EP3580618B1 - Antriebsorgan einer uhr - Google Patents

Antriebsorgan einer uhr Download PDF

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Publication number
EP3580618B1
EP3580618B1 EP18706317.7A EP18706317A EP3580618B1 EP 3580618 B1 EP3580618 B1 EP 3580618B1 EP 18706317 A EP18706317 A EP 18706317A EP 3580618 B1 EP3580618 B1 EP 3580618B1
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EP
European Patent Office
Prior art keywords
drive member
units
hub
rim
unit
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EP18706317.7A
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English (en)
French (fr)
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EP3580618A1 (de
Inventor
Jean-Baptiste LE BRIS
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Patek Philippe SA Geneve
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Patek Philippe SA Geneve
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Publication of EP3580618A1 publication Critical patent/EP3580618A1/de
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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
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/18—Constructions for connecting the ends of the mainsprings with the barrel or the arbor
    • 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
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/12—Driving mechanisms with mainspring with several mainsprings
    • 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
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/14—Mainsprings; Bridles therefor
    • 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
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/22—Compensation of changes in the motive power of the mainspring
    • 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
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/04—Oscillators acting by spring tension

Definitions

  • the present invention relates to a motor member for watchmaking, in particular a motor member with a substantially constant moment of force.
  • the clockwork drive unit can be either a drive unit for a watch movement arranged to drive a going train, or a drive unit for an additional mechanism such as a striking mechanism or a chronograph.
  • a barrel is traditionally used as the driving member of a watch mechanism.
  • a barrel is an assembly of at least three elements: a barrel spring consisting of a leaf spring in the form of a spiral, a barrel drum serving as a housing for said spring, said drum being able to rotate freely on a barrel arbor (axis pivoting between bridge and plate), and a barrel cover for closing the barrel drum, said cover also being able to rotate freely on the barrel arbor.
  • the leaf spring has the shape of an upturned S. The unwinding of the blade, wound against the diameter of the bung of the barrel arbor and seeking to return to its initial shape, produces the energy necessary for the operation of the watch mechanism.
  • a disadvantage of such a motor member is that its performance is affected by the friction of the coils of the spiral spring against each other and against the inside of the barrel drum, during the unwinding of the barrel. To reduce this friction, it is customary to lubricate the coils of the spring and to deposit an anti-friction coating in the drum. Despite this, such a motor member undergoes energy losses of approximately 15% due to friction.
  • Such a motor member is therefore expensive and difficult to manufacture.
  • the object of the present invention is to provide an alternative motor member to the barrel comprising a spiral spring traditionally used, and also alternative to the motor members disclosed by the documents CH699988A2 and EP2455820A2 .
  • the object of the present invention is also that of providing a motor member making it possible to overcome, at least in part, the aforementioned drawbacks.
  • the invention proposes for this purpose a clockwork motor member according to appended claim 1.
  • the present invention also proposes a timepiece mechanism comprising such a timepiece motor member.
  • the motor member according to the invention has the advantage of significantly improving the efficiency (average energy loss of between 0 and 3% only against approximately 15% for a traditional spiral spring barrel). Indeed, the monolithic units that compose it do not undergo or very little friction.
  • the motor member according to the invention also has the advantage of delivering a substantially constant moment of force, thus improving the isochronism of the watch movement with which it is associated, without requiring an intermediate spring between the motor member and the 'exhaust.
  • the figures 1 and 2 represent a part of a timepiece mechanism, more precisely of a timepiece movement, comprising a clockwork motor member 1 according to a particular embodiment of the invention, this motor member 1 being held in position by means of a axis 2 of said watch movement.
  • This watch movement further comprises, in particular, a gear train 3, an escapement 4 and a winding mechanism 5a, 5b, as illustrated in figures 1 and 2 .
  • the winding mechanism comprises a winding stem 5a and a winding wheel 5b. In a variant, it could be of the automatic type, with an oscillating mass.
