EP3203326B1 - Konvertierungsmechanismus für einer rotationsbewegung in jeder drehrichtung in einer bewegung mit einer einzelen bewegung richtung. - Google Patents

Konvertierungsmechanismus für einer rotationsbewegung in jeder drehrichtung in einer bewegung mit einer einzelen bewegung richtung. 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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English (en)
French (fr)
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EP3203326A1 (de
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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Classifications

    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • 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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Claims (25)

  1. Umwandlungsmechanismus für eine Uhrenanwendung, der enthält:
    ein erstes Drehteil (3), das gemäß einer beliebigen Drehbewegung angetrieben werden kann, ein zweites Drehteil (5) und ein Übertragungsorgan (4), das mit dem ersten und dem zweiten Drehteil (3, 5) zusammenwirkt;
    dadurch gekennzeichnet, dass
    das erste Drehteil (3) eine um eine Achse (33) schwenkende Platte (31) und ein Führungsorgan (32) enthält, wobei letzteres konfiguriert ist, das Übertragungsorgan (4) exzentrisch bezüglich der Achse (33) anzutreiben;
    und dass
    das zweite Drehteil (5) ein Kupplungsorgan (51) aufweist; wobei das Übertragungsorgan (4) mit dem Kupplungsorgan (51) durch Verkanten intermittierend zusammenwirkt, um das zweite Drehteil (5) gemäß einer unidirektionalen Drehbewegung anzutreiben.
  2. Umwandlungsmechanismus nach Anspruch 1, wobei das Übertragungsorgan (4) mindestens einen Hebel (42) enthält, der sich vom Führungsorgan (32) erstreckt und in einem Blockierorgan (40) endet, wobei letzteres mit einer Fläche (54, 57') des Kupplungsorgans (51) intermittierend zusammenwirkt, wenn das Übertragungsorgan (4) angetrieben wird.
  3. Umwandlungsmechanismus nach einem der vorhergehenden Ansprüche, der außerdem ein auf das Gestell montiertes Blockierelement (60) enthält, das es ermöglicht, die Drehung des zweiten Drehteils (5) in die andere Richtung zu verhindern, wenn das Blockierorgan (40) nicht mit dem zweiten Drehteil (5) zusammenwirkt.
  4. Umwandlungsmechanismus nach Anspruch 2, wobei das Übertragungsorgan (4) zwei Hebel (42) enthält, wobei jeder der Hebel (42) das Blockierorgan (40) enthält, so dass das Blockierorgan (40) jedes der Hebel (42) abwechselnd mit dem Kupplungsorgan (51) zusammenwirkt.
  5. Umwandlungsmechanismus nach einem der Ansprüche 2 bis 4, wobei das Blockierorgan (40) ein bewegliches Element (44) enthält, das durch Verkanten zwischen dem Kupplungsorgan (51) und einer Aufnahme (45) des Blockierorgans mitwirkt.
  6. Umwandlungsmechanismus nach Anspruch 5, wobei das bewegliche Element mindestens eine Kugel oder eine Rolle (44) enthält, die in einer Aufnahme (45) gehalten wird, die eine geneigte Ebene (401) aufweist, so dass, wenn das Blockierorgan (40) mit dem Kupplungsorgan (51) zusammenwirkt, die mindestens eine Kugel oder Rolle (44) sich zwischen das Kupplungsorgan (51) und die geneigte Ebene (401) der Aufnahme (45) klemmt.
  7. Umwandlungsmechanismus nach einem der Ansprüche 5 oder 6, wobei das Kupplungsorgan (51) einen Laufring oder eine Laufscheibe (53) aufweist, die mit einer Laufbahn (54) versehen ist, die konfiguriert ist, mit dem beweglichen Element (44) zusammenzuwirken.
  8. Umwandlungsmechanismus nach dem vorhergehenden Anspruch, wobei das Blockierorgan (40) auf eine Wippe (403) montiert ist, die durch einen Zapfen (402) bezüglich des Hebels (42) beweglich montiert und auf eine Drehachse (55) des Laufrings (53) schwenkbar montiert ist.
  9. Umwandlungsmechanismus nach Anspruch 4, wobei das Blockierorgan (40) mindestens einen Blockierexzenter (406) enthält, der durch Verkanten mit dem Kupplungsorgan (51) zusammenwirkt.
  10. Umwandlungsmechanismus nach Anspruch 9, wobei das Kupplungsorgan (51) eine Scheibe (57) enthält, die um die Achse (55) des zweiten Drehteils (5) schwenkt und mit dem Blockierexzenter (406) des Blockierorgans (40) zusammenwirkt.
  11. Umwandlungsmechanismus nach einem der vorhergehenden Ansprüche, wobei das Führungsorgan (32) ein Gelenkelement (321) enthält, das fest mit dem ersten Drehteil (3) verbunden und bezüglich der Drehachse (33) des ersten Drehteils (3) exzentrisch ist; wobei das Gelenkelement (321) eine Wippe (41) führt, die den mindestens einen Hebel (42) führt.
  12. Umwandlungsmechanismus nach einem der vorhergehenden Ansprüche, wobei das Führungsorgan (32) einen Zapfen (322) enthält, der dazu bestimmt ist, in Drehung mit einer Bohrung (46) der Wippe (41) zusammenzuwirken.
  13. Umwandlungsmechanismus nach Anspruch 12, wobei ein Lager (47) zwischen den Zapfen (322) und die Bohrung (46) der Wippe (41) montiert ist.
  14. Umwandlungsmechanismus nach einem der vorhergehenden Ansprüche, wobei das Führungsorgan (32) eine konzentrisch mit der Achse (33) montierte Nockenscheibe enthält, deren Radius bezüglich der Achse variiert, so dass die Wippe (41) von der Nockenscheibe gemäß einer nicht zur Achse (33) konzentrischen Bewegung geführt wird.
  15. Umwandlungsmechanismus nach einem der Ansprüche 1 bis 13, wobei das Führungsorgan (32) Einstelleinrichtungen (36) der Exzentrizität zwischen der Drehachse (33) des ersten Drehteils (3) und der Drehachse des Führungsorgans (32) aufweist.
  16. Umwandlungsmechanismus nach dem vorhergehenden Anspruch, wobei die Einstelleinrichtungen der Exzentrizität ein zweites exzentrisches Element (36) enthalten, das bezüglich des Führungsorgans (32) positioniert werden kann.
  17. Umwandlungsmechanismus nach dem vorhergehenden Anspruch, wobei das zweite exzentrische Element (36) im Wesentlichen kreisförmig ist und um eine Mitte (35) des Führungsorgans (32) geschwenkt werden kann.
  18. Umwandlungsmechanismus nach einem der Ansprüche 2 bis 17, wobei der Hebel (42) starr, flexibel sein oder aus mehreren miteinander gelenkig verbundenen Teilen bestehen kann.
  19. Umwandlungsmechanismus nach dem vorhergehenden Anspruch, wobei der Hebel (42) einen flexiblen Abschnitt (405, 409) enthält, der die Aufgabe eines virtuellen Zapfens übernehmen kann, der die Wippe (41) mit dem Kupplungsorgan (40) verbindet.
  20. Umwandlungsmechanismus nach einem der vorhergehenden Ansprüche, wobei das Kupplungsorgan (51) so eingerichtet ist, dass es bezüglich der Drehachse des zweiten Drehteils (5) exzentrisch schwenkt.
  21. Umwandlungsmechanismus nach einem der vorhergehenden Ansprüche, wobei das erste Drehteil (3), die Platte (31) und das Führungsorgan (32) aus einem einzigen Bauteil bestehen.
  22. Uhrwerk, das den Umwandlungsmechanismus nach einem der vorhergehenden Ansprüche enthält.
  23. Automatischer Aufziehmechanismus einer Uhr, der den Umwandlungsmechanismus nach einem der Ansprüche 1 bis 21 enthält.
  24. Automatischer Aufziehmechanismus nach Anspruch 23, wobei das erste Drehteil (3) mit einer Schwingmasse (1) fest verbunden montiert oder von der Schwingmasse (1) mittels mindestens eines Drehteils (2) angetrieben wird.
  25. Uhr, die den automatischen Aufziehmechanismus nach einem der Ansprüche 23 oder 24 enthält.
EP17151430.0A 2016-02-04 2017-01-13 Konvertierungsmechanismus für einer rotationsbewegung in jeder drehrichtung in einer bewegung mit einer einzelen bewegung richtung. Active EP3203326B1 (de)

