EP3588201B1 - Jahreskalendermechanismus für uhrwerk - Google Patents

Jahreskalendermechanismus für uhrwerk Download PDF

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Publication number
EP3588201B1
EP3588201B1 EP19179904.8A EP19179904A EP3588201B1 EP 3588201 B1 EP3588201 B1 EP 3588201B1 EP 19179904 A EP19179904 A EP 19179904A EP 3588201 B1 EP3588201 B1 EP 3588201B1
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EP
European Patent Office
Prior art keywords
wheel
subsystem
synchronization
control cam
date
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EP19179904.8A
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English (en)
French (fr)
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EP3588201A1 (de
Inventor
Timée GERBER
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Montblanc Montre SA
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Montblanc Montre SA
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Publication of EP3588201A1 publication Critical patent/EP3588201A1/de
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    • GPHYSICS
    • G04HOROLOGY
    • G04BMECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B19/00Indicating the time by visual means
    • G04B19/24Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars
    • G04B19/241Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars the date is indicated by one or more hands
    • GPHYSICS
    • G04HOROLOGY
    • G04BMECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B19/00Indicating the time by visual means
    • G04B19/24Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars
    • G04B19/243Clocks or watches with date or week-day indicators, i.e. calendar clocks or watches; Clockwork calendars characterised by the shape of the date indicator
    • G04B19/247Clocks 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
    • G04B19/253Driving or releasing mechanisms
    • G04B19/25333Driving or releasing mechanisms wherein the date indicators are driven or released mechanically by a clockwork movement
    • G04B19/25353Driving or releasing mechanisms wherein the date indicators are driven or released mechanically by a clockwork movement driven or released stepwise by the clockwork movement
    • G04B19/2536Driving 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 the field of watchmaking. It relates more particularly to a perpetual calendar mechanism for a timepiece.
  • the document EP2490084 describes a perpetual calendar mechanism which ensures the advance of a calendar mobile by the appropriate number of steps at the end of each month, including that of February according to the simplified leap cycle of four years. The user must therefore not correct the display of the date until the year 2100 AD, which is non-leap even if it is divisible by 4.
  • This mechanism comprises a programming mobile which has a large number of levels, some of which have one or two retractable teeth. These teeth are carried by levers and are brought into their active position by corresponding control cams, so that they can cooperate with a daily indexing wheel comprising several levels of drive fingers. When the daily indexing wheel rotates, it drives the programming mobile at a rate of at least one step per day.
  • one or more of the retractable teeth are in the active position and in the trajectory of the corresponding drive finger, and are also driven by the daily indexing wheel.
  • the programming mobile is thus trained at the rate of one, two or three additional steps depending on the month and, in the case of February, whether the year is leap or not.
  • said programming mobile has high complexity in view of the fact that it comprises a stack of several levels of teeth and control cams, which is difficult to develop and assemble. Furthermore, this arrangement has a relatively height important, which represents a bulk in the thickness of the movement.
  • the aim of the invention is therefore to provide a perpetual calendar mechanism for a timepiece, in which the aforementioned defects are at least partially overcome.
  • the thickness of the mechanism is significantly reduced compared to that of the prior art mentioned above since no complex stacking of cams and wheels is no longer necessary, and the subsystems are easier to handle. adjust individually with respect to the aforementioned prior art programming mobile.
  • the use of the synchronization wheel not only makes it possible to ensure the synchronization of the date mobile with the three subsystems, but also gives the manufacturer great freedom to arrange the three subsystems as well as the mobile of date in the mechanism according to its needs.
  • said synchronization wheel is a toothed ring, with internal or external toothing.
  • the synchronization wheel can thus have a large diameter while leaving the possibility of pivoting other moving parts on axes passing through its interior space.
  • said date wheel set, and / or one or more of said wheels of the subsystems meshes directly with said synchronization wheel.
  • This construction represents a very compact arrangement comprising a minimum of components.
  • control cam of each sub-system is coaxial with said corresponding wheel.
