EP3203326B1 - Timepiece conversion mechanism of a rotary motion with any amplitude and direction into a one-way motion - Google Patents

Timepiece conversion mechanism of a rotary motion with any amplitude and direction into a one-way motion Download PDF

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Publication number
EP3203326B1
EP3203326B1 EP17151430.0A EP17151430A EP3203326B1 EP 3203326 B1 EP3203326 B1 EP 3203326B1 EP 17151430 A EP17151430 A EP 17151430A EP 3203326 B1 EP3203326 B1 EP 3203326B1
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EP
European Patent Office
Prior art keywords
mobile
conversion mechanism
mechanism according
axis
previous
Prior art date
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EP17151430.0A
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German (de)
French (fr)
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EP3203326A1 (en
Inventor
Mathieu Bonnardin
Jérémy Kress
Christophe Lechot
Martin Sigrist
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Cartier International AG
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Cartier International AG
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    • 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
    • G04B5/00—Automatic winding up
    • G04B5/02—Automatic winding up by self-winding caused by the movement of the watch
    • G04B5/10—Automatic winding up by self-winding caused by the movement of the watch by oscillating weights the movement of which is not limited
    • G04B5/14—Automatic winding up by self-winding caused by the movement of the watch by oscillating weights the movement of which is not limited acting in both directions
    • 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
    • G04B11/006—Clutch mechanism between two rotating members with transfer of movement in only one direction (free running devices)
    • G04B11/008—Clutch mechanism between two rotating members with transfer of movement in only one direction (free running devices) with friction members, e.g. click springs or jumper