  • the motor member 1 comprises several monolithic units 110, 210, 310, stacked on top of each other and connected in series, as illustrated in picture 3 .
  • Each of these units 110, 210, 310 comprises a hub 120, 220, 320 and a rim 130, 230, 330 connected by several elastic arms 140, 240, 340 uniformly distributed around its hub 120, 220, 320, as illustrated in figures 4a, 4b and 4c .
  • the first 110 of said units is associated with a toothing 160 allowing the connection with the winding wheel 5b.
  • This toothing 160 which meshes with the winding wheel 5b is typically carried by a winding wheel 170 coaxial with and integral with the hub 120 of the said first unit 110, as shown in figures 1, 2, 3 and 4a .
  • the toothing 160 can be fixed to the rim 130 of the first unit 110. That or that of the hub 120 or of the rim 130 of the first unit 110 which is fixed to the toothing 160, and therefore by which between the energy, constitutes an input element of the stack of units 110, 210, 310.
  • the last 310 of said units is associated with another toothing 360 which meshes with the going train 3 to deliver a moment of force to it.
  • This other toothing 360 is typically integral with the rim 330 of this last unit 310, as shown in figures 1, 2, 3 and 4c .
  • the toothing 360 can be integral with the hub 320 of the last unit 310. That or that of the hub 320 or the rim 330 of the last unit 310 which is integral with said other toothing 360, and therefore through which the energy exits, constitutes an output element of the stack of units 110, 210, 310.
  • the intermediate units 210 placed between said first 110 and last 310 units are not associated with a toothing, as shown in figures 1, 3 and 4b .
  • each of the units 110, 210, 310 is unidirectional, that is to say that it has, due to the shape of its elastic arms 140, 240, 340, a privileged direction of rotation. of its rim 130, 230, 330 relative to its hub 120, 220, 320, this direction being defined as that which allows, from the rest state of the unit in question, the greatest relative angular displacement of its serge 130, 230, 330 with respect to its hub 120, 220, 320.
  • the arrows A, B and C represented respectively on the figures 4a, 4b and 4c , illustrate this preferred direction of rotation of the edges 130, 230, 330 with respect to the hubs 120, 220, 320 for the units 110, 210, 310 of the motor member 1 represented.
  • all the units 110, 210, 310 are identical (in particular the arms 140, 240, 340 have the same shape) and are stacked coaxially and head to tail, two successive units having different directions of rotation. privileged opposites.
  • the motor member comprises three units 110, 210, 310, it can comprise a first unit 110 whose preferred direction of rotation is clockwise (as shown in figure 4a ), a single intermediate unit 210 whose preferred direction of rotation is counterclockwise (corresponding to a unit 210 as shown in figure 4b turned over) and a last unit 310 whose preferred direction of rotation is clockwise (as shown in figure 4c ).
  • the units 110, 210, 310 are also connected in series, these units 110, 210, 310 being two by two connected alternately by their edges 130, 230, 330 and by their hubs 120, 220, 320.
  • rim 130 of first unit 110 is integral with rim 231 of first intermediate unit 211
  • hub 221 of this first intermediate unit 211 is integral with hub 222 of second intermediate unit 212 and so on, hub of the last intermediate unit being integral with the hub 320 of the last unit 310.
  • the privileged direction of rotation of the first 110 and of the last 310 unit and the choice of the input and output elements (serge or hub) depends on the position of the driving member 1 in the watch mechanism and depends on the mechanism of crown 5a, 5b and of the going train 3.
  • the preferred direction of rotation of the intermediate units 210 is granted according to their number and according to the direction of the first 110 and last 310 units.
  • the hubs 120, 220, 320 of the units 110, 210, 310 of the motor member 1 comprise holes 150, 250, 350, for example circular, these holes 150, 250, 350 being traversed by the axis 2 of the movement watchmaker, said axis 2 preferably being mounted fixed relative to the movement, for example in the plate of the movement.
  • This axis 2 positions the motor member 1 and helps to keep the hubs 120, 220, 320 of all the units 110, 210, 310 aligned, the hubs 120, 220, 320 being free to rotate around the axis 2 .
  • the hubs 120, 220, 320 of the units 110, 210, 310 of the drive member 1 may not include holes 150, 250, 350.
  • the drive member may, in this case, be held in position , for example, by means of two axes mounted on the hubs 120, 320 respectively of the first 110 and last 310 units, these axes being, respectively, integral in rotation with said hubs 120, 320 and free in rotation with respect to a fixed part of the movement, typically in relation to the plate.
  • This driving member can also be placed in a drum.
  • the very structure of the drive member 1 involves the centering of the hub 120, 220, 320 of each unit 110, 210, 310 with respect to its rim 130, 230, 330.
  • the motor member 1 can comprise one or more hub centering devices aimed at reinforcing the centering of the hubs 120, 220, 320.