  • each retractable tooth is carried by a corresponding lever mounted to tilt on said corresponding wheel and cooperating with said corresponding control cam in order to determine the radial position of the retractable tooth in question.
  • each control cam is arranged to be driven by a kinematic link driven directly or indirectly on said synchronization wheel.
  • said actuators are arranged to be driven by a watch movement via a respective kinematic link which does not involve said synchronization wheel.
  • Another advantage of the mechanism according to the invention is to allow corrections to be made in both directions, that is to say forwards and backwards, while keeping the synchronization of the different displays when the user performs a manual correction by means of an actuator such as a time setting rod.
  • the mechanism according to the invention can be incorporated into a watch movement, which also comprises at least one display member arranged to be driven by said mechanism, for example in order to provide an indication of the date, month or the like.
  • the figures 1 and 2 represent views of the entire perpetual calendar mechanism 1 according to the invention, respectively in isometric view and in top view (that is to say view from the dial side).
  • the mechanism 1 comprises a date mobile 3, with 31 teeth, integral in rotation with a star 3a, also with 31 teeth, and is driven at a rate of one step per day from a power take-off on the movement base (not shown) by means of a first ad hoc kinematic link 5.
  • this power take-off is located at the level of the mobile of hours 7, which is driven by a motor source such as than a barrel, an electric motor or the like, at the rate of two complete revolutions per day under the control of a regulating system such as a spiral balance, a tuning fork, a quartz oscillator or the like in a known manner.
  • the first kinematic link 5 comprises a series of mobiles arranged in an ad hoc manner ending in a driving wheel 9 arranged to perform one revolution per 24 hours, the gear ratios as well as the teeth that the first kinematic link 5 comprises being adapted for this purpose.
  • the drive wheel set 9 includes not only a pinion in indirect kinematic connection with the hour wheel set 7, but also a finger 9a. The latter is arranged to drive said star with 31 teeth 3a which the date wheel set 3 comprises, at a rate of one step per day, typically around midnight, and therefore acts as an actuator.
  • a jumper 11 cooperates with the teeth of the star 3a in a known manner.
  • the power take-off can be on any other mobile of the movement, the details of the first kinematic link 5 being adapted accordingly so that the finger 9a (or an actuator taking another form) drives the date mobile to at the rate of one step per day.
  • the date mobile 3 is engaged with a synchronization wheel 13 which connects the date mobile 3 to three subsystems 15, 17 and 19 which are arranged laterally with respect to each other in the plane of the mechanism 1, and which ensure that the date mobile 3 performs an appropriate number of additional steps, at the end of months having less than 31 days, as will follow more clearly below.
  • the synchronization wheel 13 may be a toothed crown (as illustrated here), or may be a solid wheel, and acts as a reference between the date wheel set 3 and the correction wheels 15a, 17a, 19a that the subsystems 15 include. , 17, 19, and which will be described below.
  • the date mobile 3 or one of the correction wheels 15a, 17a, 19a pivots, the others are also driven by the synchronization wheel 13.
  • Each of these subsystems 15, 17, 19 is associated with a respective drive finger 23a, 23b, 23c, which is in kinematic connection with the hour wheel 7 by means of a second kinematic connection 21 also arranged in ad hoc manner.
  • This second kinematic link distributes the force received from the hour wheel 7 to each of the drive fingers 23a, 23b, 23c so that they perform one revolution per day and act as an actuator for the subsystem 15, 17, 19 correspondent.
  • These fingers 23a, 23b, 23c each cooperate with a respective retractable tooth that each subsystem 15, 17, 19 comprises, as will clearly follow below.
  • the operation of the first subsystem 15 which is arranged to ensure the additional step that the date mobile takes at the end of each month having less than 31 days, that is to say the months of February, April, June, September and November.
  • This first subsystem 15 is illustrated in more detail on the figures 3a and 3b , and has a correction wheel 15a comprising 31 teeth which engages with the synchronization wheel 13 and therefore performs one revolution per month.
  • the correction wheel 15a carries a retractable tooth 15b integral with a lever 15e.
