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EP3032349A1 - Drive mechanism of a skipping member - Google Patents

Drive mechanism of a skipping member Download PDF

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Publication number
EP3032349A1
EP3032349A1 EP15196125.7A EP15196125A EP3032349A1 EP 3032349 A1 EP3032349 A1 EP 3032349A1 EP 15196125 A EP15196125 A EP 15196125A EP 3032349 A1 EP3032349 A1 EP 3032349A1
Authority
EP
European Patent Office
Prior art keywords
cam
jumping member
wheel
drive wheel
dead
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP15196125.7A
Other languages
German (de)
French (fr)
Other versions
EP3032349B1 (en
Inventor
Bernat Monferrer
Robin Rusterholz
Edmond Capt
Marco Rochat
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.)
Blancpain SA
Original Assignee
Blancpain 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.)
Filing date
Publication date
Priority claimed from EP14197490.7A external-priority patent/EP3032348A1/en
Application filed by Blancpain SA filed Critical Blancpain SA
Priority to EP15196125.7A priority Critical patent/EP3032349B1/en
Publication of EP3032349A1 publication Critical patent/EP3032349A1/en
Application granted granted Critical
Publication of EP3032349B1 publication Critical patent/EP3032349B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00—Escapements
    • G04B15/14—Component parts or constructional details, e.g. construction of the lever or the escape wheel
    • 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
    • G04B13/00—Gearwork
    • G04B13/002—Gearwork where rotation in one direction is changed into a stepping movement
    • 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
    • G04B13/00—Gearwork
    • 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
    • G04B15/00—Escapements
    • G04B15/06—Free escapements
    • G04B15/08—Lever escapements
    • 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
    • G04B15/00—Escapements
    • G04B15/10—Escapements with constant impulses for the regulating mechanism
    • 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
    • G04B19/02—Back-gearing arrangements between gear train and hands