  • Such devices typically comprise a rigid junction element 6, on the one hand, fixed integrally to two diametrically opposed zones of the rim 130, 230, 330 of a unit 110, 210, 310 and on the other hand, positioned free in rotation on the axis 2.
  • the figures 5a and 5b are respectively bottom and top views of a unit 110, 210, 310 of the drive member 1 equipped with such a centering device.
  • the set of elastic arms 140, 240, 340 of each unit 110, 210, 310 of the motor member 1 is designed, in particular by its shape, to exert, in this unit 110, 210, 310, a substantially constant elastic return moment over a range of angular displacement of the rim 130, 230 330 of said unit 110, 210, 310 relative to its hub 120, 220, 320 of at least 10°, preferably d at least 15°, for example approximately 21°.
  • “Substantially constant” moment is understood to mean a moment not varying by more than 10%, preferably 5%, more preferably 3%, typically 1.5%, it being understood that this percentage can be further reduced.
  • Mmin and Mmax respectively be the values of the minimum and maximum moments exerted in a unit 110, 210, 310 of the engine member 1 over a given range of angular displacement of its rim 130, 230, 330 with respect to its hub 120, 220, 320
  • ⁇ be the angular displacement of the rim 130, 230, 330 of a unit 110, 210, 310 of the motor member 1 relative to the hub 120, 220, 320 of this same unit 110, 210, 310 in its direction of rotation privileged, ⁇ being equal to zero when said unit 110, 210, 310 is at rest, that is to say when all its elastic arms 140, 240, 340 are at rest, the figure 6 illustrates the evolution M( ⁇ ) of the elastic restoring moment exerted by the set of elastic arms 140, 240, 340 of a unit 110, 210, 310 in this unit as a function of the angular displacement ⁇ .
  • the monolithic units 110, 210, 310 exhibiting a curve M( ⁇ ) of the type of that shown in figure 6 differ from conventional elastic structures. Their properties are based on a sinuous shape of their elastic arms which deform in such a way as to generate a substantially constant elastic restoring moment (the curve M( ⁇ ) has a plateau). In addition, due to their sinuous shape, the elastic arms 140, 240, 340 of a given unit 110, 210, 310 have the advantage of being able to be relatively long without the risk of rubbing against each other during rotation. of the rim 130, 230, 330 of said unit 110, 210, 310 with respect to its hub 120, 220, 320.
  • the topological optimization discussed in the aforementioned article uses parametric polynomial curves such as Bézier curves to determine the geometric shape of the elastic arms.
  • each of the elastic arms 140, 240, 340 of the motor member 1 is a Bézier curve whose control points have been optimized to take into account, in particular, the dimensions of the unit 110, 210, 310 to be designed as well as the constraint "(M max -M min )/((M max +M min )/2) ⁇ 0.05" sought.
  • the inequality “(Mmax-Mmin)/((Mmax+Mmin)/2) ⁇ 0.05” corresponds to a constancy of the elastic restoring moment of 5% over an angular range [ ⁇ min_5% , ⁇ max_5% ].
  • the applicant has designed a particular unit of a motor member, said particular unit comprising twenty-three elastic arms distributed uniformly around the hub.
  • the dimensions of this particular unit are as follows: External diameter of the serge: 12mm Outside diameter of the hub: 2mm Inner diameter of the serge: 10mm Height: 0.15mm Thickness of the elastic arms: 60 ⁇ m
  • control points Q 0 , Q 1 , Q 2 , Q 3 , Q 4 , Q 5 , Q 6 were used.
  • the coordinates of these control points are shown in Table 1 below.
  • Table 1 Coordinates of control points Q ⁇ sub>0 ⁇ /sub> to Q ⁇ sub>6 ⁇ /sub>.
  • the Bézier curve was broken down into two segments, a first segment corresponding to a curve of Bézier of order 4 based on control points Q 0 to Q 3 and a second segment corresponding to a Bézier curve of order 4 based on control points Q 3 to Q 6 .
  • the graph of the figure 7 shows the geometry of the external diameter of the hub, of the internal diameter of the serge and of one of the elastic arms of the particular unit that the applicant has designed, the geometry of said arm being defined by a curve passing through the set of coordinates of points defined in Table 2 above. This graph is produced in an orthonormal frame.
  • the figure 8a represents the results of a simulation of the evolution of the elastic return moment of the particular unit thus produced as a function of the angular displacement of its rim relative to its hub.
  • the angular range of operation allowing the delivery of a substantially constant moment being a constant linked to the shape of the elastic arms, it is important to take into account the ratio between the elastic limit and the Young's modulus of the material to choose the material.
  • a motor member 1 comprising eleven units identical to the particular unit studied in figure 8a , stacked and connected in series, was also designed.
  • a simulation made it possible to graphically represent the moment of force delivered by the rim 330 (output element) of the last unit 310 of this motor member 1 as a function of the angular displacement of the rim 330 of the last unit 310 with respect to the hub 120 (input element) of the first unit 110.
  • the results of this simulation are presented in figure 8b (curve C2).