Definitions

  • the present invention relates to a clockwork conversion mechanism allowing the conversion of a rotary movement of amplitude and any direction into a unidirectional rotary movement.
  • the winding of the mainspring or barrel spring is effected by means of a mass which oscillates under the effect of the movements of the wearer of the watch.
  • the force generated by the mass oscillations is communicated to the winding spring ratchet by a gear train.
  • Certain automatic winding mechanisms known as “bidirectional”, include, between the oscillating mass and the reduction train, a device called “reverser” allowing the reduction train to rotate in the direction causing the winding of the mainspring whatever the direction of rotation. of the oscillating mass.
  • reverser allowing the reduction train to rotate in the direction causing the winding of the mainspring whatever the direction of rotation. of the oscillating mass.
  • a particularly advantageous type of this reversing device in terms of simplicity, efficiency and size, is known under the name of "Pellaton system" and described in the patent. DE882227 .
  • the Pellaton system comprises a cam secured to the oscillating mass, a rocker cooperating with the cam by means of two rollers, and two pawls mounted on the rocker.
  • the respective spouts of the pawls are kept in contact, by a spring acting between the pawls, with the teeth of a wolf tooth wheel connected to the winding ratchet via the reduction gear train.
  • these two pawls alternately advance the wolf tooth wheel. Variants of this mechanism have been described in the patent. US3846973 and in the requests for patent JP 2003130967 and JP 2003279666
  • the document CH242384 describes a timepiece with automatic winding and by hand, in which a ratchet and a transmission member of the automatic winding device each drive the barrel shaft by means of a freewheel clutch, the two clutches with freewheel being arranged so that the ratchet and said automatic winding member act independently of one another.
  • the invention relates to a conversion mechanism comprising a first mobile driven by any rotary movement, a second mobile, and a transmission member cooperating with the first and second mobile; the first mobile comprising a plate pivoting about an axis and a guide member, the latter being configured to drive the transmission member eccentrically to the axis; the second mobile comprising a clutch member; the transmission member cooperating with the clutch member by bracing intermittently so as to drive the second mobile in a unidirectional rotary movement.
  • the bracing uses a principle of wedging in one direction, which allows us to achieve a clutch in one direction, the direction of wedging, the other direction releasing the moving part, an eccentric for example, from this position bracing.
  • the invention also relates to an automatic winding mechanism of a timepiece comprising the conversion mechanism of the invention as well as a watch comprising such an automatic winding mechanism.
  • This solution has in particular the advantage compared to the prior art to offer better performance, in particular a yield increased as well as a so-called braking angle and so-called dead angle, otherwise called lost path, reduced, all contributing to a better efficiency of the mechanism.
  • a reduction in the forces and torques at the input for the same parameters at the output leads to a reduction in the stresses and an increase in the longevity of the system and of the watch movement which is equipped with it.
  • the figure 1 represents a conversion mechanism intended for a horological application, according to one embodiment.
  • the mechanism comprises a first mobile 3 which can be driven according to any rotary movement (for example bidirectional), a second mobile 5, and a transmission member 4 cooperating with the first and second mobile 3, 5.
  • the first mobile 3 comprises a board 31 pivoting about an axis of rotation 33 and a guide member 32.
  • the guide member 32 is configured to drive the transmission member 4 eccentrically to the axis 33.
  • the second mobile 5 comprises a plate 52, or toothed wheel, driving a clutch member 51. Note that the rotary movement of the first mobile 3 can be unidirectional or bidirectional.
  • the first mobile 3, the board 31 and the guide member 32 can be made in one piece.
  • the conversion mechanism is included in an automatic winding mechanism of a watch comprising an oscillating weight.
  • a ball bearing suspension 1 is shown.
  • An intermediate mobile leading 2 is engaged with a pinion (not shown) secured to the suspension 1.
  • the intermediate moving mobile 2 is also engaged with the board 31 of the first mobile 3 (or driving mobile) so that the rotational movement of the oscillating mass is transmitted to the first mobile 3 by means of the intermediate mobile driving 2.
  • the automatic winding mechanism also comprises an intermediate mobile driven 6 engaged with the board 52 of the second mobile 5 (or driven mobile) and with a barrel ratchet 7.
  • the first mobile 3 can be mounted coaxial with the pivot axis of the oscillating weight, in which case the intermediate driving mobile 2 is not required.
  • the transmission member 4 cooperates with the second mobile 5 by means of the clutch member 51 intermittently, so as to drive the second mobile 5 in a unidirectional rotary movement.
  • the oscillating mass drives, by means of the intermediate mobile 2, the first mobile 3 rotating in both directions according to the rotation of the oscillating mass.
  • the oscillating mass pivoting freely in both directions drives the barrel ratchet 7, by means of the second mobile 5 and the driven intermediate mobile 6, in one direction in order to arm the barrel spring (not shown) .
  • the transmission member 4 comprises two levers 42 extending from the guide member 32 and is terminated by a blocking member 40.
  • the locking member 40 of each of the levers 42 cooperates alternately with the clutch member 51 when the transmission member 4 cooperates with the second mobile 5.
  • the blocking member 40 comprises a movable element 44 cooperating by wedging, blocking or friction with the clutch member 51 when the transmission member 4 cooperates with the second movable 5.
  • the figure 2 shows an isolated view of the transmission member 4 and the clutch member 51.
  • the clutch member 51 comprises a bearing ring 53 provided with a raceway 54.
  • the locking member 40 takes the form of a portion of a ball bearing comprising two housings 45, each housing being configured as a cage portion.
  • the movable element comprises a ball 44 held in the housing 45.
  • the housing 45 has an inclined plane 401 so that, when the locking member 40 cooperates with the raceway 54, the ball 44 gets caught between the raceway bearing 54 and the inclined plane 401 of the housing 45.
  • the inclined plane 401 can be straight or curvilinear.
  • the blocking member 40 can thus drive the second mobile 5.
  • one of the locking members 40 is shown "closed”, that is to say with a support cage 43 enclosing the housings 45 and the balls 44.
  • the other locking member 40 is shown "open", it that is to say without the support cage 43 making it possible to see the housings 45 and the balls 44.
  • the locking member 40 may include a different number of housings 45 and balls 44.
  • the movable element 44 may also include rollers or any other suitable element instead of balls. It will also be noted that a single ball 44 or a single friction cylinder (or roller) per locking member 40 may suffice if the movable element 44 is completed by a friction ratchet (for example mounted on a watch frame) which retains the second mobile 5 in the declining direction.
  • the transmission member 4 and the guide member 32 are configured so that the locking member 40 of each of the levers 42 cooperates with the clutch member 51 intermittently and alternately driving the second mobile 5 in a one direction and avoiding rotation of the second mobile 5 in the opposite direction.
  • the second movable plate 52 can be engaged with a pinion (not shown) coaxial with the bearing ring 53 (as illustrated in the figure 1 ) or be pivotally mounted on the same axis 55 as that of the bearing ring 53.
  • the guide member 32 comprises an articulation element 321 integral with the board 31 of the first mobile 3 and eccentric with respect to the axis of rotation 33.
  • the articulation element 321 makes it possible to guide a rocker 41 on which the levers 42 are fixed.
  • the articulation element may comprise a pivot 322 (comprising a bearing surface) integral with the first mobile 3 and eccentric with respect to the axis of rotation 33 of the first mobile.
  • the lever 41 may include a bore 46 freely engaging around the pivot 322. In this configuration, each of the levers operate in a similar manner to a connecting rod articulated from the pivot 322.
  • a bearing 47 can be inserted between the pivot 322 and the circular bore 46 so as to reduce the friction between the rocker 41 and the pivot 322.
  • the levers 42 comprise a flexible portion 409 (see figure 2 ) can play a virtual pivot role connecting the rocker 41 to the clutch member 40.
  • the guide member 32 comprises a cam mounted concentric with the axis 33 and the radius of which is variable relative to the axis 33.
  • the lever 41 can be guided by the cam.
  • variable radius cam is meant any cam of any geometry, such as an eccentric, an Archimedean spiral heart, a Reuleux cam, a polygon, etc.
  • the figure 3 illustrates the conversion mechanism according to a variant, in which the transmission member 4 comprises a single lever 42 extending from the rocker 41 and is terminated by the locking member 40.
  • the single locking member 40 cooperates intermittently with the clutch member 51 and drives the second mobile 5.
  • a fixed locking element 60 makes it possible to prevent the second mobile 5 from pivoting in the opposite direction to that in which it is driven by the transmission member 4 when the locking member 40 is not in cooperation with the clutch member 51.
  • the fixed blocking element 60 comprises two housings 45, each comprising a ball 45, as illustrated in the figures 1 and 2 .
  • the fixed blocking element 60 can be fixed to a frame of the watch or can be mounted on a second rocker which is fixed while the first rocker is mobile.
  • the figure 4 shows the conversion mechanism again according to another embodiment.
  • the figure 5 shows a perspective view and the figure 6 shows a top view of the transmission member 4 and the second mobile 5 according to the configuration of the figure 4 .
  • the transmission member 4 comprises two rockers 41 each comprising a lever 42.
  • the two rockers 41 are mounted coaxially on a common articulation element 321 (pivot) eccentric relative to the axis 33 of rotation of the first mobile 3.
  • L hinge element 321 guides the two rockers and their respective lever 42 in a movement similar to that of a connecting rod so that the locking member 40 of each of the levers 42 cooperates alternately with the clutch member 51 when the transmission member 4 is driven by the first mobile 3.
  • the two rockers can be made integral with one another, for example using the driving fingers 34.
  • the locking member 40 comprises a rocker 403 itself pivotally mounted on a pivot 402 at the end of each lever 42 and on the axis 55 of the rolling ring 53.
  • the movement of the levers 42 driven by the first mobile 3 rotates the locking member 40 so that each of the two locking members 40 cooperates alternately and drives the second mobile 5.
  • the figure 7 illustrates a variant of the mechanism for converting Figures 4 and 5 comprising a single lever 41 comprising a lever 42.
  • the conversion mechanism also comprises a fixed blocking element 60 configured as in the example of the figure 3 .
  • the figures 8 to 10 show the operation of the conversion mechanism according to the configuration of figures 4 to 6 .
  • the figure 8 shows the conversion mechanism in an initial position.
  • the figure 9 shows the conversion mechanism when the articulation element 321, guided by the axis 33, is pivoted 90 ° counterclockwise from the initial position.
  • the levers 42 pivot a rocker 403 counterclockwise forcing the balls 44 to be housed in the narrow part of the housing 45 and to be wedged between the inclined plane of the housing 401, so that the locking member 40 cooperates with the clutch member 51 by bracing and driving it in a counterclockwise rotary movement.
  • the other lever 403 ′ pivots clockwise so that the balls 44 are located in the wide part of the housing 45 and can freely roll in the housing 45.
  • the direction of rotation of the driving members (the axis 33 and the locking members 40) is indicated by the solid arrows and the direction of rotation of the driven members (the articulation element 321 and the clutch member 51 ) is indicated by the dotted arrows.
  • the figure 10 shows the conversion mechanism when the hinge member 321 is rotated 270 ° counterclockwise from the initial position.
  • the lever 403 pivots clockwise and the balls 44 roll freely in the wide part of the housing 45.
  • the lever 403 'pivots counterclockwise forcing the balls 44 to be housed in the narrow part of the housing 45 so that the locking member 40 drives the clutch member 51 in a counterclockwise rotary movement.
  • the figure 11 represents the conversion mechanism according to another embodiment and the figure 12 shows a perspective view and the figure 13 shows a top view of the transmission member 4 and the second mobile 5 depending on the configuration of the figure 11 .
  • the transmission member 4 comprises a rocker 41 comprising two levers 42.
  • the rocker 41 is guided by a pivot 32 secured to the first mobile 3 and eccentric with respect to the axis of rotation 33 of the first mobile 3, as in the configuration of the figure 1 .
  • the locking member 40 comprises two unidirectional ball bearings 43, 43 ', each of the bearings being pivotally guided on a pivot 402 at the end of a lever 42.
  • Each of the bearings 43, 43' comprises a coaxial outer ring with an inner ring and a cage.
  • the cage with housings having an inclined plane (the rings, the cage and the housings are not visible on the figures 11 to 13 ).
  • the coupling between the outer and inner rings of the bearing is carried out in a single direction of rotation of the bearing, when the balls are blocked by wedging between the outer ring and the walls of the housings.
  • the second mobile 5 In the case where the second mobile 5 is integral with the second mobile 5, for example via the axis 55 of the second mobile, the second mobile 5 will be driven in rotation by one of the two bearings 43, 43 ′ rotating in one direction (for example counterclockwise, as indicated by the arrows in the figures 11 to 13 ) and will be in free rolling with the other bearings 43, 43 'rotating in the opposite direction.
  • the figure 14 represents the conversion mechanism according to another embodiment in which the clutch member 51 comprises a disc 57 pivoting concentrically with the axis 55 of a pinion 52 'of second mobile 5, the pinion 52' being intended to mesh with the plate 52 of the second mobile 5.
  • the transmission member 4 comprises two rockers 41, each comprising a lever 42.
  • the two rockers 41 are each mounted on a pivot 322 eccentric with respect to the axis 33 of rotation of the first mobile (not shown on the figure 14 ).
  • Each of the levers 42 is terminated by a blocking element support 404 comprising a blocking element (blocking eccentrics) 406 having a variable radius.
  • the locking eccentric is guided by a pin 407.
  • the configuration of the transmission member 4 is such that the locking element supports 404 are arranged on each side of the disc 57.
  • the locking eccentrics 406 come into contact with the edge 57 'of the disc 57 alternately with the edge 57' of the disc 57 so that, depending on the direction of driving the levers 42, each of the locking eccentrics 406 pivots and jams against the disc 57 by bracing.
  • the second mobile 5 is thus driven in one direction.
  • the cams 33 of the rockers are ideally offset between them, with a phase shift between their respective centers relative to the center of the pivot 322 ranging from 0 ° to 180 °.
  • each lever 42 has a flexible bend 405, in other words a virtual pivot, making it possible to guide the blocking element supports 404 so as to keep the blocking eccentrics 406 in contact with the edge 57 ′ of the disc 57 when the member blocking 40 cooperates with the second mobile 5.
  • the locking eccentric 406 can be kept in contact against the edge 57 'when the locking member 40 cooperates with the clutch member 51 using a spring 408, integrated with the locking eccentric 406 in this configuration.
  • the figure 15 illustrates the conversion mechanism of the figure 11 , according to another variant in which the locking eccentric 406 is separated from the return spring 408.
  • the locking eccentric comprises a cam 406 pivotally mounted on a pivot 407.
  • the figure 16 shows a variant of the conversion mechanism of the figure 15 , in which the transmission member 4 comprises a single lever 41 and a single lever 42 comprising a locking eccentric 406 with its return spring 408.
  • a fixed locking element 60 makes it possible to prevent the second mobile 5 from pivoting in the opposite direction to that in which it is driven by the transmission member 4 when the locking member 40 is not in cooperation with the clutch member 51.
  • the fixed blocking element 60 comprises a cam 606 pivoting around a pivot 607 and kept in contact with the edge 57 ′ of the disc 57 using a return spring 608.
  • the cam 606 can be mounted on a frame of a watch movement.
  • the figure 17 shows a variant of the conversion mechanism in which the latter is produced with a reduced number of parts, in particular by the combination of the functions of eccentric input guidance, movement transmission by an arm, pivot function of this arm by flexible element and arc pushing against the receiving disc in a single piece.
  • the proposed assembly could however, as in certain previous versions, be carried out on two levels to separate two connecting rod arms.
  • the bracing is always carried out on a movable element in rotation around a virtual pivot, this pivot preferably being a fixed pivot relative to a reference frame of the arm supporting it.
  • they can be guided by an arm movable in rotation around the axis of the output mobile.
  • the transmission member 4 comprises two levers 42, each extending from a rocker 41 pivotally mounted on the guide member 32, and terminated by a locking member 40.
  • the clutch member 51 comprises a disc 57 (only half of the disc is represented in the figure 17 ) pivoting concentrically with the axis 55 of a pinion 52 'of the second mobile 5.
  • Each of the locking members 40 comprises a flexible element 410 capable of coming into abutment against the edge 57' of the disc 57 in bracing relationship. .
  • the flexible element 410 is formed in one piece with the lever 42 and the rocker 41.
  • the bracing is obtained by the fact that each of the levers 42 is pivotally mounted on a movable element 501 in rotation around the common axis 55 of the pinion 52 'and the disc 57, by means of a pivot 402.
  • the eccentricity of the transmission member 4 is defined by the distance between the axis of rotation 33 of the first mobile 3 and the center 35 of the guide member 32 (see for example the figure 8 ).
  • the organ of guide 32 comprises a second eccentric element 36 which can move relative to the guide member 32.
  • the second eccentric element 36 can be oriented in rotation around the center 37 of the opening of the guidance 32.
  • the figure 18a shows the second eccentric element 36 arranged so as to maximize the eccentricity, that is to say a maximum distance between the axis of rotation 33 (A) of the first mobile 3 and the center 35 (B) of the member guide 32.
  • this distance AB is zero and the maximum distance between the axis of rotation 33 of the first mobile 3 and the center 35 of the guide member 32 is zero.
  • the pivoting of the second eccentric element 36 results in an intermediate eccentricity (distance AB).
  • the border between the second eccentric element 36 and the guide member 32 can be continuous as illustrated in the figures 18a to 18c , allowing continuous adjustment of the degree of eccentricity.
  • the border between the second eccentric element 36 and the guide member 32 can also have a non-continuous interface, for example fluted or faceted, as illustrated in FIG. figure 18d , allowing adjustment of the degree of eccentricity in steps, or even having any other suitable form.
  • the variation in the degree of eccentricity of the transmission member 4 makes it possible to vary the transmission speed / torque parameters of the conversion mechanism.
  • the variation in the degree of eccentricity of the transmission member 4 makes it possible to adapt the conversion mechanism of the invention of watch calibers having different characteristics (winding speed, barrel spring torque, etc.). It also makes it possible to adapt the conversion mechanism to extreme conditions of winding the watch, for example in the case of wearing that is too dynamic or, on the contrary, too static, therefore to the winding conditions defined by their wearer. It also makes it possible to adapt the conversion mechanism to the winding parameters to any other situation likely to require its application.
  • the clutch member 51 is arranged so as to pivot slightly eccentrically relative to the axis of rotation 55 of the second mobile 5.
  • the figure 19 shows an example where the locking member 40 takes the form of a portion of a ball bearing, where the ball 44 is wedged between the bearing ring 53 and the slope of the cage 45, this slope can be linear or curvilinear.
  • the figure 20 shows an example where the blocking member 40 comprises a blocking eccentric 406.
  • the eccentricity is illustrated by the dotted line in the figures.
  • the eccentricity causes the blocking / friction of the movable element 44 (blocking eccentric 406, etc.) to be distributed over a larger portion of the surface of the cage element 45.
  • the occurrence of repeated contacts locking / friction at the same locations on the surface can thus be reduced significantly compared to a configuration where the clutch member 53, 57 pivots concentrically with respect to the axis of rotation 55.
  • the effects of dulling or d wear due to pressures on the cage element 45 are minimized. Such an arrangement can be achieved without significantly disturbing the winding parameters (in the case where the conversion mechanism is used in an automatic watch winding mechanism).
  • Another way of distributing the stresses and wear on different portions of the locking eccentric 406 or of the cage element 45 consists in using a clutch disc 53 concentric with its center of rotation 55, in giving said clutch disc 53 a slightly oval shape, for example of the ellipsoidal type, or any other geometry varying slightly the distance defined between the point of contact with the locking element 406, 44 and the center of rotation 55.
  • the conversion mechanism can also be used in any other transmission device which requires the conversion of a bidirectional movement into a unidirectional movement.