Definitions

  • the invention relates to the field of mechanical watchmaking. It relates, more particularly, to a drive mechanism of a member jumping in a timepiece comprising a drive wheel arranged to rotate at a constant speed, an indicator of a unit of time, a jumping member integral with said indicator and coaxial with said drive wheel to which said jumping member is coupled by a spring, a cam arranged to control an anchor, said cam having a profile arranged to tilt the anchor in an oscillating movement so as to release the organ jumping once per unit of time.
  • the present invention also relates to a timepiece comprising such a mechanism for driving a jumping member.
  • the unit of time may be the second.
  • the drive mechanism can then be a dead second mechanism, arranged to release the jumping member once per second.
  • a dead second mechanism includes a dead second indicator, usually a large hand in the center of the dial, which is 1 jump per second.
  • Some of these mechanisms are powered by a second source of energy, specific to the second dead mechanism, in addition to the main source of energy required for movement.
  • the dead second cam includes a large number of teeth (30), involving small angular steps, which makes the jumps very sensitive to the imperfections of the dead second cam.
  • the same pallet of the dead second anchor is used both to cooperate with the dead second cam and the second wheel. The dead second anchor blocks the jumping member due to the force of the coupling spring and friction. This friction absorbs a relatively large power, so that the power consumption by the second dead mechanism is high.
  • the invention particularly aims to overcome the various disadvantages of the known mechanisms.
  • an object of the invention is to provide a mechanism for driving a jumping member, and in particular a dead second mechanism, reliable, allowing to have precise jumps at each unit of time, and in particular at each second.
  • the invention also aims to provide a mechanism for driving a jumping member, and in particular a second dead mechanism for having regular jumps throughout its life.
  • the invention also aims to provide a mechanism for driving a jumping member, and in particular a mechanism for second dead, allowing a reduced energy consumption, allowing the use of the same source of energy as that of the movement.
  • the present invention relates to a drive mechanism of a jumping member comprising a drive wheel arranged to rotate at a constant speed, an indicator of a unit of time, a jumping member integral with said indicator and coaxial with said driving wheel to which said jumping member is coupled by a spring, a cam arranged to control an anchor, said cam having a profile arranged to tilt the anchor in an oscillating motion so as to release the jumping member once by unit of time.
  • the cam and the jumping member have distinct pivoting axes
  • said drive mechanism further comprising an intermediate gear cinematically linking the drive wheel to the cam
  • the anchor has four distinct arms, two of the four arms constituting feelers arranged to cooperate with the cam and the other two arms constituting exhaust arms arranged to successively block and release once per unit of time alternating jumping member.
  • the intermediate wheel may comprise an intermediate mobile formed of an intermediate gear arranged to cooperate with the drive wheel and an intermediate wheel arranged to cooperate with a camming wheel integral with the cam.
  • the intermediate gear can be sized so that the cam comprises less than thirty teeth, each tooth having a front ramp, and performs more than one revolution per minute.
  • the unit of time is the second, the drive wheel being arranged to turn in 60 seconds, and the indicator being a second dead indicator, the cam can include ten teeth and be arranged to perform three revolutions per minute, each tooth having a front ramp decomposing in six steps.
  • the forward ramp of each tooth of the cam has, on the last three steps of the tooth, a slope greater than the slope of the front ramp on the first three steps of the tooth.
  • the four arms of the anchor can be arranged to form substantially an X, the probe arm positioned to cooperate with the cam being disposed opposite to the pivot point of the anchor to the arm exhaust positioned to release the jumping member.
  • said drive mechanism also comprises a mechanism for securing the relative position of the drive wheel and the jumping member.
  • the mechanism for securing the relative position of the drive wheel and the jumping member may comprise first support means provided on the drive wheel and a first stop provided on the jumping member, said first support means being arranged to bear on the first stop and limit the stroke of the jumping member, when the drive wheel and the jumping member rotate in opposite directions.
  • the mechanism for securing the relative position of the drive wheel and the jumping member may comprise second support means provided on the drive wheel and a second stop provided on the jumping member, said second support means being arranged to rest on the second stop and limit the travel of the drive wheel when the jumping member is stopped.
  • said first and second support means may comprise a pin.
  • the first and second support means may comprise an eccentric.
  • the jumping member may be a wheel having at least two recessed areas separated by at least one arm, and the first and second support means are arranged on either side of the arm, said arm constituting at least one of the first and second stops on which the first and second support means are able to rely respectively.
  • the drive mechanism of a jumping member allows to have precise jumps at each unit of time while allowing a reduced power consumption. In addition, jumps will be regular throughout the life of the mechanism.
  • the present invention also relates to a timepiece comprising a watch movement provided with a finishing gear powered by a power source, and a drive mechanism of a jumping member as defined above.
  • the drive wheel of the second dead mechanism can be powered by the energy source of the movement.
  • the drive wheel may be the second wheel of the work train.
  • the training mechanism then constitutes "a second dead mechanism", and will be designated thereafter under this expression.
  • the second dead mechanism is integrated in a mechanical timepiece, comprising a watch movement provided with a finishing gear powered by a power source, such as a barrel.
  • the finishing gear train traditionally comprises a second wheel 1 comprising 60 teeth and arranged to turn in 60 seconds.
  • the movement also traditionally includes an escape pinion 2 and an escape wheel 3 as well as an escapement anchor and a pendulum.
