EP3588201A1 - Jahreskalendermechanismus für uhrwerk - Google Patents

Jahreskalendermechanismus für uhrwerk Download PDF

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Publication number
EP3588201A1
EP3588201A1 EP19179904.8A EP19179904A EP3588201A1 EP 3588201 A1 EP3588201 A1 EP 3588201A1 EP 19179904 A EP19179904 A EP 19179904A EP 3588201 A1 EP3588201 A1 EP 3588201A1
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EP
European Patent Office
Prior art keywords
subsystem
wheel
control cam
month
date
Prior art date
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Granted
Application number
EP19179904.8A
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English (en)
French (fr)
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EP3588201B1 (de
Inventor
Timée GERBER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Montblanc Montre SA
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Montblanc Montre SA
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Publication date
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Publication of EP3588201A1 publication Critical patent/EP3588201A1/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
    • G04B19/241—Clocks 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
    • 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 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 not therefore correct the display of the date up to the year 2100 AD, which is non-leap even if it is divisible by 4.
  • This mechanism includes a programming unit 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 unit 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 training finger, and are also driven by the daily indexing wheel.
  • the programming unit 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 a leap year or not.
  • said programming mobile has a 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 high important, which represents a bulk in the thickness of the movement.
  • the object of the invention is therefore to propose a perpetual calendar mechanism for a timepiece, in which the above-mentioned faults 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 that the subsystems are easier to adjust individually with respect to the programming mobile of the aforementioned prior art.
  • the use of the synchronization wheel not only ensures synchronization of the date mobile with the three subsystems, but also gives the manufacturer great freedom to arrange the three subsystems and the mobile of date in the mechanism as required.
  • said synchronization wheel is a ring gear, with internal or external toothing.
  • the synchronization wheel can thus have a large diameter while leaving the possibility of pivoting of other mobiles on axes crossing its interior space.
  • said date mobile, 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 subsystem is coaxial with said corresponding wheel.
  • each retractable tooth is carried by a corresponding lever pivotally mounted 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 timepiece movement via a respective kinematic link which does not involve said synchronization wheel.
  • Another advantage of the mechanism according to the invention is that it allows corrections to be made in both directions, that is to say forward and backward, while keeping the synchronization of the different displays when the user performs a manual correction by means of an operating member 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, the month or the like.
  • the figures 1 and 2 represent views of the assembly of the 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).
  • 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 the rate of one step per day from a power take-off on the movement basic (not shown) via a first ad hoc kinematic link 5.
  • this power take-off is at the 7-hour mobile, which is driven by a power source such as than a barrel, an electric motor or the like, at the rate of two complete turns per day under the control of a regulating system such as a balance spring, 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 drive mobile 9 arranged to perform one revolution per 24 hours, the gear ratios as well as the teeth which the first kinematic link 5 comprises adapted for this purpose.
  • the driving mobile 9 not only comprises a pinion in indirect kinematic connection with the hour mobile 7, but also a finger 9a.
  • the latter is arranged to drive said star with 31 teeth 3a that comprises the date mobile 3, at a rate of one step per day, typically around midnight, and therefore acts as an actuator.
  • a jumper 11 cooperates with the toothing of the star 3a in a known manner.
  • the PTO 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 reason for one step a 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 takes an appropriate number of additional steps, at the end of the months having less than 31 days, as will follow more clearly thereafter.
  • the synchronization wheel 13 can be a ring gear (as illustrated here), or can be a solid wheel, and acts as a reference between the date wheel 3 and correction wheels 15a, 17a, 19a that comprise the subsystems 15 , 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 link 21 also arranged 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 comprises each subsystem 15, 17, 19, as will clearly follow later.
  • 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 comprises a correction wheel 15a comprising 31 teeth which is engaged with the synchronization wheel 13 and therefore performs one revolution per month.
  • the correction wheel 15a carries a retractable tooth 15b secured to a lever 15e.
  • the latter is pivotally mounted on a stud projecting 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 formed integrally 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 training finger 23a when the latter is in its active position and is located in the path of said training 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 kept 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 free to rotate relative to said correction wheel 15a.
  • the periphery of the cam 15f has five bearings 15h of a first, upper radius, which correspond to months having less than 31 days, and whose 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 so that the retractable tooth 15b is retracted out of the path of the drive 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 ad hoc kinematic link 25.
  • the gear ratio and teeth of this kinematic connection 25 are arranged to ensure the desired speed of rotation of the control wheel 15g, as well as to ensure good synchronization of the control cam 15f.
  • the bearings of greater radius 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 training finger 23a.
  • the retractable tooth 15b Since the correction wheel 15a pivots 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 located in the trajectory of finger 23a, there will be no additional training. 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 finger 23b).
  • the date mobile 3 drives the synchronization wheel 13
  • the latter drives the correction wheel 15a as well as the third kinematic link 25, which, if necessary, drives the cam in rotation 15f.
  • the control cam 15f is not angularly moved at the end of each day since the third kinematic link comprises a single-toothed wheel 25a which rarely causes the next wheel 25b of said kinematic linkage 25.
  • the third kinematic linkage is entirely conceivable, including variants in which the cam 15f is driven every day.
  • the correction wheel 15a will be driven at an additional step by said finger 23a.
  • the training of the date mobile 3 by the finger 9a takes place at midnight, and that of the first subsystem by finger 23a a little before, at 11.15 p.m., in order to separate these two trainings 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 much 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 at the rate of two steps, the first of which is effected by the synchronization wheel 13 following driving the retractable tooth 15b by the corresponding training finger 23a (which advances the date indication from 30 to "31”), the other directly via the training 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 second subsystem 17 and the third subsystem 19 which will be described below, intervene for the additional jumps to be made at the end of February.
  • 3 additional jumps must be made (28 to 29, 29 to 30 and 30 to 31), in addition to the jump made by the training finger 9a.
  • the additional jump to switch the indicator from 30 to 31 is provided by the first subsystem, as described above.
  • the second subsystem 17 is more particularly arranged to ensure the jump from the date indication from "29” to "30", and it therefore operates every February.
  • the third subsystem 19 is more particularly arranged to ensure the additional jump of the date indication from “28” to “29” at the end of the 28-day months.
  • the third subsystem 19 does not intervene, the step from "28" to "29" having been carried out regularly via the drive finger 9a cooperating with the date mobile 3.
  • the third subsystem 19 intervenes before the second subsystem 17, as will be described below as part of the discussion on the latter.
  • the second subsystem 17 is illustrated in more detail in Figures 4a and 4b , and operates on 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, especially at the end of February, the control cam 17f has only one bearing of first radius, upper, 17h which intervenes once a year. This control cam 17f therefore pivots at the same angular speed as the control cam 15f of the first subsystem 15, and consequently the control wheel 17g of the second subsystem 17 meshes directly with the control wheel 15g of the first subsystem -system 15. However, a direct meshing is not compulsory, one or more cross-references can be inserted. Alternatively, the control wheel 17g of the second subsystem 17 can be driven from the synchronization wheel 13 by means of a dedicated additional kinematic link.
  • the upper radius bearing 17h moves the lever 17e so that the retractable tooth 17b adopts its active position in the trajectory 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 3, by an additional step.
  • This training of the second subsystem 17 must take place before the training of the retractable tooth 15b of the first subsystem 15, in order to change the indication from "29" to "30".
  • this training is carried out, if necessary, around 10:00 pm, therefore before that of the first subsystem 15. Consequently, at the end of each month in 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 of an additional step by the synchronization wheel 13 under the effect of the first subsystem 15, and finally one more step with the training finger 9a.
  • These three trainings taking place in a sequence determined by the relationship between the drive fingers 9a, 23a, 23b.
  • the third subsystem 19 is illustrated on the 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 the equivalent components of the first subsystem 15 having the same suffix, and therefore should not be completely re-described. Only the differences will be discussed below.
  • This subsystem 19 relates to the additional jump at the end of February in non-leap years, February comprising only 28 days according to the simplified 4-year cycle.
  • the control cam 19f has three first radius 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 requires no additional step on the part of 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 a revolution in four years, so that the bearings of upper radius 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 the 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 on their respective control wheel 15g, 17g, 19g, or can be of material with these.
  • This third kinematic link 27 comprises a wheel with one 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 wheel with a single tooth 27c (see the figure 5c ), which in turn drives the control wheel 19g, the shapes of the teeth as well as the gear ratios ensuring that the latter performs one revolution in 4 years and has one of its bearings with a radius greater than 19h on the lever 19th at 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 training finger 23c, around 8:30 p.m. (but another time before the second subsystem 17 intervenes is of course possible).
  • the correction wheel 19a is thus driven at a 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, are thus trained to one step, 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 wheel 3 by an additional step, advancing the date indication from “29” to “ 30 ".
  • the first subsystem 15 intervenes to advance these same elements by one more 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 needle, 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, in ad hoc locations.
  • the synchronization wheel 13 can be an internal gear ring, and can be arranged at the periphery of the mechanism 1 and possibly at the periphery of the basic movement (not shown).
  • Each direct gear can be replaced by an indirect gear comprising one or more references, 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)
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.