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  • General Physics & Mathematics (AREA)
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Description

Domaine techniqueTechnical area

La présente invention concerne un mécanisme horloger de conversion permettant la conversion d'un mouvement rotatif d'amplitude et de sens quelconque en un mouvement rotatif unidirectionnel.The present invention relates to a clockwork conversion mechanism allowing the conversion of a rotary movement of amplitude and any direction into a unidirectional rotary movement.

Etat de la techniqueState of the art

Dans un mouvement d'horlogerie à remontage automatique, le remontage du ressort moteur ou ressort de barillet s'effectue au moyen d'une masse qui oscille sous l'effet des mouvements du porteur de la montre. La force générée par les oscillations de la masse est communiquée au rochet de remontage du ressort moteur par un rouage réducteur. Certains mécanismes de remontage automatique, dits « bidirectionnels », comprennent, entre la masse oscillante et le rouage réducteur, un dispositif appelé « inverseur » permettant au rouage réducteur de tourner dans le sens entraînant le remontage du ressort moteur quel que soit le sens de rotation de la masse oscillante. Un type particulièrement avantageux de ce dispositif inverseur, en termes de simplicité, d'efficacité et d'encombrement, est connu sous le nom de « système Pellaton » et décrit dans le brevet DE882227 . Le système Pellaton comprend une came solidaire de la masse oscillante, une bascule coopérant avec la came par l'intermédiaire de deux galets, et deux cliquets montés sur la bascule. Les becs respectifs des cliquets sont maintenus en contact, par un ressort agissant entre les cliquets, avec la denture d'une roue à dents de loup reliée au rochet de remontage par l'intermédiaire du rouage réducteur. Sous l'effet des mouvements oscillants de la bascule, causés par les rotations de la came, ces deux cliquets font alternativement avancer la roue à dents de loup. Des variantes de ce mécanisme ont été décrites dans le brevet US3846973 et dans les demandes de brevet JP 2003130967 et JP 2003279666 In an automatic winding watch movement, the winding of the mainspring or barrel spring is effected by means of a mass which oscillates under the effect of the movements of the wearer of the watch. The force generated by the mass oscillations is communicated to the winding spring ratchet by a gear train. Certain automatic winding mechanisms, known as “bidirectional”, include, between the oscillating mass and the reduction train, a device called “reverser” allowing the reduction train to rotate in the direction causing the winding of the mainspring whatever the direction of rotation. of the oscillating mass. A particularly advantageous type of this reversing device, in terms of simplicity, efficiency and size, is known under the name of "Pellaton system" and described in the patent. DE882227 . The Pellaton system comprises a cam secured to the oscillating mass, a rocker cooperating with the cam by means of two rollers, and two pawls mounted on the rocker. The respective spouts of the pawls are kept in contact, by a spring acting between the pawls, with the teeth of a wolf tooth wheel connected to the winding ratchet via the reduction gear train. Under the effect of the oscillating movements of the rocker, caused by the rotations of the cam, these two pawls alternately advance the wolf tooth wheel. Variants of this mechanism have been described in the patent. US3846973 and in the requests for patent JP 2003130967 and JP 2003279666

Le document CH242384 décrit une pièce d'horlogerie à remontage automatique et à la main, dans lequel un rochet et un organe de transmission du dispositif de remontage automatique entrainent chacun l'arbre de barillet par l'intermédiaire d'un embrayage à roue libre, les deux embrayages à roue libre étant disposés de façon que le rochet et ledit organe de remontage automatique agissent indépendamment l'un de l'autre.The document CH242384 describes a timepiece with automatic winding and by hand, in which a ratchet and a transmission member of the automatic winding device each drive the barrel shaft by means of a freewheel clutch, the two clutches with freewheel being arranged so that the ratchet and said automatic winding member act independently of one another.

Bref résumé de l'inventionBrief summary of the invention

L'invention concerne un mécanisme de conversion comprenant un premier mobile entraînable selon un mouvement rotatif quelconque, un second mobile, et un organe de transmission coopérant avec le premier et le second mobile; le premier mobile comprenant une planche pivotant autour d'un axe et un organe de guidage, ce dernier étant configuré pour entraîner l'organe de transmission de manière excentrée par rapport à l'axe; le second mobile comportant un organe d'embrayage; l'organe de transmission coopérant avec l'organe d'embrayage par arc-boutement de façon intermittente de manière à entraîner le second mobile selon un mouvement rotatif unidirectionnel. L'arc-boutement fait appel à un principe de coincement dans un sens, ce qui nous permet de réaliser un embrayage dans un sens, le sens de coincement, l'autre sens libérant la pièce mobile, un excentrique par exemple, de cette position d'arc-boutement.The invention relates to a conversion mechanism comprising a first mobile driven by any rotary movement, a second mobile, and a transmission member cooperating with the first and second mobile; the first mobile comprising a plate pivoting about an axis and a guide member, the latter being configured to drive the transmission member eccentrically to the axis; the second mobile comprising a clutch member; the transmission member cooperating with the clutch member by bracing intermittently so as to drive the second mobile in a unidirectional rotary movement. The bracing uses a principle of wedging in one direction, which allows us to achieve a clutch in one direction, the direction of wedging, the other direction releasing the moving part, an eccentric for example, from this position bracing.

Plusieurs modes de réalisation et variantes sont décrits dans les revendications dépendantes.Several embodiments and variants are described in the dependent claims.

L'invention concerne également un mécanisme de remontage automatique d'une pièce d'horlogerie comprenant le mécanisme de conversion de l'invention ainsi qu'une montre comprenant un tel mécanisme de remontage automatique.The invention also relates to an automatic winding mechanism of a timepiece comprising the conversion mechanism of the invention as well as a watch comprising such an automatic winding mechanism.

Cette solution présente notamment l'avantage par rapport à l'art antérieur d'offrir de meilleures performances, notamment un rendement accru ainsi qu'un angle dit de freinage et angle dit mort, autrement appelé chemin perdu, réduits, le tout contribuant à une meilleure efficacité du mécanisme. D'autre part, une réduction des forces et couples à l'entrée pour les mêmes paramètres à la sortie conduit à une réduction des contraintes et un accroissement de la longévité du système et du mouvement horloger qui en est équipé.This solution has in particular the advantage compared to the prior art to offer better performance, in particular a yield increased as well as a so-called braking angle and so-called dead angle, otherwise called lost path, reduced, all contributing to a better efficiency of the mechanism. On the other hand, a reduction in the forces and torques at the input for the same parameters at the output leads to a reduction in the stresses and an increase in the longevity of the system and of the watch movement which is equipped with it.

Brève description des figuresBrief description of the figures

Des exemples de mise en œuvre de l'invention sont indiqués dans la description illustrée par les figures annexées dans lesquelles:

  • la figure 1 représente un mécanisme de conversion destiné à une application horlogère comprenant un organe excentrique, un organe de transmission et un organe d'embrayage, selon un mode de réalisation;
  • la figure 2 montre une vue isolée de l'organe de transmission et de l'organe d'embrayage, selon un mode de réalisation;
  • la figure 3 représente un mécanisme de conversion, selon un autre mode de réalisation;
  • la figure 4 montre un mécanisme de conversion, selon un autre mode de réalisation;
  • les figures 5 et 6 montrent une vue en perspective (figure 5) et du dessus (figure 6) de l'organe de transmission selon la configuration de la figure 4;
  • la figure 7 illustre le mécanisme de conversion des figures 4 à 6 selon une variante;
  • les figures 8 à 10 montrent le fonctionnement du mécanisme de conversion selon la configuration des figures 4 à 6;
  • la figure 11 représente le mécanisme de conversion selon un autre mode de réalisation;
  • les figure 12 et 13 montrent une vue en perspective (figure 12) et du dessus (figure 13) de l'organe de transmission, selon la configuration de la figure 11;
  • la figure 14 montre le mécanisme de conversion, encore selon un autre mode de réalisation;
  • la figure 15 montre le mécanisme de conversion, encore selon un autre mode de réalisation;
  • la figure 16 illustre le mécanisme de conversion de la figure 15, selon une autre variante;
  • la figure 17 montre une variante du mécanisme de conversion;
  • les figures 18a à 18d montrent un mobile excentrique, selon un mode de réalisation; et
  • les figures 19 et 20 représentent un organe d'embrayage arrangé excentriquement, selon un mode de réalisation.
Examples of implementation of the invention are indicated in the description illustrated by the appended figures in which:
  • the figure 1 represents a conversion mechanism intended for a horological application comprising an eccentric member, a transmission member and a clutch member, according to one embodiment;
  • the figure 2 shows an isolated view of the transmission member and the clutch member, according to one embodiment;
  • the figure 3 represents a conversion mechanism, according to another embodiment;
  • the figure 4 shows a conversion mechanism, according to another embodiment;
  • the figures 5 and 6 show a perspective view ( figure 5 ) and from above ( figure 6 ) of the transmission member according to the configuration of the figure 4 ;
  • the figure 7 illustrates the mechanism for converting figures 4 to 6 according to a variant;
  • the figures 8 to 10 show the operation of the conversion mechanism according to the configuration of figures 4 to 6 ;
  • the figure 11 represents the conversion mechanism according to another embodiment;
  • the figure 12 and 13 show a perspective view ( figure 12 ) and from above ( figure 13 ) of the transmission member, depending on the configuration of the figure 11 ;
  • the figure 14 shows the conversion mechanism, again according to another embodiment;
  • the figure 15 shows the conversion mechanism, again according to another embodiment;
  • the figure 16 illustrates the conversion mechanism of the figure 15 , according to another variant;
  • the figure 17 shows a variant of the conversion mechanism;
  • the figures 18a to 18d show an eccentric mobile, according to one embodiment; and
  • the Figures 19 and 20 represent a clutch member arranged eccentrically, according to one embodiment.