  • the second dead mechanism comprises a drive wheel constituted more specifically here by the second wheel of the finishing gear.
  • the dead second mechanism also comprises a jumping member 6, such as a wheel, secured to a dead second indicator, such as a needle (not shown).
  • the jumping member 6 is mounted loosely on the axis of the second wheel 1, so that the jumping member 6 is coaxial with the second wheel 1 and not integral with the latter.
  • Jumping organ 6 is elastically connected to the second wheel 1 by means of a spiral spring 8, which is on the one hand driven on the second wheel 1 and secondly fixed on the jumping member 6.
  • the spring -spiral 8 comprises at its end intended to be fixed on the jumping member 6, a fixing notch 9 in which is inserted a holding pin 11 provided on the jumping member.
  • the spiral spring 8 comprises at its end intended to be fixed on the jumper member 6, a double fixing notch 32 having two housings or notches.
  • the jumping member 6 is provided with two holding lugs 34, each holding lug 34 being intended to be inserted into one of the housings of the double fixing notch 32.
  • the holding lugs 34 are arranged to limit the axial clearance. . More particularly, each holding pin 34 has a groove around which is positioned each notch.
  • the jumping member 6 is a wheel comprising 30 teeth and making a turn in 60 seconds.
  • the dead second mechanism also comprises a dead second cam mobile formed of a cam drive wheel 10 and a second dead cam 12, integral with said cam drive wheel 10.
  • the cam drive wheel 10 is arranged to cooperate with the escape pinion 2. More particularly, the cam drive wheel 10 is in direct contact with the escape pinion 2.
  • the second wheel 1 and the cam drive wheel 10 are pivotally mounted on the frame of the movement so as to have separate pivot axes, so that the dead second cam 12 and the jumping member 6 (or the second wheel 1) are not coaxial.
  • the second wheel 1 and the cam drive wheel 10 are kinematically connected by an intermediate wheel, and more particularly an intermediate mobile comprising an intermediate gear 14 meshing with the second wheel 1 and an intermediate wheel 16, integral with said intermediate gear 14, and meshing with the driving cam wheel 10.
  • the main kinematic chain of the movement goes from the wheel from second 1 to the escape gear 2 passing successively by the intermediate gear and the cam drive wheel 10, without a direct connection between the drive pinion and the second wheel.
  • the dimensions and the number of teeth of the intermediate mobile are provided so that the cam drive wheel 10 and the dead second cam 12 perform one revolution per 20 seconds, ie 3 revolutions per minute, the cam driving wheel 10 comprising 66 teeth and the dead second cam 12 comprising 10 teeth 18. It is obvious that the speed of the cam driving wheel and the dead second cam, as well as the number of teeth can be modified without departing from the scope of the present invention. We can choose for example a period of 16 seconds, with a second dead cam with 8 teeth.
  • the dead second mechanism also includes a second dead anchor 20 pivotally mounted at a pivot point A on the movement frame, and controlled by the second dead cam 12 to release and blow the jumping member 6 once per second. .
  • the jumping member 6 thus constitutes a dead second escape wheel.
  • the dead second anchor 20 comprises four separate arms 20a, 20b, 20c and 20d.
  • the end of each arm acts as a pallet.
  • the term "pallet" is used to designate the end of an arm 20a, 20b, 20c and 20d, the pallet thus forming a single piece with the corresponding arm.
  • the second dead anchor 20 is monobloc and made by LIGA.
  • the upper arm 20a and the lower arm 20b constitute upper and lower probes arranged to cooperate with the cam of second dead 12.
  • the upper arm 20c and the lower arm 20d are upper and lower exhaust arms arranged to successively block and release, once a second, the jumping member 6 alternately.
  • the four arms 20a, 20b, 20c and 20d are positioned relative to the pivot point A so as to form substantially an X, the end of each arm being bent to cooperate with either the dead second cam 12 or with the Jumping member 6.
  • the arms 20a, 20b, 20c and 20d work in opposition to the pivot point A.
  • the upper feeler arm 20a is positioned to be controlled by the tooth profile 18 of the dead second cam 12 while the exhaust arm opposite from the pivot point A, namely the lower exhaust arm 20d. , is positioned to release the jumping member 6.
  • Each tooth 18 of the dead second cam 12 has a profile defined by a front ramp 18a, the functional portion of the tooth on which the end or the pallet of the feeler arms 20a, 20b rubs, and a reverse 18b.
  • the frequency of the balance is chosen at 3 Hz (or 6 alternations per second) so that each front ramp 18a can be decomposed into six steps, each step corresponding to a rotation angle of 3 ° of the cam second dead. It is obvious that another frequency can be chosen.
  • the front ramp 18a of each tooth 18 has a slope which is higher on the last three steps corresponding to a rotation angle of the second dead cam between 9 ° and 18 °, ie at moment close to the jump, that on the first three steps corresponding to an angle of rotation of the dead second cam between 0 ° and 9 °.
  • the height is of the tooth corresponding to the third step, ie a rotation angle of 9 ° of the dead second cam, is between 10% and 15% of the height h, and the height b of the tooth corresponding to the fifth pitch, an angle of rotation 15 ° of the dead second cam, is between 55% and 60% of the height h.
  • the profile of the reverse 18b avoids the premature jump of the second dead anchor.
  • This profile is the result of the profile of the front ramp 18a, so that when the pallet of one of the feeler arms is in contact with the front ramp 18a of a tooth 18 of the dead second cam 12, a constant clearance is maintained between the dead second cam 12 and the passive pallet of the other probe arm (that is to say the pallet of the probe arm which is not in contact with the ramp before a tooth).
  • said mechanism for securing the relative position of the second wheel 1 and the jumping member 6 comprises a first pin 30 and a second pin 36 driven on the second wheel 1. Said pins 30 and 36 are shown only on the figure 4 to simplify the drawings.
  • the jumping member 6 is a toothed wheel having four recessed areas whose edges form four separation arms 6a, 6b, 6c, 6d. The pins 30 and 36 are positioned on the second wheel 1 on either side of one of the separation arms 6a.
  • the first pin 30 is positioned so as to be in front of the separation arm 6a of the jumping member 6 when the second wheel 1 and the jumping member 6 rotate in the same direction, especially during operation. normal mechanism.
