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EP4325303B1 - Mechanismus eines immerwährenden kalenders mit konzentrischen nocken - Google Patents

Mechanismus eines immerwährenden kalenders mit konzentrischen nocken Download PDF

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Publication number
EP4325303B1
EP4325303B1 EP22190621.7A EP22190621A EP4325303B1 EP 4325303 B1 EP4325303 B1 EP 4325303B1 EP 22190621 A EP22190621 A EP 22190621A EP 4325303 B1 EP4325303 B1 EP 4325303B1
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EP
European Patent Office
Prior art keywords
cam
month
wheel
year
finger
Prior art date
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Active
Application number
EP22190621.7A
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English (en)
French (fr)
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EP4325303A1 (de
Inventor
Xavier Guillaume
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Manufacture dHorlogerie Audemars Piguet SA
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Manufacture dHorlogerie Audemars Piguet SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by Manufacture dHorlogerie Audemars Piguet SA filed Critical Manufacture dHorlogerie Audemars Piguet SA
Priority to EP22190621.7A priority Critical patent/EP4325303B1/de
Priority to PCT/IB2023/057952 priority patent/WO2024038348A1/fr
Publication of EP4325303A1 publication Critical patent/EP4325303A1/de
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Publication of EP4325303B1 publication Critical patent/EP4325303B1/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
    • G04B19/00—Indicating the time by visual means
    • G04B19/24—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars
    • G04B19/243—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars characterised by the shape of the date indicator
    • G04B19/247—Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars characterised by the shape of the date indicator disc-shaped
    • G04B19/253—Driving or releasing mechanisms
    • G04B19/25333—Driving or releasing mechanisms wherein the date indicators are driven or released mechanically by a clockwork movement
    • G04B19/25353—Driving or releasing mechanisms wherein the date indicators are driven or released mechanically by a clockwork movement driven or released stepwise by the clockwork movement
    • G04B19/2536—Driving or releasing mechanisms wherein the date indicators are driven or released mechanically by a clockwork movement driven or released stepwise by the clockwork movement automatically corrected at the end of months having less than 31 days