  • the figure 8b also represents the elastic restoring moment of a single particular unit identical to that studied in figure 8a as a function of the angular displacement of its rim relative to its hub (curve C1).
  • a drive member 1 comprising p units 110, 210, 310, p being an integer greater than or equal to two, allows the delivery of a moment of force that is substantially constant over a range of angular displacement of the output element, rim 330 or hub 320, of its last unit 310 relative to the input element, rim 130 or hub 120, of its first unit 110 of at least (p ⁇ 10) °, preferably at least (p ⁇ 15)°, for example approximately (p ⁇ 21)°.
  • the motor member 1 does not include an intermediate unit 210 but only includes a first unit 110 and a last unit 310 stacked and connected by their respective edges or by their respective hubs.
  • the timepiece mechanism incorporating the motor member 1 can comprise stops making it possible to maintain said motor member 1 in the range of angular displacement of the output element of its last unit 310 with respect to the input element of its first unit 110 allowing the delivery of a substantially constant moment of force.
  • the motor member 1 can be made of any suitable material, in particular as regards its elastic limit and its Young's modulus.
  • Units 110, 210, 310 can be manufactured separately and then assembled. They can for example be manufactured by machining, in particular in the case where they are made of metal or an alloy such as Nivaflex ® , by DRIE etching in the case of silicon for example, or even by molding, in particular in the case where they are made of plastic or metallic glass. The units 110, 210, 310 obtained can then be assembled together, typically by gluing, welding or brazing.
  • the motor member 1 can be produced in a single monolithic part, for example by using 3-dimensional printing techniques or laser cutting techniques, typically in mineral glass.
  • the units 110, 210, 310 stacked coaxially are arranged so that the elastic arms 140, 240, 340 of the units whose preferred direction of rotation is the same align, which makes it possible to obtain an advantageous aesthetic effect. , as illustrated in figures 1 and 2 .
  • the motor member 1 can comprise monolithic units of different shape from that illustrated in figures 1, 2 and 4 . They may in particular take a form as shown in figure 9 .
  • the monolithic unit 10 shown in figure 9 comprises elastic arms 40 exerting a substantially constant elastic restoring moment over a range of angular displacement of the rim 30 of said unit relative to its hub 20 of at least 10°, preferably at least 15°, for example around 21°.
  • a motor member 1 comprising a number of monolithic units different from that represented in the figures and/or comprising units with elastic arms of different shapes from those represented in the figures and/or whose the number of elastic arms is different from that shown in the figures, it being possible in particular for a monolithic unit to have only one elastic arm.
  • the value of the moment of force reached in the stable phase of the driving member can in particular be adjusted by acting on the number of elastic arms that comprise the units which constitute it, on the thickness of the elastic arms and/or on the material used. .
  • q being an integer greater than or equal to 2
  • the moment of force exerted by all of these q elastic arms in the monolithic unit in its stable phase is typically equal to q times the moment of force exerted, in a similar monolithic unit comprising only one of these elastic arms, by said single elastic arm in this unit, in its stable phase.
  • the angular range [ ⁇ min, ⁇ max ] over which the moment of force delivered is substantially constant can, for its part, be adjusted by adjusting the number of units stacked and connected in series.
  • At least one or each of the elastic arms of the units according to the invention could have a variable section, for example a variable thickness.
  • the section could typically be larger on the hub side than on the rim side.
  • the toothing 360 associated with the last unit 310 of the motor member 1 according to the invention can, as desired, be integral with the hub 320 or rim 330 of this unit 310. In particular, it can be carried directly by said rim 330 or by said hub 320.
  • the toothing 160 associated with the first unit 110 of the motor member 1 according to the invention can, as desired, be secured to the hub 120 or to the rim 130 of this unit 110. In particular, it can be carried directly by said rim 130 or by said hub 120.
  • the person skilled in the art can also easily adjust, according to his needs (that is to say for example according to the number of units that the motor member 1 comprises, according to whether the toothing 360 is integral with the hub 320 or the rim 330 of the last unit 310, depending on whether the toothing 160 is integral with the hub 120 or the rim 130 of the first unit 110, depending on the preferred direction of rotation chosen for any of the units, etc.) , the arrangement of the serge-serge and hub-hub connections of a motor member 1 according to the invention.
  • the moment of force delivered by the driving member 1 can allow the setting in motion of another type of gear train than a finishing gear train 3 or of an additional mechanism such as a striking or chronograph mechanism. .