  • the first pin 30, secured to the second wheel 1 is supported on the separation arm 6a of the jumping member 6, the separation arm 6a then constituting a stop for the first pin 30.
  • the first pin 30, continuing its movement with the second wheel 1, drives the separation arm 6a and thus the jumping member 6 in its displacement, so that the second wheel 1 and the jumping member 6 recoil together and remain indexed, especially when setting the time.
  • the second pin 36 is positioned so as to be at the rear of the separation arm 6a of the jumping member 6 when the second wheel 1 and the jumping member 6 rotate in the same direction, in particular during the normal operation of the mechanism .
  • a margin of at least one step, and preferably equal to one step, is provided.
  • the first and second support means comprise an eccentric 38, 40 in place of the first pin 30 and the second pin 36 respectively, their operation being similar.
  • the advantage of the eccentrics 38 and 40 with respect to the pins 30, 36 is that the watchmaker can move them and position to adjust the clearance between the two eccentric 38, 40 and the separation arm 6a of the jumping member 6. This allows less depend on manufacturing tolerances.
  • the first support means are positioned so as to be in front of one of the separation arms of the jumping member 6 when the second wheel 1 and the jumping member 6 rotate in the same direction, and the second support means are positioned to be at the rear of another separation arm of the jumping member 6 when the second wheel 1 and the jumping member 6 rotate in the same way.
  • one of the separation arms of the jumping member 6 constitutes the first stop on which the first support means are able to rest and the other separation arm of the jumping member 6 constitutes the second stop on which the second support means are able to rely.
  • the first and second stops are not constituted by the separating arms of the jumping member but are parts driven on the jumping member 6 and arranged so as to be able to come into contact with their respective bearing means, in particular pins or eccentrics, provided on the drive wheel.
  • the second dead mechanism drives the intermediate gear 14 and thus the intermediate wheel 16, which in turn drives the cam drive wheel 10 and thus the dead second cam 12.
  • Said dead second cam 12 turning, allows the front ramp 18a of a tooth 18 to act on the pallet of the upper probe arm 20a of the dead second anchor 20, so that said anchor 20 tilts around its pivot point A to exit, to the opposite, the pallet of the lower exhaust arm 20d of the second dead anchor 20 of the toothing of the jumping member 6.
  • step 0 represented on the figure 1
  • step 5 the fifth step of the ramp before 18a of the tooth concerned (ie for an angle of rotation of the dead second cam 12 of 15 °, cf. figure 5 )
  • the pallet of the lower exhaust arm 20d does not come out of the toothing of the jumping member 6, regardless of the clearance clearance.
  • the asymmetric profile of each tooth 18 of the second dead cam 12 is such that the raising of the anchor is done progressively with the pallet of the upper probe arm 20a while the pallet of the lower probe arm 20b descends without touching the dead second cam 12.
  • the jumping member 6 has not yet jumped, and is still blocked by the pallet of the lower exhaust arm 20d.
  • the pallet of the upper probe arm 20a has arrived at the fifth step of the ramp before 18a, if the dead second anchor 20 undergoes a catch of play following a shock for example, the pallet of the lower probe arm 20b is positioned at the contact 18b of the corresponding tooth 18 of the dead second cam 12, as shown in FIG. figure 3 .
  • the jumping organ 6 has not jumped, but remains at the limit of jumping.
  • the jumping member 6 jumps when the pallet of the upper feeler arm 20a moves between the fifth and sixth steps.
  • the movement of the dead second anchor is a reciprocating movement that releases, tooth by tooth, the jumping member 6, once with the pallet of the upper exhaust arm 20c, then with the pallet of the arm lower exhaust 20d, successively and alternately.
  • the dead second indicator advances in increments of 1 second.
  • the second dead mechanism of the invention allows for precise jumps every second with less energy consumption.
  • the mechanism of the invention is powered by the same source of energy as the finishing gear. A second source of energy is not necessary.
  • the arrangement on separate axes of the jumper member and the dead second cam provides optimized shapes for the vanes of the exhaust arms on the one hand and for the pallets of the feeler arms on the other hand , in connection with optimized shapes of the teeth of the dead second cam.
  • the energy consumption due to the spiral spring between the second wheel and the jumping member is almost zero. In particular, the higher the slope of the front ramp of the teeth of the second dead cam will be high on the last three steps of the tooth, the more the jump will be marked and therefore accurate.
  • a lower slope on the first three steps of the tooth makes the angular pitch of the second dead anchor relatively low over this period.
  • the torque consumption is therefore low.
  • the slope on the last three steps is on the contrary more important but must however remain measured in order to avoid over-consumption of torque on the mobile cam second dead.
  • the angular pitch of the dead second anchor is higher on the last three steps, which allows the jump to be performed over a larger measurement range, and consequently increases the jump accuracy.
  • the use of a dead second cam with only 10 teeth makes it possible to obtain larger angular steps, and therefore less sensitive jumps to the imperfections of the dead second cam.
  • the radius forming the flank of the toothing of the jumping member is chosen to be concentric and equal to that of the second dead anchor with which it is in contact.
  • the arrangement on separate axes of the jumping member and the second dead cam makes it possible not to add a large number of parts on the same axis and therefore to limit the accumulation of tolerances and the misalignment of the mobiles, unlike to the coaxial mechanisms of the prior art.
  • the precision on the axis of the jumping member is therefore greater while simplifying the assembly of parts.
  • the second dead mechanism described above can be adapted to another unit of time than the second.
  • the drive mechanism of a jumping member according to the invention can be adapted to the display of any unit of time: second, minute, ten seconds, ten minutes, etc. To do this, the skilled person knows how to adapt accordingly the number of teeth on the cam and the jumping member, as well as the gear ratios in the gear train.