  • the latter is mounted tilting on a protruding stud from the board of said correction wheel 15a.
  • the retractable tooth 15b is held in the inactive position, that is to say retracted, by an elastic element 15c which cooperates with the lever 15e.
  • the elastic element as illustrated is a leaf spring, but another form of elastic element (spiral spring, elastomer block, leaf spring integral with the lever 15e, etc.) is also possible.
  • An optional mounting plate 15d is interposed between, on the one hand, the lever 15e and the elastic element 15c and, on the other hand, with the correction wheel 15a in order to position the retractable tooth 15b to cooperate with the corresponding drive finger 23a when the latter is in its active position and is located in the path of said drive finger 23a.
  • the position of the lever 15e and therefore the active or inactive position of the retractable tooth 15b are defined by a control (or programming) cam 15f.
  • the lever 15e is maintained in contact with the periphery of the control cam 15f.
  • the latter is integral in rotation with a control wheel 15g, and is mounted coaxially and freely in rotation with respect to said correction wheel 15a.
  • the periphery of the cam 15f comprises five bearings 15h of a first, upper radius, which correspond to months having less than 31 days, and of which the radius is defined to bring the retractable tooth 15b into its active position.
  • the rest of the periphery of the cam 15f has a second, lower radius, defined such that the retractable tooth 15b is retracted out of the path of the driving finger 23a under the effect of the elastic element 15c when this part of the cam 15f cooperates with the lever 15e.
  • the control wheel 15g is rotated at the rate of one revolution per year from the synchronization wheel 13 via a third kinematic link 25 ad hoc.
  • the gear ratio and teeth of this kinematic link 25 are arranged to ensure the desired speed of rotation of the control wheel 15g, as well as to ensure the correct synchronization of the control cam 15f.
  • the upper radius bearings 15h corresponding to the month in question cooperate with the lever 15e so that the retractable tooth 15b is brought into its active position and can cooperate with the corresponding drive finger 23a.
  • the retractable tooth 15b Since the correction wheel 15a rotates at an angular speed which is different from that of the control wheel 15g, the retractable tooth 15b will of course be moved radially several times during each month, but if the tooth 15b is not found in the path of the finger 23a, there will be no additional drive. It can thus be considered that the “active position” of the retractable tooth 15b corresponds exclusively to the state in which the tooth is capable of cooperating with the finger 23a (that is to say that the tooth 15b is deployed and is located in the path of the finger 23b).
  • the control cam 15f is not displaced angularly at the end of each day since the third kinematic connection comprises a wheel with a single tooth 25a which rarely drives the next one. wheel 25b of said kinematic link 25.
  • the third kinematic link comprises a wheel with a single tooth 25a which rarely drives the next one. wheel 25b of said kinematic link 25.
  • a large number of other variants of the third kinematic link are entirely possible, including variants in which the cam 15f is driven every day.
  • the correction wheel 15a will be driven at the rate of an additional step by said finger 23a.
  • the driving of the date mobile 3 by the finger 9a takes place at midnight, and that of the first sub-system by finger 23a a little before, at 11:15 pm, in order to separate these two training sessions in time so that the training of the date mobile 3 is done correctly at midnight, the fact of separating the jumps allows us not to take too many couple in a jump.
  • the exact moments of the two drives can be determined by the manufacturer by working on the angular positions of the actuators 9a and 23a.
  • the date mobile 3 is advanced by two steps, the first of which is effected by the synchronization wheel 13 following the drive of the retractable tooth 15b by the corresponding drive finger 23a (which advances the date indication from 30 to "31”), the other directly via the drive finger 9a, which advances the date indication from 31 to “1”.
  • the retractable tooth 15b is retracted and therefore does not cooperate with the actuator 23a.
  • the additional jump to move the indicator from 30 to 31 is provided by the first subsystem, as described above.
  • the second sub-system 17 is more particularly designed to ensure the jump of the date indication from “29” to “30”, and it therefore occurs every February.
  • the third subsystem 19 is more particularly designed to ensure the additional jump in the date indication from “28” to “29” at the end of the 28-day months.