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EP4016192A1 (de) 2020-12-16 2022-06-22 Manufacture d'Horlogerie Audemars Piguet SA Übertragungsmechanismus für uhrwerk

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EP3926411B1 (de) * 2020-06-16 2024-10-16 Damasko Präzisionstechnik GmbH & Co. KG Automatischer aufzugsmechanismus mit dezentralem wälzlager

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CH242384A (fr) 1945-12-18 1946-05-15 Tissot Horlogerie Pièce d'horlogerie à remontage automatique et à la main.
DE882227C (de) 1950-06-07 1953-07-06 Ernest Homberger Rauschenbach Selbsttaetige Aufziehvorrichtung mit Schwungmasse fuer Remontoiruhrwerke (Armbanduhren)
US3846973A (en) 1970-12-28 1974-11-12 Suwa Seikosha Kk Automatic winding watch with bridge plate offset to receive automatic winding mechanism
JP2003130967A (ja) 1999-09-29 2003-05-08 Seiko Epson Corp 計時装置
JP2003279666A (ja) 2002-03-25 2003-10-02 Seiko Epson Corp 時 計
DE102008051197A1 (de) * 2008-10-14 2010-04-15 Konrad Damasko Mechanischer Federaufzug für die Antriebsfeder von Armbanduhren sowie Armbanduhr mit einem derartigen Aufzug
CH704893A2 (fr) * 2011-05-03 2012-11-15 Patek Philippe Sa Geneve Mécanisme de remontage automatique.
CH706144A1 (fr) * 2012-02-29 2013-08-30 Richemont Int Sa Mécanisme de remontage automatique bidirectionnel pour mouvement d'horlogerie.

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Publication number Priority date Publication date Assignee Title
EP4016192A1 (de) 2020-12-16 2022-06-22 Manufacture d'Horlogerie Audemars Piguet SA Übertragungsmechanismus für uhrwerk

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