return torque imposed by the barrel spring 35, the inner end 36 of which rotates with the barrel shaft 33 while the end 37 external remains fixed with the barrel drum 34 blocked by the pawl 47 in engagement with the ring 46 toothed. It is therefore understood that the rotation of the rack 48 has the effect of arming the mainspring.

The chain 40, drawn (in the direction of arrow Y2 in Fig. 3) on the side of its distal end 42 by the piece 10 hours, itself recalled in rotation (in the direction of the arrow Z2 in Fig. 3) to its reading position by the spring 19 of hours, rolls out pulley 38.

Having reached the reading position, in which the feeler 11 hours comes into contact with snail 6 hours, the room 10 hours is stopped, while that, if any, the room 22 quarters and room 24 minutes may 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 of the minutes come into contact, respectively, with the snail 8 quarters and snail 9 minutes.

The release of the pusher 59 releases the barrel spring 35, whose outer end 37 remains fixed with the barrel drum 34 and whose end 36 internally rotates the barrel shaft 33 (in the indicated direction). by the arrow X1 in Fig. 1) and with it the pulley 38 (in the same direction of rotation). As the return torque imposed on the pulley by the mainspring is greater (or even greater) than the resisting torque opposed to the workpiece 10 hours by the spring 19 hours, the pulley 38 draws (in the direction indicated in 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 in FIG. 3 by the arrow Z1, until the hours room reaches its rest position, to which it comes by abutting against the bearing 45 of return, which blocks the repetition 5.

During the race accompanying the release of the pusher 59, 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.

It is for the ringing is performed at a predetermined fixed frequency that the repetition 5 is provided with the device 13 for regulating the angular speed of the workpiece 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.

According to an embodiment illustrated in FIGS. 5 and fig. 6, 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.

In this embodiment, 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 As a result of the centrifugal force, the flyweights 63 are spaced apart from each other and counteract the rotation of the rotor 15 by a higher inertia and thus contribute to braking it (Figs 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.

More specifically, 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 polarity magnets 68 arranged opposite the magnets of the first series so as to form loop-like magnetic field lines 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 part 10 hours during part of its stroke from its reading position to its rest position.

To ensure this drive, the repetition 5 is further provided with a gear train 14, interposed between the workpiece 10 hours and the rotor 15. The gear 14 provides a transmission with gear ratio whose report will be mentioned hereinafter after.

The transmission train comprises a disengageable primary mobile 69 which can adopt two configurations: a) an engaged configuration in which the primary mobile 69 couples the workpiece 10 hours and the rotor 15 as the room 10 hours moves from its reading position at rest position; b) a disengaged configuration in which the primary mobile 69 uncouples the rotor 15 and the room 10 hours when it stops in the rest position.

According to an embodiment illustrated in the figures, and more particularly in FIG. 5, the primary mobile 69 comprises: - a primary input wheel 70, rotatably mounted about a primary axis A7 and connected to the workpiece 10 hours; a primary output wheel 71 rotatable relative to the primary input wheel 70 and connected to the rotor 15; and a primary unidirectional epicyclic train 72 interposed between the primary input wheel 70 and the primary output wheel 71.

In the illustrated example, the primary planetary gear train 72 comprises a primary sun gear 73, integral in rotation with the primary output wheel 71, and one (or more: three in the illustrated example) pinion (s) 74 primary satellite (s) mounted on the primary input wheel 70 and meshing with the primary sun wheel 73.

According to a preferred embodiment, the primary sun gear 73 is symmetrical gear 75, and the (or each) pinion 74 primary satellite is asymmetrical gear 76.

More specifically, and as illustrated in the detail circles at the top in FIGS. 8, fig. 10, fig. 12 and fig. 14, each tooth of the toothing 76 of the primary satellite pinion 74 has a curved front flank 77 and a right posterior flank 78.

In FIGS. 8, fig. 10, fig. 12 and fig. 14, the primary output wheel 71 is partially torn off at its center to show the primary planetary gear 72.