Exemple(s) de mode de réalisation de l'inventionExample (s) of embodiment of the invention

La figure 1 représente un mécanisme de conversion destiné à une application horlogère, selon un mode de réalisation. En particulier, le mécanisme comprend un premier mobile 3 entraînable selon un mouvement rotatif quelconque (par exemple bidirectionnel), un second mobile 5, et un organe de transmission 4 coopérant avec le premier et le second mobile 3, 5. Le premier mobile 3 comprend une planche 31 pivotant autour d'un axe de rotation 33 et un organe de guidage 32. L'organe de guidage 32 est configuré pour entraîner l'organe de transmission 4 de manière excentrée par rapport à l'axe 33. Le second mobile 5 comporte une planche 52, ou roue dentée, entraînant un organe d'embrayage 51. Remarquons que le mouvement rotatif du premier mobile 3 peut être unidirectionnel ou bidirectionnel.The figure 1 represents a conversion mechanism intended for a horological application, according to one embodiment. In particular, the mechanism comprises a first mobile 3 which can be driven according to any rotary movement (for example bidirectional), a second mobile 5, and a transmission member 4 cooperating with the first and second mobile 3, 5. The first mobile 3 comprises a board 31 pivoting about an axis of rotation 33 and a guide member 32. The guide member 32 is configured to drive the transmission member 4 eccentrically to the axis 33. The second mobile 5 comprises a plate 52, or toothed wheel, driving a clutch member 51. Note that the rotary movement of the first mobile 3 can be unidirectional or bidirectional.

Le premier mobile 3, la planche 31 et l'organe de guidage 32 peuvent être constitués d'une seule pièce.The first mobile 3, the board 31 and the guide member 32 can be made in one piece.

Dans l'exemple de la figure 1, le mécanisme de conversion est compris dans un mécanisme de remontage automatique d'une montre comprenant une masse oscillante. Dans la figure, seule une suspension 1 à roulement à billes est représentée. Un mobile intermédiaire menant 2 est en prise avec un pignon (pas représenté) solidaire de la suspension 1. Le mobile intermédiaire menant 2 est également en prise avec la planche 31 du premier mobile 3 (ou mobile menant) de sorte que le mouvement de rotation de la masse oscillante est transmis au premier mobile 3 par le biais du mobile intermédiaire menant 2. Le mécanisme de remontage automatique comprend également un mobile intermédiaire mené 6 en prise avec la planche 52 du second mobile 5 (ou mobile mené) et avec un rochet de barillet 7. Alternativement, le premier mobile 3 peut être monté coaxial avec l'axe de pivotement de la masse oscillante, dans quel cas le mobile intermédiaire menant 2 n'est pas requis.In the example of the figure 1 , the conversion mechanism is included in an automatic winding mechanism of a watch comprising an oscillating weight. In the figure, only a ball bearing suspension 1 is shown. An intermediate mobile leading 2 is engaged with a pinion (not shown) secured to the suspension 1. The intermediate moving mobile 2 is also engaged with the board 31 of the first mobile 3 (or driving mobile) so that the rotational movement of the oscillating mass is transmitted to the first mobile 3 by means of the intermediate mobile driving 2. The automatic winding mechanism also comprises an intermediate mobile driven 6 engaged with the board 52 of the second mobile 5 (or driven mobile) and with a barrel ratchet 7. Alternatively, the first mobile 3 can be mounted coaxial with the pivot axis of the oscillating weight, in which case the intermediate driving mobile 2 is not required.

Dans cette configuration, l'organe de transmission 4 coopère avec le second mobile 5 par le biais de l'organe d'embrayage 51 de façon intermittente, de manière à entraîner le second mobile 5 selon un mouvement rotatif unidirectionnel. En particulier, la masse oscillante entraîne, par le biais du mobile intermédiaire menant 2, le premier mobile 3 en rotation dans les deux sens selon la rotation de la masse oscillante.In this configuration, the transmission member 4 cooperates with the second mobile 5 by means of the clutch member 51 intermittently, so as to drive the second mobile 5 in a unidirectional rotary movement. In particular, the oscillating mass drives, by means of the intermediate mobile 2, the first mobile 3 rotating in both directions according to the rotation of the oscillating mass.

De la sorte, la masse oscillante pivotant librement dans les deux sens entraîne le rochet de barillet 7, par le biais du second mobile 5 et du mobile intermédiaire mené 6, dans un seul sens afin d'armer le ressort de barillet (non représenté).In this way, the oscillating mass pivoting freely in both directions drives the barrel ratchet 7, by means of the second mobile 5 and the driven intermediate mobile 6, in one direction in order to arm the barrel spring (not shown) .

Selon une forme d'exécution, l'organe de transmission 4 comprend deux leviers 42 s'étendant depuis organe de guidage 32 et est terminé par un organe de blocage 40. Lorsque l'organe de transmission 4 est entraîné par le premier mobile 3, l'organe de blocage 40 de chacun des leviers 42 coopère alternativement avec l'organe d'embrayage 51 lorsque l'organe de transmission 4 coopère avec le second mobile 5.According to one embodiment, the transmission member 4 comprises two levers 42 extending from the guide member 32 and is terminated by a blocking member 40. When the transmission member 4 is driven by the first mobile 3, the locking member 40 of each of the levers 42 cooperates alternately with the clutch member 51 when the transmission member 4 cooperates with the second mobile 5.

Dans un mode de réalisation, l'organe de blocage 40 comprend un élément mobile 44 coopérant par coincement, blocage ou friction avec l'organe d'embrayage 51 lorsque l'organe de transmission 4 coopère avec le second mobile 5.In one embodiment, the blocking member 40 comprises a movable element 44 cooperating by wedging, blocking or friction with the clutch member 51 when the transmission member 4 cooperates with the second movable 5.

La figure 2 montre une vue isolée de l'organe de transmission 4 et l'organe d'embrayage 51.The figure 2 shows an isolated view of the transmission member 4 and the clutch member 51.

Selon une forme d'exécution, l'organe d'embrayage 51 comporte une bague de roulement 53 pourvue d'un chemin de roulement 54. L'organe de blocage 40 prend la forme d'une portion d'un roulement à bille comportant deux logements 45, chaque logement étant configuré comme une portion de cage. L'élément mobile comprend une bille 44 maintenue dans le logement 45. Le logement 45 possède un plan incliné 401 de sorte que, lorsque l'organe de blocage 40 coopère avec le chemin de roulement 54, la bille 44 se coince entre le chemin de roulement 54 et le plan incliné 401 du logement 45. Le plan incliné 401 peut être rectiligne ou curviligne. L'organe de blocage 40 peut ainsi entraîner le second mobile 5. Dans les figures 1 et 2, un des organes de blocage 40 est représenté "fermé", c'est-à-dire avec une cage de support 43 enfermant les logements 45 et les billes 44. L'autre organe de blocage 40 est montré "ouvert", c'est-à-dire sans la cage de support 43 permettant de voit les logements 45 et les billes 44.According to one embodiment, the clutch member 51 comprises a bearing ring 53 provided with a raceway 54. The locking member 40 takes the form of a portion of a ball bearing comprising two housings 45, each housing being configured as a cage portion. The movable element comprises a ball 44 held in the housing 45. The housing 45 has an inclined plane 401 so that, when the locking member 40 cooperates with the raceway 54, the ball 44 gets caught between the raceway bearing 54 and the inclined plane 401 of the housing 45. The inclined plane 401 can be straight or curvilinear. The blocking member 40 can thus drive the second mobile 5. In the figures 1 and 2 , one of the locking members 40 is shown "closed", that is to say with a support cage 43 enclosing the housings 45 and the balls 44. The other locking member 40 is shown "open", it that is to say without the support cage 43 making it possible to see the housings 45 and the balls 44.

On admettra d'autres arrangements de l'organe de blocage 40 dans le cadre de l'invention. Par exemple, l'organe de blocage 40 peut comprendre un nombre différent de logements 45 et de billes 44. L'élément mobile 44 peut également comprendre des rouleaux ou tout autre élément approprié au lieu de billes. On notera également qu'une seule bille 44 ou un seul cylindre de friction (ou rouleau) par organe de blocage 40 peut suffire si l'élément mobile 44 est complété par un rochet à friction (par exemple monté sur un bâti de montre) qui retient le second mobile 5 dans le sens de dégrènement.Other arrangements of the locking member 40 will be accepted within the scope of the invention. For example, the locking member 40 may include a different number of housings 45 and balls 44. The movable element 44 may also include rollers or any other suitable element instead of balls. It will also be noted that a single ball 44 or a single friction cylinder (or roller) per locking member 40 may suffice if the movable element 44 is completed by a friction ratchet (for example mounted on a watch frame) which retains the second mobile 5 in the declining direction.