  • the third sub-system 19 does not intervene, the step from "28" to "29" having been made from regularly by means of the drive finger 9a cooperating with the date mobile 3.
  • the third sub-system 19 intervenes before the second sub-system 17, as will be described. below as part of the discussion of the latter.
  • the second subsystem 17 is illustrated in more detail in figures 4a and 4b , and operates according to the same general principle as the first subsystem 15.
  • the control cam 17f Since the retractable finger 17b of this subsystem is brought into its active position only once a year, in particular at the end of February, the control cam 17f has only one first radius bearing, upper, 17h which occurs once a year. This control cam 17f therefore pivots at the same angular speed as the control cam 15f of the first sub-system 15, and consequently the control wheel 17g of the second sub-system 17 meshes directly with the control wheel 15g of the first sub-system. -system 15. However, a direct engagement is not obligatory, one or more references can be interposed there. Alternatively, the control wheel 17g of the second subsystem 17 can be driven from the synchronization wheel 13 by means of an additional dedicated kinematic link.
  • the upper radius bearing 17h moves the lever 17e so that the retractable tooth 17b adopts its active position in the path of the corresponding drive finger 23b.
  • the corresponding drive finger 23b drives the retractable tooth 17b, if it is present and in its active position, which drives the synchronization wheel 13, as well as the date wheel set 3, by an additional step.
  • This training of the second sub-system 17 must take place before the training of the retractable tooth 15b of the first sub-system 15, in order to change the indication from "29" to "30". In the illustrated embodiment, this training takes place, if necessary, around 22:00, therefore before that of the first subsystem 15. Consequently, at the end of each month of February, the date mobile 3 is driven at a rate of a first step by the synchronization wheel 13 under the effect of the second subsystem 17, then an additional step by the synchronization wheel 13 under the effect of the first subsystem 15, and finally a further step by the drive finger 9a.
  • These three trainings are performed according to a sequence determined by the relationship between the drive fingers 9a, 23a, 23b.
  • the third subsystem 19 is illustrated on figures 5a, 5b and 5c . Again, the components of the third subsystem 19, whose reference signs have the suffixes "a”, “b", “c” etc., correspond to equivalent components of the first subsystem 15 having the same suffix, and therefore should not be redescribed exhaustively. Only the differences will be discussed below.
  • This subsystem 19 concerns the additional jump at the end of the months of February of non-leap years, February comprising only 28 days according to the simplified cycle of 4 years.
  • the control cam 19f comprises three first ray bearings, upper, 19h, which correspond to the months of February at 28 days of the 4-year cycle, the angular difference between a 19h bearing and the following 19h bearing being 90 °, 90 ° and 180 ° respectively.
  • the “missing” level corresponds to the month of February of 29 days of the leap year, which therefore does not require any additional steps from the third subsystem 19.
  • control cam 19f as well as the control wheel 19g which is integral with it in rotation, are arranged to perform one revolution in four years, such that the upper radius bearings 19h control the lever 19e to bring the retractable tooth 19b into its active position at the end of each February having 28 days according to the simplified four-year cycle.
  • control cam 19f is made integral in rotation with the control wheel 19g by means of lugs 19i projecting from the upper surface of the cam 19f, which cooperate with complementary notches (not shown) provided on the underside of the control wheel 19g.
  • This same principle can also be applied to the cams 15f, 17f of other subsystems 15, 17.
  • the positions of the lugs and notches can be reversed, or the cams 15f, 17f, 19f can be screwed, pinned, welded. or glued to their respective control wheel 15g, 17g, 19g, or may be made of material with the latter.
  • This third kinematic link 27 comprises a single wheel.
  • single tooth 27a which is integral in rotation with the correction wheel 19a and which drives a wheel 27b which is coaxial, and integral in rotation with a single tooth wheel 27c (see figure 5c ), which in turn drives the 19g control wheel, the shapes of the teeth as well as the gear ratios ensuring that the latter performs one revolution in 4 years and presents one of its bearings with a radius greater than 19h at the 19th lever at the good time.