Definitions

  • the present invention relates to a perpetual calendar mechanism, for a watch movement, comprising a month cam and a year cam nested in the month cam in a concentric manner.
  • the invention also relates to a timepiece, in particular a wristwatch, comprising a watch movement equipped with the perpetual calendar mechanism with concentric cams.
  • Perpetual calendar mechanisms therefore most often have a complex and bulky construction, which can have a significant impact on the size of the watch case incorporating a watch movement equipped with such a mechanism.
  • EP3026504 discloses a perpetual calendar mechanism based on a 48 cam comprising 48 notches which are each associated with a month over a period of four years consecutive. This mechanism also includes a rocker with a feeler tail intended to cooperate with these 48 notches.
  • EP3734373 discloses another example of a perpetual calendar mechanism.
  • This comprises a month cam having an eccentric circular cutout in which a year cam is arranged.
  • a large lever is arranged to come into contact with the profile of one or the other of the month cam and the year cam depending on the respective angular position of each cam.
  • the year cam being eccentric with respect to the month cam, the perpetual calendar mechanism comprises a drive system capable not only of actuating the year cam in rotation about its axis at a rate of one revolution every four years but also of driving the year cam together with the month cam around the center thereof at a rate of one revolution per year.
  • This mechanism includes a drive system which therefore has the disadvantage of being relatively complex in order to print two distinct movements to the year cam.
  • An aim of the present invention is therefore to provide a perpetual calendar mechanism at least free from the above limitations.
  • an aim of the present invention is to provide a compact perpetual calendar mechanism.
  • Another object of the present invention is to provide a perpetual calendar mechanism of simpler, more robust and therefore more reliable construction.
  • An additional aim of the present invention is to propose a perpetual calendar mechanism comprising a system for driving the month and year cams which is simplified compared to the aforementioned mechanisms.
  • a perpetual calendar mechanism for a watch movement comprising a concentric cam assembly.
  • This assembly comprises a month cam arranged to be driven at a rate of one revolution per year, and a year cam arranged to be driven at a rate of one revolution every four years.
  • the month cam comprises a central housing in which the year cam is positioned.
  • the mechanism further comprises a lever comprising a feeler arranged to cooperate with the concentric cam assembly, as well as a star.
  • This star is arranged to be actuated daily directly or indirectly by the lever and to be further actuated on the last day of months with less than 31 days, depending on the angular position of the month cam and the year cam in order to catch up until reaching a state corresponding to the first date of the following month.
  • the month cam has a radial opening so that the rocker feeler can cooperate with either the month cam or the year cam depending on the angular position of the month cam.
  • the thickness of one of the month cam and the year cam is at least half the thickness of the other of the month cam and the year cam.
  • At least 3/5, preferably at least 4/5 of the thickness of one of the month cam and the years is at the thickness level of the other of the months cam and the years cam.
  • the upper face of the month cam is substantially coplanar with the upper face of the year cam.
  • the lower face of the month cam is substantially coplanar with the lower face of the year cam.
  • the central housing of the month cam comprises a cylindrical wall arranged against at least a portion of the profile of the year cam so that the year cam can guide the month cam in rotation.
  • the year cam is secured to a large wheel meshing with at least one wheel arranged to be driven once a month by the star.
  • the month cam is arranged to be driven by a gear train comprising a first wheel secured to the month cam and mounted coaxially therewith, a second wheel meshing with the first wheel and a return secured to the second wheel and meshing with the teeth of the large wheel.
  • the feeler of the scale is arranged between the first wheel and the large wheel.
  • the first wheel and the month cam together form a single piece.
  • the large wheel and the year cam together form a single piece.
  • the profile of the year cam comprises three radial notches corresponding to the sectors of the month of February of the non-leap years of the cam.
  • the mechanism further comprises a 24-hour wheel arranged to be driven at a rate of one revolution in 24 hours and a 24-hour finger secured to the 24-hour wheel.
  • the lever itself comprises a first beak arranged to cooperate with a 24-hour finger and a second beak arranged to rotate the 31 star, typically secured to the day of the month indications.
  • the mechanism further comprises a wheel and a finger secured to the wheel.
  • the lever comprises a rack engaged with the wheel in order to engage the finger with the 31 star each time the lever is actuated by the 24H finger.
  • the 31 star can be actuated in rotation by one step per day.
  • aspects of the invention relate on the one hand to a watch movement equipped with the concentric cam date mechanism according to the invention, and on the other hand to a timepiece, in particular a wristwatch, comprising a watch movement equipped with the concentric cam date mechanism according to the invention.
  • the perpetual calendar mechanism 10 comprises a concentric cam assembly 20 and a lever 50 arranged to cooperate with the concentric cam assembly 20 and to actuate a 31 - 70 star depending on the information given by the concentric cam assembly 20.
  • This assembly 20 comprises a month cam 22, commonly called a 12 cam, and a 30s cam which are mounted coaxially.