L'organe de transmission 4 et l'organe de guidage 32 sont configurés de sorte que l'organe de blocage 40 de chacun des leviers 42 coopère avec l'organe d'embrayage 51 de manière intermittente et alternée entraînant le second mobile 5 dans un seul sens et évitant une rotation du second mobile 5 dans le sens contraire.The transmission member 4 and the guide member 32 are configured so that the locking member 40 of each of the levers 42 cooperates with the clutch member 51 intermittently and alternately driving the second mobile 5 in a one direction and avoiding rotation of the second mobile 5 in the opposite direction.

La planche 52 de second mobile 5 peut être en prise avec un pignon (non représenté) coaxial avec la bague de roulement 53 (tel qu'illustré à la figure 1) ou être montée pivotante sur le même axe 55 que celui de la bague de roulement 53.The second movable plate 52 can be engaged with a pinion (not shown) coaxial with the bearing ring 53 (as illustrated in the figure 1 ) or be pivotally mounted on the same axis 55 as that of the bearing ring 53.

Selon mode d'exécution, l'organe de guidage 32 comprend un élément d'articulation 321 solidaire de la planche 31 de premier mobile 3 et excentré par rapport l'axe de rotation 33. L'élément d'articulation 321 permet de guider une bascule 41 sur laquelle sont fixés les leviers 42. Par exemple, l'élément d'articulation peut comprendre un pivot 322 (comprenant une portée) solidaire au premier mobile 3 et excentré par rapport à l'axe de rotation 33 du premier mobile. La bascule 41 peut comprendre un alésage 46 s'engageant librement autour du pivot 322. Dans cette configuration, chacun des leviers fonctionnent de façon semblable à une bielle articulée à partir du pivot 322.According to embodiment, the guide member 32 comprises an articulation element 321 integral with the board 31 of the first mobile 3 and eccentric with respect to the axis of rotation 33. The articulation element 321 makes it possible to guide a rocker 41 on which the levers 42 are fixed. For example, the articulation element may comprise a pivot 322 (comprising a bearing surface) integral with the first mobile 3 and eccentric with respect to the axis of rotation 33 of the first mobile. The lever 41 may include a bore 46 freely engaging around the pivot 322. In this configuration, each of the levers operate in a similar manner to a connecting rod articulated from the pivot 322.

Un palier 47 peut être inséré entre le pivot 322 et l'alésage circulaire 46 de manière à diminuer les frottements entre la bascule 41 et le pivot 322.A bearing 47 can be inserted between the pivot 322 and the circular bore 46 so as to reduce the friction between the rocker 41 and the pivot 322.

Dans une variante, les leviers 42 comprennent une portion flexible 409 (voir figure 2) pouvant jouer un rôle de pivot virtuel reliant la bascule 41 à l'organe d'embrayage 40.In a variant, the levers 42 comprise a flexible portion 409 (see figure 2 ) can play a virtual pivot role connecting the rocker 41 to the clutch member 40.

Selon une variante non représentée, l'organe de guidage 32 comprend une came montée concentrique avec l'axe 33 et dont le rayon est variable par rapport à l'axe 33. La bascule 41 peut être guidée par la came. Par came à rayon variable, on entend une came quelconque de n'importe quelle géométrie, comme par exemple un excentrique, un cœur à spirale d'Archimède, une came de Reuleux, un polygone, etc.According to a variant not shown, the guide member 32 comprises a cam mounted concentric with the axis 33 and the radius of which is variable relative to the axis 33. The lever 41 can be guided by the cam. By variable radius cam is meant any cam of any geometry, such as an eccentric, an Archimedean spiral heart, a Reuleux cam, a polygon, etc.

La figure 3 illustre le mécanisme de conversion selon une variante, dans laquelle l'organe de transmission 4 comprend un seul levier 42 s'étendant depuis la bascule 41 et est terminé par l'organe de blocage 40. Lorsque l'organe de transmission 4 est entraîné par le premier mobile 3, l'unique organe de blocage 40 coopère de façon intermittente avec l'organe d'embrayage 51 et entraîne le second mobile 5. Un élément fixe de blocage 60 permet d'éviter que le second mobile 5 pivote dans le sens opposé à celui dans lequel il est entraîné par l'organe de transmission 4 lorsque l'organe de blocage 40 n'est pas en coopération avec l'organe d'embrayage 51. Dans l'exemple de la figure 3, l'élément fixe de blocage 60 comporte deux logements 45, chacun comprenant une bille 45, comme illustré dans les figures 1 et 2. L'élément fixe de blocage 60 peut être fixé à un bâti de la montre ou peut être monté sur une seconde bascule qui est fixe pendant que la première bascule est mobile.The figure 3 illustrates the conversion mechanism according to a variant, in which the transmission member 4 comprises a single lever 42 extending from the rocker 41 and is terminated by the locking member 40. When the transmission member 4 is driven by the first mobile 3, the single locking member 40 cooperates intermittently with the clutch member 51 and drives the second mobile 5. A fixed locking element 60 makes it possible to prevent the second mobile 5 from pivoting in the opposite direction to that in which it is driven by the transmission member 4 when the locking member 40 is not in cooperation with the clutch member 51. In the example of the figure 3 , the fixed blocking element 60 comprises two housings 45, each comprising a ball 45, as illustrated in the figures 1 and 2 . The fixed blocking element 60 can be fixed to a frame of the watch or can be mounted on a second rocker which is fixed while the first rocker is mobile.

La figure 4 montre le mécanisme de conversion encore selon un autre mode de réalisation. La figure 5 montre une vue en perspective et la figure 6 montre une vue du dessus de l'organe de transmission 4 et du second mobile 5 selon la configuration de la figure 4. L'organe de transmission 4 comprend deux bascules 41 comportant chacune un levier 42. Les deux bascules 41 sont montées coaxiales sur un élément d'articulation 321 (pivot) commun excentré par rapport à l'axe 33 de rotation du premier mobile 3. L'élément d'articulation 321 guide les deux bascules et leur levier 42 respectif selon un mouvement semblable à celui d'une bielle de sorte que l'organe de blocage 40 de chacun des leviers 42 coopère alternativement avec l'organe d'embrayage 51 lorsque l'organe de transmission 4 est entraîné par le premier mobile 3. Les deux bascules peuvent être rendues solidaires l'une de l'autre, par exemple à l'aide des doigts entraineurs 34.The figure 4 shows the conversion mechanism again according to another embodiment. The figure 5 shows a perspective view and the figure 6 shows a top view of the transmission member 4 and the second mobile 5 according to the configuration of the figure 4 . The transmission member 4 comprises two rockers 41 each comprising a lever 42. The two rockers 41 are mounted coaxially on a common articulation element 321 (pivot) eccentric relative to the axis 33 of rotation of the first mobile 3. L hinge element 321 guides the two rockers and their respective lever 42 in a movement similar to that of a connecting rod so that the locking member 40 of each of the levers 42 cooperates alternately with the clutch member 51 when the transmission member 4 is driven by the first mobile 3. The two rockers can be made integral with one another, for example using the driving fingers 34.

Dans la configuration des figures 4 et 5, l'organe de blocage 40 comprend une bascule 403 elle-même montée pivotante sur un pivot 402 à l'extrémité de chaque levier 42 et sur l'axe 55 de la bague de roulement 53. Dans cette configuration, le mouvement des leviers 42 entrainés par le premier mobile 3 fait pivoter l'organe de blocage 40 de sorte à ce que chacun des deux organes de blocage 40 coopère alternativement et entraîne le second mobile 5.In the configuration of Figures 4 and 5 , the locking member 40 comprises a rocker 403 itself pivotally mounted on a pivot 402 at the end of each lever 42 and on the axis 55 of the rolling ring 53. In this configuration, the movement of the levers 42 driven by the first mobile 3 rotates the locking member 40 so that each of the two locking members 40 cooperates alternately and drives the second mobile 5.

La figure 7 illustre une variante du mécanisme de conversion des figures 4 et 5 comprenant une seule bascule 41 comportant un levier 42. Le mécanisme de conversion comporte également un élément fixe de blocage 60 configuré comme dans l'exemple de la figure 3.The figure 7 illustrates a variant of the mechanism for converting Figures 4 and 5 comprising a single lever 41 comprising a lever 42. The conversion mechanism also comprises a fixed blocking element 60 configured as in the example of the figure 3 .

Les figures 8 à 10 montrent le fonctionnement du mécanisme de conversion selon la configuration des figures 4 à 6. En particulier, la figure 8 montre le mécanisme de conversion dans une position initiale. La figure 9 montre le mécanisme de conversion lorsque l'élément d'articulation 321, guidé par l'axe 33, est pivoté à 90° dans le sens antihoraire par rapport à la position initiale. Dans ce cas, les leviers 42 pivotent une bascule 403 dans le sens antihoraire forçant les billes 44 à se loger dans la partie étroite du logement 45 et se coincer entre le plan incliné du logement 401, de sorte que l'organe de blocage 40 coopère avec l'organe d'embrayage 51 par arc-boutement et l'entraînant selon un mouvement rotatif antihoraire. L'autre bascule 403' pivote dans le sens horaire de sorte que les billes 44 se trouvent dans la partie large du logement 45 et peuvent librement rouler dans le logement 45. Dans les figures 8 à 10, le sens de rotation des organes entraînants (l'axe 33 et les organes de blocage 40) est indiqué par les flèches pleines et le sens de rotation des organes entraînés (l'élément d'articulation 321 et l'organe d'embrayage 51) est indiqué par les flèches en pointillés.The figures 8 to 10 show the operation of the conversion mechanism according to the configuration of figures 4 to 6 . In particular, the figure 8 shows the conversion mechanism in an initial position. The figure 9 shows the conversion mechanism when the articulation element 321, guided by the axis 33, is pivoted 90 ° counterclockwise from the initial position. In this case, the levers 42 pivot a rocker 403 counterclockwise forcing the balls 44 to be housed in the narrow part of the housing 45 and to be wedged between the inclined plane of the housing 401, so that the locking member 40 cooperates with the clutch member 51 by bracing and driving it in a counterclockwise rotary movement. The other lever 403 ′ pivots clockwise so that the balls 44 are located in the wide part of the housing 45 and can freely roll in the housing 45. In the figures 8 to 10 , the direction of rotation of the driving members (the axis 33 and the locking members 40) is indicated by the solid arrows and the direction of rotation of the driven members (the articulation element 321 and the clutch member 51 ) is indicated by the dotted arrows.