When the primary input wheel 70 is rotated relative to the primary output wheel 71 (integral in rotation with the primary sun wheel 73) such that the toothing 76 of each pinion 74 primary satellite attack the toothing 75 of the primary sun wheel on the side of the rear flanks 78 (detail medal at the top in Fig. 12), the toothing 76 (and therefore the primary planet gear) sticks against the toothing of the wheel primary planetary, which secures in rotation the primary input wheel 70 and the primary sun wheel 73 (and therefore the primary output wheel 71): this is the engaged configuration of the primary mobile 69.

On the other hand, when the primary output wheel 71 (integral in rotation with the primary sun wheel 73) is driven relative to the primary input wheel 70 such as the toothing 75 of the sun gear. The primary attack on the toothing 76 of each primary planet gear 74 on the side of the front flank 77 (detail medal at the top in Fig. 14), the toothing 75 slide on the front flanks 77 of the toothing 76 and the primary sun gear causes the primary satellite gear rotation around its own axis, without driving the primary input wheel is the disengaged configuration of the mobile 69 primary.

According to an embodiment illustrated in the drawings, and more particularly in FIGS. 5, fig. 8, fig. 10, fig. 12 and fig. 14, 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 pinion 80 of secondary input, rotatably mounted about a secondary axis A8 and which meshes the toothed sector 12 of the workpiece 10 hours, and a wheel 81 of secondary output connected to the 69 primary mobile. According to a preferred embodiment, the mobile 79 secondary is disengageable.

For this purpose, in the illustrated example, 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 secondary input gear and the secondary output wheel.

Still in the illustrated example, the secondary epicyclic train 82 comprises a secondary sun gear 83, rotatably connected to the secondary input pinion 80, and one (or more: three in the illustrated example) pinion (s) 84 secondary satellite (s) mounted in rotation on the secondary output wheel 81 and meshing with the secondary sun gear.

According to a preferred embodiment, the secondary sun gear 83 is symmetrical toothing 85, and the (or each) pinion 84 secondary satellite is asymmetrical toothing 86. More precisely, and as illustrated in the detail circles below and to the left in FIGS. 8, fig. 10, fig. 12 and fig. 14, each tooth of the toothing 86 of the secondary planet gear has a curved front flank 87, and a right posterior flank 88.

When the secondary input gear 80 is (with the secondary sun gear 83 which is secured thereto) animated relative rotation with respect to the secondary output wheel 81 such as the toothing 85 of the secondary sun gear attack the toothing 86 of each secondary satellite gear 84 on the side of the posterior flanks 88 (detail medallion at the bottom in Fig. 12), the toothing 86 (and thus the secondary satellite gear 84) sticks against the toothing 85 of the secondary sun gear, which secures in rotation thereof and the secondary output wheel: the mobile 79 secondary then adopts an engaged configuration.

In contrast, when the secondary output wheel 81 is driven relative to the secondary input pinion 80, such that the toothing 86 of each secondary planet gear engages the toothing 85 of the secondary sun gear of side of the anterior flanks 87 (left detail medallion in Fig. 14), the toothing of each secondary satellite gear 84 slides on the anterior flanks of the toothing of the secondary sun gear, the secondary sun gear then rotating freely by compared to the secondary sun gear 83. The secondary output wheel 81 then rotates without driving the secondary sun gear 83 (or the secondary input pinion 80 which is integral with the latter): the secondary mobile 79 then adopts a disengaged configuration.

Moreover, according to a preferred embodiment shown in the drawings from FIG. 4, the gear train 14 also includes an average mobile 89 interposed between the mobile 69 primary and the mobile 79 secondary.

In the illustrated example, the mobile 89 means includes a medium pinion 90 rotatably mounted about a mean axis A9, and a medium wheel 91 rotatably integral with the average pinion 90 and meshing the wheel 70 of primary input of the 69 primary mobile.