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Metallurgy (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Gears, Cams (AREA)
  • Micromachines (AREA)
  • Measurement Of Unknown Time Intervals (AREA)
  • Transmission Devices (AREA)

Claims (14)

  1. Antriebsorgan (1) einer Uhr, das mindestens zwei monolithische Einheiten (110, 210, 310) umfasst, die gestapelt und in Reihe geschaltet sind, wobei jede dieser Einheiten eine Nabe (120, 220, 320) und einen Fußkreis (130, 230, 330) umfasst, die durch mindestens einen elastischen Arm (140, 240, 340) verbunden sind, wobei der oder jeder der elastischen Arme (140, 240, 340) von einer beliebigen der Einheiten (110, 210, 310) eine gewundene Form aufweist.
  2. Antriebsorgan (1) nach Anspruch 1, dadurch gekennzeichnet, dass es eine erste Zahnung (160), die die Verbindung zwischen den monolithischen Einheiten (110, 210, 310) und einem Aufzugmechanismus (5a, 5b) ermöglicht, und eine zweite Zahnung (360) umfasst, die die Abgabe eines Kraftmoments durch die monolithischen Einheiten (110, 210, 310) ermöglicht.
  3. Antriebsorgan (1) nach Anspruch 2, dadurch gekennzeichnet, dass die erste Zahnung (160) fest mit der Nabe (120) oder mit dem Fußkreis (130) von einer ersten (110) der monolithischen Einheiten (110, 210, 310) verbunden ist.
  4. Antriebsorgan (1) nach einem der Ansprüche 2 oder 3, dadurch gekennzeichnet, dass die zweite Zahnung (360) fest mit der Nabe (320) oder mit dem Fußkreis (330) einer letzten (310) der monolithischen Einheiten (110, 210, 310) verbunden ist.
  5. Antriebsorgan (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Form des mindestens einen elastischen Arms (140, 240, 340) für alle monolithischen Einheiten (110, 210, 310) gleich ist, und dadurch, dass die monolithischen Einheiten (110, 210, 310) unidirektional sind und paarweise entgegengesetzt platziert sind.
  6. Antriebsorgan (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass jede der monolithischen Einheiten (110, 210, 310) mehrere elastische Arme (140, 240, 340) umfasst, die gleichförmig um ihre Nabe (120, 220, 320) herum verteilt sind.
  7. Antriebsorgan (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass es mindestens eine Vorrichtung (6) zur Zentrierung der Naben (120, 220, 230) umfasst.
  8. Antriebsorgan (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der mindestens eine elastische Arm (140, 240, 340) von jeder monolithischen Einheit (110, 210, 310) so entworfen ist, dass ein elastisches Rückstellmoment ausgeübt wird, das über einen Winkelverlagerungsbereich des Fußkreises (130, 230, 330) der monolithischen Einheit (110, 210, 310) in Bezug auf seine Nabe (120, 220, 320) von mindestens 10°, vorzugsweise mindestens 15 °, um nicht mehr als 10 %, vorzugsweise 5 %, schwankt.