La figure 10 montre le mécanisme de conversion lorsque l'élément d'articulation 321 est pivoté à 270° dans le sens antihoraire par rapport à la position initiale. Dans cette configuration, la bascule 403 pivote dans le sens horaire et les billes 44 roulent librement dans la partie large du logement 45. La bascule 403' pivote dans le sens antihoraire forçant les billes 44 à se loger dans la partie étroite du logement 45 de sorte que l'organe de blocage 40 entraîne l'organe d'embrayage 51 selon un mouvement rotatif antihoraire.The figure 10 shows the conversion mechanism when the hinge member 321 is rotated 270 ° counterclockwise from the initial position. In this configuration, the lever 403 pivots clockwise and the balls 44 roll freely in the wide part of the housing 45. The lever 403 'pivots counterclockwise forcing the balls 44 to be housed in the narrow part of the housing 45 so that the locking member 40 drives the clutch member 51 in a counterclockwise rotary movement.

La figure 11 représente le mécanisme de conversion selon un autre mode de réalisation et la figure 12 montre une vue en perspective et la figure 13 montre une vue du dessus de l'organe de transmission 4 et du second mobile 5 selon la configuration de la figure 11. L'organe de transmission 4 comprend une bascule 41 comportant deux leviers 42. La bascule 41 est guidée par un pivot 32 solidaire au premier mobile 3 et excentré par rapport à l'axe de rotation 33 du premier mobile 3, comme dans la configuration de la figure 1.The figure 11 represents the conversion mechanism according to another embodiment and the figure 12 shows a perspective view and the figure 13 shows a top view of the transmission member 4 and the second mobile 5 depending on the configuration of the figure 11 . The transmission member 4 comprises a rocker 41 comprising two levers 42. The rocker 41 is guided by a pivot 32 secured to the first mobile 3 and eccentric with respect to the axis of rotation 33 of the first mobile 3, as in the configuration of the figure 1 .

L'organe de blocage 40 comprend deux roulements à billes unidirectionnels 43, 43', chacun des roulements étant guidé en pivotement sur un pivot 402 à l'extrémité d'un levier 42. Chacun des roulements 43, 43' comprend une bague extérieure coaxiale avec une bague intérieure et une cage. La cage comportant des logements possédant un plan incliné (les bagues, la cage et les logements ne sont pas visible sur les figures 11 à 13). L'accouplement entre les bagues extérieure et intérieure du roulement est réalisé dans un seul sens de rotation du roulement, lorsque les billes se bloquent par coincement entre la bague extérieure et les parois des logements. Dans le cas où le second mobile 5 est solidaire du second mobile 5, par exemple par l'intermédiaire de l'axe 55 de second mobile, le second mobile 5 sera entraîné en rotation par l'un des deux roulements 43, 43' tournant dans un sens (par exemple dans le sens antihoraire, tel qu'indiqué par les flèches dans les figures 11 à 13) et sera en roulement libre avec l'autre roulements 43, 43' tournant dans le sens inverse.The locking member 40 comprises two unidirectional ball bearings 43, 43 ', each of the bearings being pivotally guided on a pivot 402 at the end of a lever 42. Each of the bearings 43, 43' comprises a coaxial outer ring with an inner ring and a cage. The cage with housings having an inclined plane (the rings, the cage and the housings are not visible on the figures 11 to 13 ). The coupling between the outer and inner rings of the bearing is carried out in a single direction of rotation of the bearing, when the balls are blocked by wedging between the outer ring and the walls of the housings. In the case where the second mobile 5 is integral with the second mobile 5, for example via the axis 55 of the second mobile, the second mobile 5 will be driven in rotation by one of the two bearings 43, 43 ′ rotating in one direction (for example counterclockwise, as indicated by the arrows in the figures 11 to 13 ) and will be in free rolling with the other bearings 43, 43 'rotating in the opposite direction.

La figure 14 représente le mécanisme de conversion selon un autre mode de réalisation dans lequel l'organe d'embrayage 51 comprend un disque 57 pivotant concentriquement avec l'axe 55 d'un pignon 52' de second mobile 5, le pignon 52' étant destiné à engrener avec la planche 52 de second mobile 5. L'organe de transmission 4 comprend deux bascules 41, chacune comportant un levier 42. Les deux bascules 41 sont montées chacune sur un pivot 322 excentré par rapport à l'axe 33 de rotation du premier mobile (pas représenté sur la figure 14). Chacun des leviers 42 est terminé par un support d'élément de blocage 404 comportant un élément de blocage (excentriques de blocage) 406 ayant un rayon variable. L'excentrique de blocage est guidé par une cheville 407. La configuration de l'organe de transmission 4 est telle que les supports d'élément de blocage 404 sont arrangés de chaque côté du disque 57. Lors de l'entraînement de l'organe de transmission 4 par le premier mobile 3, les excentriques de blocage 406 viennent en contact avec la tranche 57' du disque 57 alternativement avec la tranche 57' du disque 57 de sorte que, selon le sens d'entraînement des leviers 42, chacun des excentriques de blocage 406 pivote et se coince contre le disque 57 par arc-boutement. Le second mobile 5 est ainsi entraîné dans une seule direction. Les cames 33 des bascules sont idéalement excentrées entre elles, avec un déphasage entre leurs centres respectifs par rapport au centre du pivot 322 allant de 0° à 180°.The figure 14 represents the conversion mechanism according to another embodiment in which the clutch member 51 comprises a disc 57 pivoting concentrically with the axis 55 of a pinion 52 'of second mobile 5, the pinion 52' being intended to mesh with the plate 52 of the second mobile 5. The transmission member 4 comprises two rockers 41, each comprising a lever 42. The two rockers 41 are each mounted on a pivot 322 eccentric with respect to the axis 33 of rotation of the first mobile (not shown on the figure 14 ). Each of the levers 42 is terminated by a blocking element support 404 comprising a blocking element (blocking eccentrics) 406 having a variable radius. The locking eccentric is guided by a pin 407. The configuration of the transmission member 4 is such that the locking element supports 404 are arranged on each side of the disc 57. When the drive of the transmission member 4 by the first mobile 3, the locking eccentrics 406 come into contact with the edge 57 'of the disc 57 alternately with the edge 57' of the disc 57 so that, depending on the direction of driving the levers 42, each of the locking eccentrics 406 pivots and jams against the disc 57 by bracing. The second mobile 5 is thus driven in one direction. The cams 33 of the rockers are ideally offset between them, with a phase shift between their respective centers relative to the center of the pivot 322 ranging from 0 ° to 180 °.

Dans la configuration illustrée à la figure 14, chaque levier 42 possède un coude 405 flexible, autrement dit un pivot virtuel, permettant de guider les support d'élément de blocage 404 de sorte à maintenir les excentriques de blocage 406 en contact avec la tranche 57' du disque 57 quand l'organe de blocage 40 coopère avec le second mobile 5. L'excentrique de blocage 406 peut être maintenu en contact contre la tranche 57' lorsque l'organe de blocage 40 coopère avec l'organe d'embrayage 51 à l'aide d'un ressort de rappel 408, intégré à l'excentrique de blocage 406 dans cette configuration.In the configuration illustrated in figure 14 , each lever 42 has a flexible bend 405, in other words a virtual pivot, making it possible to guide the blocking element supports 404 so as to keep the blocking eccentrics 406 in contact with the edge 57 ′ of the disc 57 when the member blocking 40 cooperates with the second mobile 5. The locking eccentric 406 can be kept in contact against the edge 57 'when the locking member 40 cooperates with the clutch member 51 using a spring 408, integrated with the locking eccentric 406 in this configuration.

La figure 15 illustre le mécanisme de conversion de la figure 11, selon une autre variante dans laquelle l'excentrique de blocage 406 est séparé du ressort de rappel 408. L'excentrique de blocage comprend une came 406 montée pivotante sur un pivot 407 .The figure 15 illustrates the conversion mechanism of the figure 11 , according to another variant in which the locking eccentric 406 is separated from the return spring 408. The locking eccentric comprises a cam 406 pivotally mounted on a pivot 407.

La figure 16 montre une variante du mécanisme de conversion de la figure 15, dans laquelle l'organe de transmission 4 comprend une seule bascule 41 et un seul levier 42 comportant un excentrique de blocage 406 avec son ressort de rappel 408. Un élément fixe de blocage 60 permet d'éviter que le second mobile 5 ne pivote dans le sens opposé à celui dans lequel il est entraîné par l'organe de transmission 4 lorsque l'organe de blocage 40 n'est pas en coopération avec l'organe d'embrayage 51. Dans la configuration de la figure 16, l'élément fixe de blocage 60 comporte une came 606 pivotant autour d'un pivot 607 et maintenue en contact avec la tranche 57' du disque 57 à l'aide d'un ressort de rappel 608. La came 606 peut être montée sur un bâti d'un mouvement horloger.The figure 16 shows a variant of the conversion mechanism of the figure 15 , in which the transmission member 4 comprises a single lever 41 and a single lever 42 comprising a locking eccentric 406 with its return spring 408. A fixed locking element 60 makes it possible to prevent the second mobile 5 from pivoting in the opposite direction to that in which it is driven by the transmission member 4 when the locking member 40 is not in cooperation with the clutch member 51. In the configuration of the figure 16 , the fixed blocking element 60 comprises a cam 606 pivoting around a pivot 607 and kept in contact with the edge 57 ′ of the disc 57 using a return spring 608. The cam 606 can be mounted on a frame of a watch movement.