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  • General Physics & Mathematics (AREA)
  • Transmission Devices (AREA)
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Abstract

L'invention se rapporte à un mécanisme d'entrainement d'un organe sautant comprenant une roue d'entrainement (1), un indicateur d'une unité de temps, un organe sautant (6) solidaire dudit indicateur et coaxial à ladite roue d'entrainement (1) à laquelle ledit organe sautant (6) est accouplé par un ressort (8), une came (12) agencée pour faire basculer une ancre (20) selon un mouvement oscillant de manière à libérer l'organe sautant (6) une fois par unité de temps. Selon l'invention la came (12) et l'organe sautant (6) présentent des axes de pivotement distincts, le mécanisme d'entrainement comprenant en outre un rouage intermédiaire liant cinématiquement la roue d'entrainement (1) à la came (12), et l'ancre (20) présente quatre bras (20a, 20b, 20c, 20d) distincts, deux (20a, 20b) des quatre bras constituant des palpeurs agencés pour coopérer avec la came (12) et les deux autres bras (20c, 20d) constituant des bras d'échappement agencés pour successivement bloquer et libérer une fois par unité de temps l'organe sautant (6) en alternance.The invention relates to a drive mechanism for a jumping member comprising a drive wheel (1), an indicator of a unit of time, a jumping member (6) integral with said indicator and coaxial with said drive wheel. the drive (1) to which said jumping member (6) is coupled by a spring (8), a cam (12) arranged to tilt an anchor (20) in an oscillating movement so as to release the jumping member (6). ) once per unit of time. According to the invention the cam (12) and the jumping member (6) have distinct pivot axes, the drive mechanism further comprising an intermediate gear kinematically linking the drive wheel (1) to the cam (12). ), and the anchor (20) has four distinct arms (20a, 20b, 20c, 20d), two (20a, 20b) of the four arms constituting feelers arranged to cooperate with the cam (12) and the other two arms ( 20c, 20d) constituting exhaust arms arranged to successively block and release once per unit time the jumping member (6) alternately.