  • the cam of the months 22 comprises for this purpose a central housing 28 defined by a cylindrical wall 28a and a radial opening 27 extending from the edge of the cam profile and opening into the central housing 28 as illustrated in particular by the Figures 5 and 6 .
  • the 30s cam is arranged inside the central housing 28 of the month cam.
  • this central housing 28 consists of a through opening formed in the month cam 22. More preferably, this opening is essentially circular in shape and would allow the passage of the 30s cam through the month cam 22.
  • the month cam comprises four sectors 25a corresponding to the 30-day months of the year, and seven sectors 25b corresponding to the 31-day months of the year, of which two pairs of sectors, corresponding to the pairs of months July-August and December-January, are each formed of contiguous sectors 25b.
  • Sectors 25a and 25b, as well as the radial opening 27 representing the month of February, are successively arranged so as to represent, in chronological order, the different months of the year.
  • the radial opening 27 is bordered by two sectors 25b corresponding to the months of January and March.
  • the sectors 25a and 25b are typically circular sectors whose distal edges define arcs of circles with the same center.
  • the radial opening 27 allows the rocker 50 to take the information on the year cam in order to carry out a catch-up on the star 70 at the end of the month of February depending on whether it is a non-leap year or a leap year.
  • the profile of the 1930s cam comprises three radial notches 34a spaced apart from each other by 90°. These three notches make it possible to correct the display of the date at the end of February of a non-leap year.
  • the profile of the 1930s cam further comprises a sector 34b extending between two radial notches 34a which are substantially diametrically opposed. The sector 34b makes it possible to correct the display of the date at the end of February of a leap year.
  • the upper and lower faces of the 22-month and 30-year cams are planar and perpendicular to the common axis of rotation of these cams.
  • the upper face 23a of the month cam 22 is substantially coplanar with the upper face 32a of the 30s cam, i.e. the offset between the respective upper faces of the two cams does not exceed 20%, preferably 10%, of the thickness of one of the cams.
  • the respective lower faces 23b, 32b of the month cam 22 and the 30s cam is preferably fully nested in the month cam 22 with the constant diameter cam profile lying against the cylindrical wall 28a of the central housing 28 so that the month cam can thus be guided in rotation by the year cam.
  • the thickness of the month cam may, however, be significantly different from the thickness of the year cam according to variants of execution not illustrated.
  • the thickness of the month cam 22 may be much less than the thickness of the 30s cam and represent, for example, half the thickness of the year cam.
  • the reverse is also possible, i.e. the thickness of the 30s cam may be much less than the thickness of the month cam 22 and represent, for example, half the thickness of the latter.
  • the cylindrical wall 28a defining the central housing 28 of the month cam 22 is arranged against the constant diameter cam profile of the 30s cam.
  • this arrangement is established with just sufficient clearance so that one of the cams 22, 30 does not drive the other by friction.
  • the years cam can thus be rotated at a rate of one revolution every four years while guiding the rotation of the month cam 22 around its profile at a rate of one revolution per year.
  • the month cam 22 and the 30s cam therefore remain separate and rotate at different speeds.
  • the cam from the 30s is attached to a large 36 wheel.
  • This is typically engaged with a gear train preferably comprising a first and a second wheel 37, 38 as illustrated in figure 1 .
  • the first wheel 37 is arranged to be driven once a month by the passage of a drive finger 76 secured to the star 70.
  • the latter is secured to a display (not shown) comprising the numbers from 1 to 31 in order to scroll them successively for example through a window of a dial.
  • the gear train 37, 38 makes it possible to drive the large wheel 36 by one complete revolution every four years in order to drive the cam of the 30s so that it also makes one complete revolution every four years.
  • the large wheel 36 and the 1930s cam are made in one piece but could just as well be made separately and fixed against each other.
  • the month cam 22 is arranged to be driven by a gear train comprising a first wheel 42 secured to the month cam 22 and mounted coaxially therewith, a second wheel 44 meshing with the first wheel 42 and a return 46 secured to the second wheel 44 and meshing with the teeth of the large wheel 36.
  • the month cam 22 and the first wheel 42 are made in one piece but could just as well be made separately and fixed against each other.
  • the second wheel 44 has twelve teeth and cooperates with a jumper 47 in order to drive the month cam 22 by the second wheel 44 in rotation at a rate of a jump of 30° (one twelfth of a turn) every month, the jumper 47 allowing the jump to be completed.
  • the perpetual calendar mechanism 10 further comprises a 24H wheel 80 arranged to be driven at a rate of one turn per day.
  • a 24H finger 82 is fixed on the 24H wheel 80 to actuate the lever 50 which in turn actuates in rotation the wheel 62 engaged with a rack 58 secured to the lever 50 in order to actuate in rotation the star 70 by means of the finger 66 secured of wheel 62 so that star 70 makes a jump every day.
  • a catch-up at the end of the month is carried out according to the angular position of the cam of months 22 and the cam of years 30.
  • the rocker 50 comprises for this purpose a feeler 52 arranged to cooperate with the profile of one or the other of the month cam and the year cam according to the respective angular position of each cam.
  • the feeler 52 is arranged to bear against the profile of one of the aforementioned cams. Being located at different radial distances from the common center of rotation of the cams 22 and 30, these different profiles make it possible to vary the amplitude of the movement of the rocker 50, when the latter is actuated by the 24H finger 82.