  • this third kinematic link are possible, which take force on any suitable mobile.
  • the retractable finger 19b of the third subsystem 19 is driven by the corresponding drive finger 23c, around 8:30 p.m. (but another time before the second subsystem 17 involved is of course possible).
  • the correction wheel 19a is thus driven at the rate of one step, which in turn drives the synchronization wheel 13.
  • the correction wheels 17a, 15a of the other subsystems as well as the date wheel set, are thus driven at by one step, thus advancing the date indication from "28" to "29".
  • the retractable tooth 17b of the second subsystem 17 is driven as described above, which in turn advances the synchronization wheel 13 and the date mobile 3 at the rate of an additional step, advancing the date indication from "29" to " 30 ".
  • the first sub-system 15 intervenes to advance these same elements by a further step, thus advancing the date indication from "30” to "31”, and finally the drive finger 9a drives the date mobile d 'a final step, to advance the indication from "31" to "1".
  • this mechanism cannot delete the leap year for years divisible by 100 which are not divisible by 400, so a user must correct the indication himself at the end of the month of February for the year 2100, 2200 etc.
  • This member 29 may be a hand, a disc, a ring. or similar.
  • a member 29 can be driven directly or indirectly by the date mobile 3 or by the synchronization wheel 13.
  • the mechanism 1 thus forms part of a display mechanism.
  • the synchronization wheel 13 gives the manufacturer the freedom to place the subsystems according to his needs in the plane of the mechanism, at ad hoc locations.
  • the synchronization wheel 13 may be a ring gear with internal teeth, and may be arranged at the periphery of the mechanism 1 and possibly at the periphery of the base movement (not illustrated).
  • Each direct gear can be replaced by an indirect gear comprising one or more returns, and the number of teeth of the various toothed members can vary according to the needs of the manufacturer.

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

Claims (11)

  1. Kalendermechanismus (1) für eine Uhr, umfassend:
    - ein Kalendardrehteil (3), das angeordnet ist, um schrittweise mit einem Schritt pro Tag durch einen entsprechenden Aktuator (9a) angetrieben zu werden;
    dadurch gekennzeichnet, dass der Mechanismus (1) ferner Folgendes umfasst:
    - ein Synchronisationsrad (13) in kinematischer Verbindung mit dem Kalendardrehteil (3);
    - ein erstes Untersystem (15), ein zweites Untersystem (17) und ein drittes Untersystem (19), die seitlich zueinander und im Wesentlichen in einer gleichen Ebene angeordnet sind, wobei jedes Untersystem (15, 17, 19) ein Korrekturrad (15a, 17a, 19a) umfasst, das mit dem Synchronisationsrad (13) in kinematischer Verbindung steht und einen jeweiligen einziehbaren Zahn (15b, 17b, 19b) sowie einen jeweiligen Steuernocken (15f, 17f, 19f) trägt, der angeordnet ist, um den jeweiligen einziehbaren Zahn (15b, 17b, 19b) in eine aktive Position zu führen, in der er am Ende eines Monats durch einen jeweiligen Aktuator (23a, 23b, 23c) angetrieben werden kann,
    wobei:
    - der Steuernocken (15f) des ersten Untersystems (15) angeordnet ist, um den jeweiligen einziehbaren Zahn (15b) am Ende jedes Monats, der weniger als 31 Tage aufweist, in seine aktive Position zu führen;
    - der Steuernocken (17f) des zweiten Untersystems (17) angeordnet ist, um den jeweiligen einziehbaren Zahn (17b) am Ende jedes Monats Februar in seine aktive Position zu führen; und
    - der Steuernocken (19f) des dritten Untersystems (19) angeordnet ist, um den jeweiligen einziehbaren Zahn (19b) am Ende jedes Monats Februar, der nur 28 Tage aufweist, in seine aktive Position zu führen.