Still in the illustrated example, the average wheel 91 does not directly mesh the wheel 70 of primary input. Indeed, the primary mobile 69 comprises a primary pinion 92 integral in rotation with the primary input wheel. It is this primary pinion 92 meshes with the average wheel 91, possibly (as illustrated) with the interposition of a reversing pinion gear 93 rotatably mounted about an inversion axis A10.

Similarly, in the illustrated example, the connection between the primary output wheel 71 and the rotor 15 is via a pinion 94 rotor, fixed in rotation with the rotor and meshing with the output wheel. primary.

Thus, to recapitulate, the kinematic chain which connects the part 10 hours to the rotor 15 comprises successively: - the secondary input pinion 80, which meshes the toothed sector 12 of the room 10 hours; - The secondary output wheel 81, connected to the secondary input gear by the secondary epicyclic gear 82 and which is either integral in rotation (in the engaged configuration of the mobile 79 secondary), or is uncoupled (in the disengaged configuration of the mobile secondary); - The average gear 90, which meshes the secondary output wheel 81; the average wheel 91, integral in rotation with the average pinion 90; - The gear 93 inverter, which meshes the average wheel 91; - The primary gear 92, which meshes the gear 93 inverter; the primary input wheel 70, integral in rotation with the primary pinion 92; the primary output wheel 71, connected to the primary input wheel 70 by the primary epicyclic gear train 72 and which is either integral with it in rotation (in the engaged configuration of the primary mobile unit 69), or is disconnected from it (in the disengaged configuration primary mobile); and - the rotor gear 94, which meshes with the primary output wheel and is integral in rotation with the rotor 15.

We have already explained the actuation of the repetition 5. Previously, the room 10 hours is stationary, wedged against the bearing 45 of return. Similarly, the rotor 15 is stationary, and the same is true of the components of the transmission train 14 (FIG 7, FIG 8).

The rotational movement of the workpiece 10 hours during the actuation of the repetition 5 is illustrated in FIG. 9 (where the hours part is locally torn to the right of the inverter pinion 93, for clarity) and in FIG. 10 by the arrow F1 which indicates the direction.

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 secured thereto ( arrow F2, fiq 9 and Fig. 10).

Under these conditions, and given the mounting direction of the gears 84 secondary satellites, 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 rotating the secondary planet gears in freewheel (arrow F3, detail lock at the bottom of 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.

When the pusher 59 is released, the barrel spring 35 recalls the pulley 38, which pulls the chain 40, which embeds the piece 10 hours, which, from its reading position, is rotated around its axis A3 towards its rest position (arrow F4, Fig. 11 and Fig. 12).

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 sun gear 83 which is secured thereto ( arrow F5, Fig. 11 and Fig. 12).

Under these conditions, and given the mounting direction of the gears 84 secondary satellites, the toothing 85 of the secondary sun gear 83 attack the toothing 86 of the secondary satellite gears 84 on the side of its posterior flank 88, which puts the toothing 86 causes jamming of the secondary planet gears on the secondary sun gear and securing in rotation therewith the secondary output wheel 81 (on which are mounted the secondary satellite gears 84), as illustrated in figs. 11 and fig. 12 by the arrows F6. The secondary mobile 79 is then in its engaged configuration, so that it transmits the rotation of the workpiece 10 hours to the mobile 89 means (arrow F7, Fig. 11 and Fig. 12), which transmits it via the pinion 93 inverter (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).

In view of the direction of mounting of the primary satellite gears 74, their toothing 76 attacks the toothing 75 of the primary sun gear 73 on the side of the posterior flank 78, which puts the toothing 76 in a jamming manner and causes the locking of the teeth. primary planet gears on the primary sun wheel, which is thus rotated in the same direction (arrows F10, Fig. 12). As the primary sun wheel is itself secured to the primary output wheel 71, it is in turn driven in rotation in the same direction (arrow F11, Fig. 11 and Fig. 12).

The primary output wheel 71 engages the rotor gear 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).