  • the feeler 52 is arranged between the first wheel 42 and the large wheel 36 as illustrated in figure 3 .
  • the radial opening 27 of the month cam 22 is positioned opposite the feeler 52 so that the feeler can be introduced into this opening to come into contact with the profile of the 30s cam so as to be able to make the necessary correction at the end of February, taking into account leap years.
  • the lever 50 further comprises a first beak 54 positioned on the trajectory of the 24H finger 82 as well as a second beak 56 arranged to actuate the star 70 by means of a catch finger 72 secured to the star 70, which cooperates with a jumper 74 as shown in FIG. figure 1 .
  • the take-up finger 72 is mounted on a spring blade 73 arranged to flex under the action of the second beak 56 of the rocker against the take-up finger 72 so that the rocker 50 is not blocked by this finger when the feeler 52 falls back against the concentric cam assembly 20.
  • a rocking spring 60 for example in the form of a spiral, is fixed to the wheel 62 in order to constrain the latter into the angular position illustrated in figure 1 .
  • This arrangement comprising in particular the rake 58, the wheel 62 and the rocker spring 60, makes it possible to constrain the feeler 52 of the rocker 50 against the profile of one or the other of the month cam 22 and the year cam 30 when the rocker is at rest.
  • a finger 66 is secured to the wheel 62 in order to be able to actuate the star 70 by one jump each day, namely by one step. It will be noted that the figure 1 illustrates the state of the mechanism on the 28th day of February in a non-leap year.
  • the catch-up finger 72 being integral with the star 70, it therefore performs a rotation every month. This finger is clear of the trajectory of the second beak 56 of the lever 50 throughout the month so that the latter actuates the star 70 each day only by means of the finger 66, thus ensuring the transition from an indication of one day to an indication of the following day. At the end of each month of less than 31 days, the catch-up finger 72 comes to position itself on the trajectory of the second beak 56 of the lever 50 as illustrated in particular in figure 1 .
  • THE figures 1 And 8a to 8d represent an operational sequence at the end of February of a non-leap year.
  • the figure 1 illustrates the state of the mechanism on the 28th day of February in a non-leap year.
  • the lateral edges of a portion of the feeler 52 are against the edges of the radial opening 27 of the month cam.
  • the distal portion of the feeler 52 is inside one of the notches 34a of the 30s cam ( figure 7 ).
  • FIG. 8a illustrates the mechanism when the 24H finger 82 comes into contact with the first beak 54 of the lever 50 and exerts a thrust on the latter in order to disengage the feeler 52 from the radial notch 34a of the years cam.
  • the second beak 56 of the lever 50 in turn exerts a thrust on the catch finger 72 of the star of 31, which initiates the rotation of the latter.
  • the movement of the second beak 56 illustrated between the representations of the Figures 8a And 8b allows the star 70 to be actuated in rotation, by means of the catch-up finger 72, so that it makes three successive jumps.
  • the amplitude of the movement of the rocker 50 is consequently maximum during this period.
  • the rake of the latter actuates the wheel 62 in rotation, which progressively pivots the finger 66 until the latter actuates the star 70 by one step as shown in Figures 8c And 8d .
  • the second beak 56 of the scale 50 activates the star 70 so that it makes three successive jumps
  • finger 66 activates the star so that it makes an additional jump.
  • the catch-up finger 72 is cleared from the path of the beak 56 of the lever 50 throughout the month so that the latter actuates the star 70 each day only via the finger 66, thus ensuring the transition from an indication of one day to an indication of the following day.
  • the contact of the feeler 52 of the lever against the sector 25b of the month cam makes it possible to position the lever 50 so that the second beak 56 is cleared from the path of the catch-up finger 72, in particular at the end of the month when it passes during the period March 30-31. No correction is thus made for this month.
  • FIG. 9a And 9b illustrate an operational sequence at the end of February of a leap year.
  • the Figure 9a represents the mechanism on the 29th day.
  • the feeler 52 of the rocker 50 is arranged at this instant against a sector 34b of the profile of the cam of the years.
  • the 24H finger 82 exerts a thrust on the first beak 54 of the lever 50, driving the latter until the second beak 56 in turn exerts a thrust on the catch-up finger 72 of the star 70 ( figure 9b ) so that it makes two successive jumps.
  • finger 66 actuates star 70 according to the description above, which makes an additional jump in order to make the transition from the indication of 29 to the indication of March 1.
  • FIGS. 10a to 10d represent an operational sequence at the end of April.
  • the figure 10a represents the mechanism on the 30th day of the month of April.
  • the feeler 52 of the lever 50 is arranged at this moment against a sector 25a of the profile of the month cam.
  • the 24H finger 82 exerts a thrust on the first beak 54 of the lever 50 according to the figure 10b then the second beak 56 of the latter drives the star 70 by means of the catch-up finger 72 according to the figure 10c so that the star performs a jump followed by an additional jump under the action of the finger 66 which is pivoted thanks to the action of the rake of the rocker on the wheel 62.
  • the lever 50 could be shaped to directly actuate the star of 31 each day so that it can in particular make a single jump independently of the amplitude of movement of the lever, which would make it possible, for example, to do without the finger 66.
  • the lever could be replaced by a large conventional lever comprising a large pawl cooperating with a cam of 31 secured to the star of 31 in place of the catch-up finger.