Publications (2)

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

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP19179904.8A Active EP3588201B1 (de) 2018-06-22 2019-06-13 Jahreskalendermechanismus für uhrwerk

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EP (1) EP3588201B1 (de)
CH (1) CH715119A1 (de)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001048568A1 (fr) * 1999-12-24 2001-07-05 Belpanoram Ag Mecanisme de calendrier annuel, perpetuel ou seculaire
EP2490084A1 (de) 2011-02-17 2012-08-22 Glashütter Uhrenbetrieb GmbH Datumsmechanismus
EP2713226A2 (de) * 2012-09-28 2014-04-02 Manufacture et fabrique de montres et chronomètres Ulysse Nardin Le Locle SA Datumsmechanismus
EP2813902A1 (de) * 2013-06-14 2014-12-17 Cartier Création Studio S.A. Kalendermechanismus für Uhrwerk
WO2017081231A1 (fr) * 2015-11-13 2017-05-18 Gfpi S.A. Mecanisme de calendrier pour piece d'horlogerie

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001048568A1 (fr) * 1999-12-24 2001-07-05 Belpanoram Ag Mecanisme de calendrier annuel, perpetuel ou seculaire
EP2490084A1 (de) 2011-02-17 2012-08-22 Glashütter Uhrenbetrieb GmbH Datumsmechanismus
EP2713226A2 (de) * 2012-09-28 2014-04-02 Manufacture et fabrique de montres et chronomètres Ulysse Nardin Le Locle SA Datumsmechanismus
EP2813902A1 (de) * 2013-06-14 2014-12-17 Cartier Création Studio S.A. Kalendermechanismus für Uhrwerk
WO2017081231A1 (fr) * 2015-11-13 2017-05-18 Gfpi S.A. Mecanisme de calendrier pour piece d'horlogerie

Also Published As

Publication number Publication date
CH715119A1 (fr) 2019-12-30
EP3588201B1 (de) 2020-12-09

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