  9. Antriebsorgan (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass es p monolithische Einheiten (110, 210, 310) umfasst, wobei p eine ganze Zahl größer oder gleich zwei ist, und dadurch, dass die elastischen Arme (140, 240, 340) so entworfen sind, dass das Antriebsorgan (1) ein Kraftmoment abgibt, das über einen Winkelverlagerungsbereich eines Ausgangselements, Fußkreis (330) oder Nabe (320), der Stapelung der monolithischen Einheiten (110, 210, 310) in Bezug auf ein Eingangselement, Fußkreis (130) oder Nabe (120), der Stapelung von mindestens (p × 10)°, vorzugsweise mindestens (p × 15)°, um nicht mehr als 10 %, vorzugsweise 5 %, schwankt.
  10. Antriebsorgan (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die geometrische Form des oder jedes elastischen Arms (140, 240, 340) einer beliebigen der monolithischen Einheiten (110, 210, 310) eine Bézier-Kurve oder eine Folge von Bézier-Kurven ist.
  11. Uhrmechanismus, dadurch gekennzeichnet, dass er ein Antriebsorgan (1) nach einem der Ansprüche 1 bis 10 umfasst.
  12. Uhrmechanismus nach Anspruch 11, dadurch gekennzeichnet, dass er eine Achse (2) umfasst, die die Naben (120, 220, 320) der monolithischen Einheiten (110, 210, 310) durchquert.
  13. Uhrmechanismus nach Anspruch 11 oder 12, dadurch gekennzeichnet, dass er Anschläge umfasst, die es ermöglichen, das Antriebsorgan (1) in einem Winkelverlagerungsbereich eines Ausgangselements, Fußkreis (330) oder Nabe (320), der Stapelung monolithischer Einheiten (110, 210, 310) in Bezug auf ein Eingangselement, Fußkreis (130) oder Nabe (120), der Stapelung zu halten, wodurch die Abgabe eines im Wesentlichen konstanten Kraftmoments ermöglicht wird.
  14. Uhrmechanismus nach einem der Ansprüche 11 bis 13, dadurch gekennzeichnet, dass er einen Aufzugmechanismus (5a, 5b) umfasst, der so gestaltet ist, dass das Antriebsorgan (1) und ein Räderwerk (3) aufgezogen werden, das so gestaltet ist, dass es durch das Antriebsorgan (1) angetrieben wird.
EP18706317.7A 2017-02-13 2018-02-12 Antriebsorgan einer uhr Active EP3580618B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP17155883 2017-02-13
PCT/IB2018/050834 WO2018146639A1 (fr) 2017-02-13 2018-02-12 Organe moteur d'horlogerie

Publications (2)

Publication Number Publication Date
EP3580618A1 EP3580618A1 (de) 2019-12-18
EP3580618B1 true EP3580618B1 (de) 2022-01-26

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EP18706317.7A Active EP3580618B1 (de) 2017-02-13 2018-02-12 Antriebsorgan einer uhr

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US (1) US11543775B2 (de)
EP (1) EP3580618B1 (de)
JP (1) JP7100650B2 (de)
WO (1) WO2018146639A1 (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3882714A1 (de) 2020-03-19 2021-09-22 Patek Philippe SA Genève Verfahren zur herstellung einer uhrenkomponente aus silizium
EP4248278A1 (de) 2020-11-17 2023-09-27 Patek Philippe SA Genève Uhrelement, das mindestens ein federblatt umfasst
EP4248277A1 (de) 2020-11-17 2023-09-27 Patek Philippe SA Genève Verfahren zur herstellung eines federblattes eines uhrenelements und besagtes federblatt

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JP2020509358A (ja) 2020-03-26
WO2018146639A1 (fr) 2018-08-16
US20200004202A1 (en) 2020-01-02
EP3580618A1 (de) 2019-12-18
US11543775B2 (en) 2023-01-03
JP7100650B2 (ja) 2022-07-13

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