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  • General Physics & Mathematics (AREA)
  • Electromechanical Clocks (AREA)

Claims (15)

  1. Ewiger Kalendermechanismus (10) für ein Uhrwerk, umfassend :
    eine Anordnung aus konzentrischen Nocken (20) aufweisend eine Monatsnocke (22), die eine zentrale Aufnahme (28) umfasst und so angeordnet ist, dass er mit einer Umdrehung pro Jahr angetrieben wird, und eine Jahresnocke (30), die in der zentralen Aufnahme (28) der Monatsnocke (22) positioniert ist und so angeordnet ist, dass sie alle vier Jahre mit einer Umdrehung angetrieben wird,
    eine Wippe (50) mit einem Taster (52), der so angeordnet ist, dass er mit der konzentrischen Nockenanordnung (20) zusammenwirkt, und
    einen Stern (70), der so angeordnet ist, dass er täglich direkt oder indirekt durch die Wippe (50) betätigt wird und des Weiteren am letzten Tag von Monaten mit weniger als 31 Tagen in Abhängigkeit von der Winkelposition der Monatsnocken (22) und der Jahresnocken (30) betätigt wird, um eine Nachholung zu bewirken,
    wobei die Monatsnocke (22) eine radiale Öffnung (27) aufweist, so dass der Fühler (52) der Wippe (50) in Abhängigkeit von der Winkelposition der Monatsnocke (22) mit entweder der Monatsnocke (22) oder der Jahresnocke (30) zusammenwirken kann.
  2. Mechanismus (10) nach Anspruch 1, wobei die Dicke von entweder der Monatsnocke (22) oder der Jahresnocke (30) mindestens die Hälfte der Dicke der jeweils anderen Monatsnocke (22) oder der Jahresnocke (30) beträgt.
  3. Mechanismus (10) nach einem der vorhergehenden Ansprüche, wobei mindestens 3/5, vorzugsweise mindestens 4/5 der Dicke entweder der Monatsnocke (22) oder der Jahresnocken (30) auf der Höhe der Dicke der jeweils anderen Monatsnocke (22) oder Jahresnocken (30) liegt.
  4. Mechanismus (10) nach einem der vorhergehenden Ansprüche, wobei die obere Fläche (23a) der Monatsnocke (22) im Wesentlichen koplanar mit der oberen Fläche (32a) der Jahresnocke (30) ist.
  5. Mechanismus (10) nach einem der vorhergehenden Ansprüche, wobei die Unterseite (23b) der Monatsnocke (22) im Wesentlichen koplanar mit der Unterseite (32b) der Jahresnocke (30) ist.
  6. Mechanismus (10) nach einem der vorhergehenden Ansprüche, wobei das zentrale Gehäuse (28) der Monatsnocke (22) eine zylindrische Wand (28a) aufweist, die gegen mindestens einen Teil des Profils der Jahresnocken (30) angeordnet ist, so dass die Jahresnocke die Monatsnocke drehbar führen kann.
  7. Mechanismus (10) nach einem der vorhergehenden Ansprüche, bei dem die Jahresnocke (30) fest mit einem großen Rad (36) verbunden ist, das mit mindestens einem Rad (37, 38) in Eingriff steht, das so angeordnet ist, dass es einmal pro Monat von dem Stern (70) angetrieben wird, und bei dem die Monatsnocke (30) so angeordnet ist, dass sie von einem Getriebe angetrieben wird, das ein erstes Rad (42), das mit der Monatsnocke (12) fest verbunden und koaxial zu dieser montiert ist, ein zweites Rad (44), das mit dem ersten Rad (42) kämmt, und ein Umlenkgetriebe (46) umfasst, das mit dem zweiten Rad (44) fest verbunden ist und mit der Verzahnung des großen Rades (36) in Eingriff steht.