  2. Mechanismus (1) nach Anspruch 1, wobei das Synchronisationsrad (13) ein Zahnkranz ist.
  3. Mechanismus (1) nach einem der vorhergehenden Ansprüche, wobei das Kalendardrehteil (3) direkt mit dem Synchronisationsrad (13) in Eingriff steht.
  4. Mechanismus (1) nach einem der vorhergehenden Ansprüche, wobei das Korrekturrad (15a, 17a, 19a) mindestens eines der Untersysteme (15, 17, 19) direkt mit dem Synchronisationsrad (13) in Eingriff steht.
  5. Mechanismus (1) nach einem der vorhergehenden Ansprüche, wobei der Steuernocken (15f, 17f, 19f) jedes Untersystems (15, 17, 19) koaxial zu dem entsprechenden Korrekturrad (15a, 17a, 19a) angeordnet ist.
  6. Mechanismus (1) nach einem der vorhergehenden Ansprüche, wobei jeder einziehbare Zahn (15b, 17b, 19b) fest mit einem jeweiligen Hebel (15e, 17e, 19e) verbunden ist, der an dem jeweiligen Korrekturrad (15a, 17a, 19a) schwenkbar montiert ist und mit dem entsprechenden Steuernocken (15f, 17f, 19f) zusammenwirkt.
  7. Mechanismus (1) nach einem der vorhergehenden Ansprüche, wobei jeder Steuernocken (15f, 17f, 19f) angeordnet ist, um durch eine kinematische Verbindung (25, 27), die Kraft aus dem Synchronisationsrad (13) ableitet, angetrieben zu werden.
  8. Mechanismus (1) nach dem vorhergehenden Anspruch, wobei die Aktuatoren (9a, 23a, 23b, 23c) angeordnet sind, um mittels einer jeweiligen kinematischen Verbindung (5, 21), die das Synchronisationsrad (13) nicht einschließt, durch ein Uhrwerk angetrieben zu werden.
  9. Uhrwerk, das einen Mechanismus (1) nach einem der vorhergehenden Ansprüche sowie mindestens eine Anzeigevorrichtung (29, 31, 33), die angeordnet ist, um durch den Mechanismus (1) angetrieben zu werden, umfasst.
  10. Uhrwerk nach dem vorhergehenden Anspruch, wobei der Mechanismus so angeordnet ist, dass eine Korrektur des Kalendardrehteils (3) durch eine Betätigungsvorrichtung, wie etwa eine Aufzugswelle, in beiden Drehrichtungen vorgenommen werden kann, und dies während die Synchronisation der mindestens einen Anzeigevorrichtung (29, 31, 33) beibehalten wird.
  11. Uhr, die ein Uhrwerk nach einem der Ansprüche 9 und 10 umfasst.
EP19179904.8A 2018-06-22 2019-06-13 Jahreskalendermechanismus für uhrwerk Active EP3588201B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH00794/18A CH715119A1 (fr) 2018-06-22 2018-06-22 Mécanisme de quantième perpétuel pour pièce d'horlogerie.

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Publication Number Publication Date
EP3588201A1 EP3588201A1 (de) 2020-01-01
EP3588201B1 true EP3588201B1 (de) 2020-12-09

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CH (1) CH715119A1 (de)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1240559B1 (de) * 1999-12-24 2005-08-31 Belpanoram AG Jahres-, dauer- oder jahrhundertsdatumschaltwerk
CH704505A2 (fr) * 2011-02-17 2012-08-31 Glashuetter Uhrenbetrieb Gmbh Mécanisme de calendrier.
CH707014B1 (fr) * 2012-09-28 2017-03-15 Mft Et Fabrique De Montres Et Chronomètres Ulysse Nardin Le Locle Sa Mécanisme de quantième.
EP2813902A1 (de) * 2013-06-14 2014-12-17 Cartier Création Studio S.A. Kalendermechanismus für Uhrwerk
CH711749A1 (fr) * 2015-11-13 2017-05-15 Gfpi Sa Mécanisme de calendrier pour pièce d'horlogerie.

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
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EP3588201A1 (de) 2020-01-01
CH715119A1 (fr) 2019-12-30

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