Noting: Z12 the number of teeth (referred to its entire circumference) sector 12 teeth of the room 10 hours (here, Z12 = 130), Z80 the number of teeth of the pinion 80 secondary input (here, Z80 = 10) Z81 the number of teeth of the secondary output wheel 81 (here, Z81 = 66), Z90 the number of teeth of the average gear 90 (here, Z90 = 10), Z91 the number of teeth of the average wheel 91 (here, Z91 = 60), Z92 the number of teeth of the primary gear 92 (here, Z92 = 12), Z71 the number of teeth of the primary output wheel 71 (here, Z71 = 55), Z94 the number of teeth of the rotor pinion 94 (here, Z94 = 10), then the transmission ratio R between the hour piece and the rotor 15 is:

For the values of the numbers of teeth provided above, the ratio R of transmission is therefore:

It is thus seen that, for an estimated rotational speed of the workpiece 10 hours of about 1 rpm, the rotor 15 would be driven, if not braked, to about 2360 rpm.

[0108] However, the rotor 15 is braked. Indeed, the flyweights 63 pivot towards 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 increase in inertia which results, and the Laplace force generated by the eddy currents induced by the rotation of the weights 15 in the alternating stationary electromagnetic field prevailing in the stator 16, combine to brake the rotor 15, whose angular velocity is capped at a so-called angular velocity nominal, here of 2300 rpm.

As the primary mobile 69 and the secondary mobile 79 are both in their engaged position, the capping of the angular speed of the rotor 15 is communicated, via the gear train 14, to the workpiece 10 hours whose angular velocity is thus regulated during its movement from its reading position to its rest position. As a result, ringing tones of the current time are produced at fixed frequency (or, at least, with a possible undetectable frequency variation for the human ear).

When the room 10 hours reaches its rest position, it stops dead. As the toothed sector 12 meshes the secondary input pinion 80, the rotation thereof also stops. The same is true of the secondary sun wheel 83 which is integral with it.

However, the secondary output wheel 81 can continue to rotate (arrow F6, Fig. 13 and Fig. 14), because the planet gears 84, driven with this wheel, then attack the secondary sun gear 83 (at the same time). stopping) 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 gear 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 reversing gear 93 (arrow F8, Fig. 13).

The rotation of the secondary output wheel 81 and the average wheel 91 (meshing the inverter gear 93 and the primary gear 92) decreases due to friction.

However, in view of the speed that it has reached and its inertia, the rotor continues to divert (arrow F13, Fig. 13 and Fig. 14), and the decrease in its speed of rotation is less than the decrease in the rotational speed of the average wheel 91.

This is why 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) than the wheel 70. primary input, secured to the primary gear 92 which meshes the average wheel 91 (via the gear 93 inverter). In other words, the primary output wheel is driven relative rotational relative to the primary input wheel. As a result, 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 front flank side. 77 of their toothing 76 and thus drives them in freewheeling rotation (arrow F16, detail medal at the top in Fig. 14), which allows the rotational separation of the primary output wheel 71 and the wheel 70d. primary input, placing the primary mobile 69 in disengaged configuration.

It follows from the foregoing that the part 10 hours is decoupled from the rotor 15, which can (with the wheel 71 primary output) continue to rotate freely despite the immobility of the room hours .

Similarly, the secondary output wheel 81 (and with it the mobile 89 medium and the primary input wheel 70) can continue to rotate freely despite the immobility of the room 10 hours.

This avoids the water hammers generated in the hours room by its sudden stop at the end of the race, since, with the exception of the pinion 80 of the secondary entrance (and the secondary sun gear 83 which is secured to it ), all other moving parts can continue to freewheel until they stop by friction.

The mechanical fatigue of the moving components of the repetition 5 (and in particular of the hour part, the regulating device 13 and the gear train 14) is considerably reduced.