La figure 17 montre une variante du mécanisme de conversion dans laquelle ce dernier est réalisé avec un nombre réduit de pièces, notamment par la combinaison des fonctions guidage excentrique d'entrée, transmission du mouvement par un bras, fonction pivot de ce bras par élément flexible et arc-boutement contre le disque de réception dans une seule et même pièce. L'ensemble proposé pourrait toutefois comme dans certaines versions précédentes être réalisé sur deux niveaux pour séparer deux bras de bielle. L'arc-boutement est toujours réalisé sur un élément mobile en rotation autour d'un pivot virtuel, ce pivot étant de préférence un pivot fixe par rapport à un référentiel du bras le supportant. Afin d'assurer le guidage précis des deux coinceurs autour du disque d'embrayage, ceux-ci peuvent-être guidées par un bras mobile en rotation autour de l'axe du mobile de sortie.The figure 17 shows a variant of the conversion mechanism in which the latter is produced with a reduced number of parts, in particular by the combination of the functions of eccentric input guidance, movement transmission by an arm, pivot function of this arm by flexible element and arc pushing against the receiving disc in a single piece. The proposed assembly could however, as in certain previous versions, be carried out on two levels to separate two connecting rod arms. The bracing is always carried out on a movable element in rotation around a virtual pivot, this pivot preferably being a fixed pivot relative to a reference frame of the arm supporting it. In order to ensure the precise guidance of the two jammers around the clutch disc, they can be guided by an arm movable in rotation around the axis of the output mobile.

En particulier, dans la figure 17, l'organe de transmission 4 comprend deux leviers 42, chacun s'étendant depuis une bascule 41 montée pivotante sur l'organe de guidage 32, et terminée par un organe de blocage 40. L'organe d'embrayage 51 comprend un disque 57 (seulement une moitié du disque est représentée dans la figure 17) pivotant concentriquement avec l'axe 55 d'un pignon 52' de second mobile 5. Chacun des organes de blocage 40 comprend un élément flexible 410 apte à venir en appui contre la tranche 57' du disque 57 en relation d'arc-boutement. L'élément flexible 410 est formé d'une seule pièce avec le levier 42 et la bascule 41. L'arc-boutement est obtenu par le fait que chacun des leviers 42 est monté pivotants sur un élément mobile 501 en rotation autour de l'axe 55 commun du pignon 52' et du disque 57, par l'intermédiaire d'un pivot 402.In particular, in the figure 17 , the transmission member 4 comprises two levers 42, each extending from a rocker 41 pivotally mounted on the guide member 32, and terminated by a locking member 40. The clutch member 51 comprises a disc 57 (only half of the disc is represented in the figure 17 ) pivoting concentrically with the axis 55 of a pinion 52 'of the second mobile 5. Each of the locking members 40 comprises a flexible element 410 capable of coming into abutment against the edge 57' of the disc 57 in bracing relationship. . The flexible element 410 is formed in one piece with the lever 42 and the rocker 41. The bracing is obtained by the fact that each of the levers 42 is pivotally mounted on a movable element 501 in rotation around the common axis 55 of the pinion 52 'and the disc 57, by means of a pivot 402.

L'excentricité de l'organe de transmission 4 est définie par la distance entre l'axe de rotation 33 du premier mobile 3 et le centre 35 de l'organe de guidage 32 (voir par exemple la figure 8). Dans un mode de réalisation représenté schématiquement aux figures 18a à 18d, l'organe de guidage 32 comprend un second élément excentrique 36 pouvant se déplacer par rapport à l'organe de guidage 32. Dans l'exemple illustré, le second élément excentrique 36 peut être orienté en rotation autour du centre 37 de l'ouverture de l'organe de guidage 32. En particulier, la figure 18a montre le second élément excentrique 36 disposé de manière à maximiser l'excentricité, c'est-à-dire une distance maximale entre l'axe de rotation 33 (A) du premier mobile 3 et le centre 35 (B) de l'organe de guidage 32. Dans la figure 18c, cette distance A-B est nulle et la distance maximale entre l'axe de rotation 33 du premier mobile 3 et le centre 35 de l'organe de guidage 32 est nulle. Dans la figure 18b, le pivotement du second élément excentrique 36 résulte dans une excentricité (distance A-B) intermédiaire. La frontière entre le second élément excentrique 36 et l'organe de guidage 32 peut être continue comme illustré dans les figures 18a à 18c, permettant un réglage continu du degré d'excentricité. La frontière entre le second élément excentrique 36 et l'organe de guidage 32 peut également avoir une interface non continue, par exemple cannelée ou facettée, comme l'illustre la figure 18d, permettant un réglage du degré d'excentricité par pas, ou encore avoir toute autre forme appropriée.The eccentricity of the transmission member 4 is defined by the distance between the axis of rotation 33 of the first mobile 3 and the center 35 of the guide member 32 (see for example the figure 8 ). In an embodiment shown diagrammatically in figures 18a to 18d , the organ of guide 32 comprises a second eccentric element 36 which can move relative to the guide member 32. In the example illustrated, the second eccentric element 36 can be oriented in rotation around the center 37 of the opening of the guidance 32. In particular, the figure 18a shows the second eccentric element 36 arranged so as to maximize the eccentricity, that is to say a maximum distance between the axis of rotation 33 (A) of the first mobile 3 and the center 35 (B) of the member guide 32. In the figure 18c , this distance AB is zero and the maximum distance between the axis of rotation 33 of the first mobile 3 and the center 35 of the guide member 32 is zero. In the figure 18b , the pivoting of the second eccentric element 36 results in an intermediate eccentricity (distance AB). The border between the second eccentric element 36 and the guide member 32 can be continuous as illustrated in the figures 18a to 18c , allowing continuous adjustment of the degree of eccentricity. The border between the second eccentric element 36 and the guide member 32 can also have a non-continuous interface, for example fluted or faceted, as illustrated in FIG. figure 18d , allowing adjustment of the degree of eccentricity in steps, or even having any other suitable form.

La variation du degré d'excentricité de l'organe de transmission 4 permet de faire varier les paramètres vitesse/couple de transmission du mécanisme de conversion. Dans le cas où le mécanisme de conversion de l'invention est utilisé dans un mécanisme de remontage automatique d'une montre, la variation du degré d'excentricité de l'organe de transmission 4 permet d'adapter le mécanisme de conversion de l'invention à des calibres de montres ayant des caractéristiques différentes (vitesse de remontage, couple du ressort de barillet, etc.). Il permet également d'adapter le mécanisme de conversion à des conditions extrêmes de remontage de la montre, par exemple dans le cas d'un porter trop dynamique ou, au contraire, trop statique, donc aux conditions de remontage définies par leur porteur. Il permet également d'adapter le mécanisme de conversion aux paramètres de remontage à toute autre situation propre à en requérir l'application.The variation in the degree of eccentricity of the transmission member 4 makes it possible to vary the transmission speed / torque parameters of the conversion mechanism. In the case where the conversion mechanism of the invention is used in an automatic winding mechanism of a watch, the variation in the degree of eccentricity of the transmission member 4 makes it possible to adapt the conversion mechanism of the invention of watch calibers having different characteristics (winding speed, barrel spring torque, etc.). It also makes it possible to adapt the conversion mechanism to extreme conditions of winding the watch, for example in the case of wearing that is too dynamic or, on the contrary, too static, therefore to the winding conditions defined by their wearer. It also makes it possible to adapt the conversion mechanism to the winding parameters to any other situation likely to require its application.

L'homme du métier saura toutefois recourir à tout autre moyen connu pour permettre de procéder à ce réglage (déplacement linéaire le long de l'axe A-B par micro-vis ou tout autre moyen alternatif, etc.)Those skilled in the art will however be able to use any other known means to allow this adjustment to be made (linear displacement along the axis A-B by micro-screw or any other alternative means, etc.)

Dans un mode de réalisation représenté aux figures 19 et 20, l'organe d'embrayage 51 est arrangé de manière à pivoter de façon légèrement excentrée par rapport à l'axe de rotation 55 du second mobile 5. La figure 19 montre un exemple où l'organe de blocage 40 prend la forme d'une portion d'un roulement à billes, où la bille 44 est coincée entre la bague de roulement 53 et la pente de la cage 45, cette pente pouvant être linéaire ou curviligne. La figure 20 montre un exemple où l'organe de blocage 40 comprend un excentrique de blocage 406.In an embodiment shown in Figures 19 and 20 , the clutch member 51 is arranged so as to pivot slightly eccentrically relative to the axis of rotation 55 of the second mobile 5. The figure 19 shows an example where the locking member 40 takes the form of a portion of a ball bearing, where the ball 44 is wedged between the bearing ring 53 and the slope of the cage 45, this slope can be linear or curvilinear. The figure 20 shows an example where the blocking member 40 comprises a blocking eccentric 406.