  8. Mechanismus (10) nach dem vorhergehenden Anspruch, bei dem der Taster (52) der Wippe (50) zwischen dem ersten Rad (42) und dem großen Rad (36) angeordnet ist.
  9. Mechanismus nach Anspruch 7 oder 8, bei dem das erste Rad (42) und die Monatsnocke (22) zusammen ein einziges Teil bilden.
  10. Mechanismus nach einem der Ansprüche 7 bis 9, bei dem das große Rad (36) und die Jahresnocke (30) zusammen ein einziges Teil bilden.
  11. Mechanismus (10) nach einem der vorhergehenden Ansprüche, bei dem das Profil der Jahresnocke (30) drei radiale Kerben (34a) aufweist, die den Sektoren der Nicht-Schaltjahre der Nocke entsprechen.
  12. Mechanismus (10) nach einem der vorhergehenden Ansprüche, des Weiteren umfassend ein 24 Stunden-Rad (80), das so angeordnet ist, dass es mit einer Umdrehung in 24 Stunden angetrieben wird, und einen 24 Stunden-Finger (82), der fest mit dem 24 Stunden-Rad (80) verbunden ist, wobei die Wippe (50) eine erste Nase (54), die so beschaffen ist, dass sie mit dem 24 Stunden-Finger (82) zusammenwirkt, und eine zweite Nase (56), die so beschaffen ist, dass sie den Stern (70) über einen Nachstellfinger (72), der fest mit dem Stern verbunden ist, in Drehung versetzt, umfasst.
  13. Mechanismus (10) nach dem vorhergehenden Anspruch, des Weiteren umfassend ein nachlaufendes Rad (62) und einen mit dem nachlaufenden Rad (62) fest verbundenen Finger (66), wobei die Wippe (50) einen Rechen (58) umfasst, der mit dem nachlaufenden Rad (62) in Eingriff steht, um den Finger (66) jedes Mal, wenn die Wippe durch den 24 Stunden-Finger (80) betätigt wird, mit dem Stern (70) in Eingriff zu bringen.
  14. Uhrwerk mit dem Mechanismus nach einem der vorhergehenden Ansprüche.
  15. Uhr, insbesondere eine Armbanduhr, mit dem Uhrwerk nach dem vorhergehenden Anspruch.
EP22190621.7A 2022-08-16 2022-08-16 Mechanismus eines immerwährenden kalenders mit konzentrischen nocken Active EP4325303B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP22190621.7A EP4325303B1 (de) 2022-08-16 2022-08-16 Mechanismus eines immerwährenden kalenders mit konzentrischen nocken
PCT/IB2023/057952 WO2024038348A1 (fr) 2022-08-16 2023-08-07 Mécanisme de quantième perpétuel à cames concentriques

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP22190621.7A EP4325303B1 (de) 2022-08-16 2022-08-16 Mechanismus eines immerwährenden kalenders mit konzentrischen nocken

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EP4325303A1 EP4325303A1 (de) 2024-02-21
EP4325303B1 true EP4325303B1 (de) 2024-12-25

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Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR536251A (fr) * 1921-05-20 1922-04-29 Système de quantième perpétuel applicable aux montres, pendules et horloges
EP3026504B1 (de) 2014-11-27 2017-09-27 Société anonyme de la Manufacture d'Horlogerie Audemars Piguet & Cie Uhrmechanismus eines Jahres- oder ewigen Kalenders, und Uhr, die eine solche Anwendung umfasst
EP3734373B1 (de) 2019-05-02 2023-05-10 Patek Philippe SA Genève Betätigungsvorrichtung eines datumsterns eines halbewigen oder ewigen kalendermechanismus

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EP4325303A1 (de) 2024-02-21

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