Claims (15)

claims 1. Mechanism (5) for repetition for a timepiece (1) bell, which includes: - snail (6) hours; - a part (10) hours provided with a sector (12) toothed and bearing a probe (11) hours, the part (10) hours being rotated between a fixed rest position, wherein the probe of hours is angularly spaced from the snail (6) hours, and a reading position in which the feeler hours comes into contact with snail (6) hours; - a device (13) for regulating the angular speed of the hour part, which comprises a rotor (15) and a system (60) for braking the rotor; a transmission gear train (14) interposed between the hour piece (10) and the rotor (15); this mechanism (5) for repetition being characterized in that the gear train (14) comprises a movable (69) primary disengageable can adopt two configurations: a) an engaged configuration in which the mobile (69) primary couples the workpiece (10) hours and the rotor (15) as the hours part moves from its reading position to its rest position; b) a disengaged configuration in which the mobile (69) primary uncouples the rotor (15) and the part (10) hours when it stops in the rest position. 2. Mechanism (5) according to claim 1, wherein the mobile (69) primary comprises: - a primary input wheel (70) rotatably mounted about a primary axis (A7) and connected to the workpiece ( 10) hours; - a primary output wheel (71) rotatable relative to the primary input wheel and connected to the rotor (15); and a primary unidirectional epicyclic gear train (72) interposed between the primary input wheel and the primary output wheel. 3. Mechanism (5) according to claim 2, wherein the primary gear (72) epicyclic includes a primary planetary wheel (73) rotatably connected to the primary output wheel (71), and one or more pinions (74) satellite mounted on the primary input wheel (70) and meshing with the primary sun gear. 4. Mechanism (5) according to claim 3, wherein the wheel (73) primary planetary gear is (75) symmetrical, and the or each pinion (74) primary satellite is toothing (76) asymmetric. 5. Mechanism (5) according to claim 3 or claim 4, wherein the primary epicyclic gear (72) comprises three primary satellite gears (74). 6. Mechanism (5) according to one of the preceding claims, wherein the gear train (14) comprises a transmission mobile (79) secondary interposed between the mobile (69) primary and the part (10) hours, this secondary mobile comprising a secondary input gear (80) rotatably mounted about a secondary axis (A8) and which meshes with the tooth sector (12) of the hour coin (10), and a secondary output wheel (81) connected to the primary mobile. 7. Mechanism (5) according to claim 6, wherein the mobile (79) secondary is disengageable. 8. Mechanism (5) according to claim 7, wherein the secondary output wheel (81) is rotatable relative to the secondary input pinion (80), and the secondary mobile (79) comprises a train (82). secondary epicycloid, unidirectional, interposed between the secondary input gear and the secondary output wheel. 9. Mechanism (5) according to claim 8, wherein the secondary epicyclic gear (82) comprises a secondary planetary wheel (83) rotationally fixed to the secondary input pinion (80), and one or more pinions (84) satellite secondary rotatably mounted on the secondary output wheel (81) meshing with the secondary sun gear. 10. Mechanism (5) according to claim 9, wherein the secondary planet wheel (83) is symmetrical toothing (85), and the or each secondary satellite gear (84) is toothing (86) asymmetric. The mechanism (5) of claim 10, wherein the secondary epicyclic gear (82) comprises three secondary planet gears (84). 12. Mechanism (5) according to one of claims 6 to 11, wherein the gear train (14) comprises a transmission means (89) intermediate interposed between the mobile (69) primary and the mobile (79) secondary. 13. Mechanism (5) according to claim 12, wherein the mobile (89) means comprises a mean pinion (90) rotatably mounted about an axis (A9) mean, and a wheel (91) integral with the rotation of the pinion (90) means and meshing the mobile (69) primary. 14. Mechanism (5) according to claim 13, wherein the mobile (69) primary comprises a pinion (92) primary, integral with the wheel (70) primary input and geared by the wheel (91) means. 15. Timepiece (1), such as a watch, equipped with a mechanism (5) for repetition according to one of the preceding claims.