L'excentricité est illustrée par le tracé en pointillés sur les figures. L'excentricité a pour effet que le blocage / friction de l'élément mobile 44 (excentrique de blocage 406, etc.) se répartit sur une plus grande portion de la surface de l'élément de cage 45. L'occurrence de contacts répétés de blocage / friction aux mêmes endroits de la surface peuvent être ainsi réduite significativement par rapport à une configuration où l'organe d'embrayage 53, 57 pivote de façon concentrique par rapport à l'axe de rotation 55. Les effets de matage ou d'usure dus aux pressions sur l'élément de cage 45 sont minimisés. Un tel arrangement peut être réalisé sans pour autant perturber les paramètres de remontage de manière sensible (dans le cas où le mécanisme de conversion est utilisé dans un mécanisme de remontage automatique d'une montre). Une autre manière de répartir les contraintes et l'usure sur des portions différentes de l'excentrique de blocage 406 ou de l'élément de cage 45, consiste à recourir à un disque d'embrayage 53 concentrique à son centre de rotation 55, en donnant audit disque d'embrayage 53 une forme légèrement ovalisée, par exemple de type ellipsoïdale, ou tout autre géométrie faisant varier légèrement la distance définie entre le point de contact avec l'élément de blocage 406, 44 et le centre de rotation 55.The eccentricity is illustrated by the dotted line in the figures. The eccentricity causes the blocking / friction of the movable element 44 (blocking eccentric 406, etc.) to be distributed over a larger portion of the surface of the cage element 45. The occurrence of repeated contacts locking / friction at the same locations on the surface can thus be reduced significantly compared to a configuration where the clutch member 53, 57 pivots concentrically with respect to the axis of rotation 55. The effects of dulling or d wear due to pressures on the cage element 45 are minimized. Such an arrangement can be achieved without significantly disturbing the winding parameters (in the case where the conversion mechanism is used in an automatic watch winding mechanism). Another way of distributing the stresses and wear on different portions of the locking eccentric 406 or of the cage element 45, consists in using a clutch disc 53 concentric with its center of rotation 55, in giving said clutch disc 53 a slightly oval shape, for example of the ellipsoidal type, or any other geometry varying slightly the distance defined between the point of contact with the locking element 406, 44 and the center of rotation 55.

Si le mécanisme de conversion a été illustré principalement dans le contexte d'une utilisation dans un mécanisme de remontage automatique d'une montre, le mécanisme de conversion peut également être également être utilisé dans tout autre dispositif de transmission qui requiert la conversion d'un mouvement bidirectionnel en un mouvement unidirectionnel.If the conversion mechanism has been illustrated mainly in the context of use in a winding mechanism automatic of a watch, the conversion mechanism can also be used in any other transmission device which requires the conversion of a bidirectional movement into a unidirectional movement.

Numéros de référence employés sur les figuresReference numbers used in the figures

11
pignon-suspension d'une masse oscillantepinion-suspension of an oscillating mass
22
mobile intermédiaire menantintermediate mobile leading
33
premier mobile, mobile menantfirst mobile, leading mobile
3131
planche de premier mobilefirst mobile board
3232
organe de guidageguide member
321321
élément d'articulationhinge element
322322
pivotpivot
3333
axe de rotation du premier mobileaxis of rotation of the first mobile
3434
doigt entraineurcoach finger
3535
centre du mobile excentriquecenter of the eccentric mobile
3636
second élément excentriquesecond eccentric element
3737
centre du second élément excentriquecenter of the second eccentric element
44
organe de transmissiontransmission organ
4040
élément de blocageblocking element
4141
basculetoggle
4242
articulation, brasjoint, arm
43, 43'43, 43 '
cage de support, roulement à billesupport cage, ball bearing
4444
élément mobile, billemoving element, ball
4545
logementhousing
4646
alésagebore
4747
palierbearing
401401
plan incliné du logementhousing incline
402402
pivotpivot
403,403'403.403 '
basculetoggle
404404
support d'élément de blocageblocking element holder
405405
coudeelbow
406406
excentrique de blocageeccentric blocking
407407
chevilleankle
408408
ressort de rappelspring
409409
portion flexibleflexible portion
410410
élément flexibleflexible element
55
second mobile, mobile menésecond mobile, mobile driven
5151
organe d'embrayageclutch member
5252
planche de second mobilesecond mobile board
52'52 '
pignon de second mobilesecond mobile gear
5353
bague de roulementbearing ring
5454
chemin de roulementRaceway
5555
axe de second mobilesecond mobile axis
5757
disquedisk
57'57 '
tranche du disquedisc slice
501501
élément mobilemoving element
66
mobile intermédiaire menémobile intermediate led
6060
élément fixe de blocagefixed blocking element
606606
camecam
607607
axeaxis
608608
ressort d'embrayageclutch spring
77
rochet de barilletbarrel ratchet

Claims (25)

  1. Conversion mechanism intended for a watchmaking application, comprising:
    a first mobile (3) driven according to a given rotary motion, a second mobile (5), and a transmission member (4) cooperating with the first mobile and the second mobile (3, 5);
    characterized in that
    the first mobile (3) comprises a plate (31) pivoting around an axis (33) and a guiding device (32), the latter being configured to drive the transmission member (4) eccentrically around the axis (33);
    and in that
    the second mobile (5) comprises a coupling device (51); the transmission member (4) cooperating with the coupling device (51) by intermittent buttressing to drive the second mobile (5) in a rotary unidirectional motion.
  2. Conversion mechanism according to claim 1,
    wherein the transmission member (4) comprises at least one lever (42) extending from the guiding device (32) and terminating by a locking member (40), this latter cooperating with a surface (54, 57') of the coupling device (51) intermittently when the transmission member (4) is engaged.
  3. Conversion mechanism according to any one of the previous claims,
    comprising moreover a locking member (60) mounted on the frame preventing the rotation of the second mobile (5) in the other direction when the locking member (40) is not cooperating with the second mobile (5).
  4. Conversion mechanism according to claim 2,
    wherein the transmission member (4) comprises two levers (42), each of the levers (42) comprising the locking member (40) so that the locking member (40) of each of the levers (42) cooperates alternately with the coupling device (51).
  5. Conversion mechanism according to one of the claims 2 to 4,
    wherein the locking member (40) comprises a mobile element (44) cooperating by buttressing between the coupling device (51) and a housing (45) of the locking member.
  6. Conversion mechanism according to claim 5,
    wherein the mobile element comprises at least one ball or a roller (44) held in a housing (45) comprising an inclined plane (401) so that, when the locking member (40) cooperates with the coupling device (51), said at least one ball or said at least one roller (44) becomes wedged between the coupling device (51) and the inclined plane (401) of the housing (45).
  7. Conversion mechanism according to one of the claims 5 or 6,
    wherein the coupling device (51) comprises a rolling ring or disc (53) fitted with a ball bearing rail (54) configured to cooperate with the mobile element (44).
  8. Conversion mechanism according to the previous claim,
    wherein the locking member (40) is mounted on a pivoting lever (403) movably mounted by a pivot (402) in relation to the pivoting lever (42) and pivotably mounted on an axis of rotation (55) of the rolling ring (53).
  9. Conversion mechanism according to claim 4,
    wherein the locking member (40) comprises at least one locking eccentric (406) cooperating by buttressing with the coupling device (51).
  10. Conversion mechanism according to claim 9,
    wherein the coupling device (51) comprises a disc (57) pivoting around the axis (55) of the second mobile (5) and cooperating with the locking eccentric (406) of the locking member (40).
  11. Conversion mechanism according to any one of the previous claims,
    wherein the guiding device (32) comprises an articulation element (321) attached to the first mobile (3) and eccentric to the rotation axis (33) of the first mobile (3); the articulation element (321) guiding a pivoting lever (41) guiding the said at least one lever (42).
  12. Conversion mechanism according to any one of the previous claims,
    wherein the guiding device (32) comprises a pivot (322) intended to cooperate in rotation with a bore (46) in the pivoting lever (41).
  13. Conversion mechanism according to claim 12,
    wherein a bearing (47) is inserted between the pivot (322) and the bore (46) in the pivoting lever (41).
  14. Conversion mechanism according to any one of the previous claims,
    wherein the guiding device (32) comprises a cam mounted concentrically to the axis (33) and whose radius varies according to said axis so that the pivoting lever (41) is guided by the cam in a non-concentric motion in relation to the axis (33).
  15. Conversion mechanism according to any one of the claims 1 à 13,
    wherein the guiding device (32) comprises means for adjusting (36) the eccentricity between the axis (33) of rotation of the first mobile (3) and the axis of rotation of the guiding device (32).
  16. Conversion mechanism according to the previous claim,
    wherein the means for adjusting the eccentricity comprise a second eccentric element (36) able to be positioned in relation to the guiding device (32).
  17. Conversion mechanism according to the previous claim,
    wherein the second eccentric element (36) is substantially circular and can be pivoted around a centre (35) of the guiding device (32).
  18. Conversion mechanism according to any one of the claims 2 to 17,
    wherein the lever (42) can be rigid, flexible or constituted of several parts articulated to one other.
  19. Conversion mechanism according to the previous claim,
    wherein the lever (42) comprises a flexible portion (405, 409) being able to play a role of virtual pivot linking the pivoting lever (41) to the coupling device (40).
  20. Conversion mechanism according to any one of the previous claims,
    wherein the coupling device (51) is arranged to pivot eccentrically in relation to the rotation axis of the second mobile (5).
  21. Conversion mechanism according to any one of the previous claims;
    wherein the first mobile (3), the plate (31) and the guiding device (32) are constituted of a single piece.
  22. Watch movement comprising the conversion mechanism according to any one of the previous claims.
  23. Automatic winding mechanism of a timepiece comprising the conversion mechanism according to any one of the claims 1 to 21.
  24. Automatic winding mechanism, according to claim 23
    wherein the first mobile (3) is fixed to an oscillating weight (1) or is driven by the oscillating weight (1) by means of at least one wheel (2).
  25. Watch comprising the automatic winding mechanism according to any one of the claims 23 or 24.
EP17151430.0A 2016-02-04 2017-01-13 Timepiece conversion mechanism of a rotary motion with any amplitude and direction into a one-way motion Active EP3203326B1 (en)

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EP4016192A1 (en) 2020-12-16 2022-06-22 Manufacture d'Horlogerie Audemars Piguet SA Transmission mechanism for a timepiece movement

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EP3926411A1 (en) * 2020-06-16 2021-12-22 Damasko Präzisionstechnik GmbH & Co. KG Automatic winding mechanism with decentralized roller bearing

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Publication number Priority date Publication date Assignee Title
EP4016192A1 (en) 2020-12-16 2022-06-22 Manufacture d'Horlogerie Audemars Piguet SA Transmission mechanism for a timepiece movement

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