Description

Domaine de l'inventionField of the invention

L'invention se rapporte au domaine de l'horlogerie mécanique. Elle concerne, plus particulièrement, un mécanisme d'entrainement d'un organe sautant dans une pièce d'horlogerie comprenant une roue d'entrainement agencée pour tourner à vitesse constante, un indicateur d'une unité de temps, un organe sautant solidaire dudit indicateur et coaxial à ladite roue d'entrainement à laquelle ledit organe sautant est accouplé par un ressort, une came agencée pour commander une ancre, ladite came présentant un profil agencé pour faire basculer l'ancre selon un mouvement oscillant de manière à libérer l'organe sautant une fois par unité de temps. La présente invention concerne également une pièce d'horlogerie comprenant un tel mécanisme d'entrainement d'un organe sautant.The invention relates to the field of mechanical watchmaking. It relates, more particularly, to a drive mechanism of a member jumping in a timepiece comprising a drive wheel arranged to rotate at a constant speed, an indicator of a unit of time, a jumping member integral with said indicator and coaxial with said drive wheel to which said jumping member is coupled by a spring, a cam arranged to control an anchor, said cam having a profile arranged to tilt the anchor in an oscillating movement so as to release the organ jumping once per unit of time. The present invention also relates to a timepiece comprising such a mechanism for driving a jumping member.

Arrière-plan de l'inventionBackground of the invention

Lorsque la roue d'entrainement fait un tour par minute, l'unité de temps peut être la seconde. Le mécanisme d'entrainement peut alors constituer un mécanisme de seconde morte, agencé pour libérer l'organe sautant une fois par seconde. Un mécanisme de seconde morte comprend un indicateur de seconde morte, généralement une grande aiguille au centre du cadran, qui fait 1 saut par seconde. Ces mécanismes sont de réalisation extrêmement compliquée. Ils manquent toutefois parfois de précision, les sauts s'effectuant dans certains cas au 5/6 de seconde. Ils sont également très consommateurs d'énergie.When the drive wheel is one revolution per minute, the unit of time may be the second. The drive mechanism can then be a dead second mechanism, arranged to release the jumping member once per second. A dead second mechanism includes a dead second indicator, usually a large hand in the center of the dial, which is 1 jump per second. These mechanisms are extremely complicated realization. However, they sometimes lack accuracy, the jumps taking place in some cases to 5/6 of a second. They are also very energy consumers.

Certains de ces mécanismes sont alimentés par une deuxième source d'énergie, propre au mécanisme de seconde morte, en plus de la source d'énergie principale, nécessaire au mouvement.Some of these mechanisms are powered by a second source of energy, specific to the second dead mechanism, in addition to the main source of energy required for movement.

D'autres mécanismes sont alimentés par la source d'énergie du mouvement, du type de celui décrit en préambule. De tels mécanismes sont connus de l'homme du métier et décrits par exemple dans le brevet CH 311 865 . Dans ces mécanismes, la came de seconde morte comprend un grand nombre de dents (30), impliquant de petits pas angulaires, ce qui rend les sauts très sensibles aux imperfections de la came de seconde morte. De plus, la même palette de l'ancre de seconde morte est utilisée à la fois pour coopérer avec la came de seconde morte et la roue de seconde. L'ancre de seconde morte bloque l'organe sautant sous l'effet de la force du ressort d'accouplement et des frottements. Ces frottements absorbent une puissance relativement grande, de sorte que la consommation d'énergie par le mécanisme de seconde morte est élevée.Other mechanisms are powered by the energy source of the movement, of the type described in the preamble. Such mechanisms are known to those skilled in the art and described for example in the patent CH 311865 . In these mechanisms, the dead second cam includes a large number of teeth (30), involving small angular steps, which makes the jumps very sensitive to the imperfections of the dead second cam. In addition, the same pallet of the dead second anchor is used both to cooperate with the dead second cam and the second wheel. The dead second anchor blocks the jumping member due to the force of the coupling spring and friction. This friction absorbs a relatively large power, so that the power consumption by the second dead mechanism is high.

Résumé de l'inventionSummary of the invention

L'invention a notamment pour objectif de pallier les différents inconvénients des mécanismes connus.The invention particularly aims to overcome the various disadvantages of the known mechanisms.

Plus précisément, un objectif de l'invention est de fournir un mécanisme d'entrainement d'un organe sautant, et notamment un mécanisme de seconde morte, fiable, permettant d'avoir des sauts précis à chaque unité de temps, et notamment à chaque seconde.More specifically, an object of the invention is to provide a mechanism for driving a jumping member, and in particular a dead second mechanism, reliable, allowing to have precise jumps at each unit of time, and in particular at each second.

L'invention a également pour objectif de fournir un mécanisme d'entrainement d'un organe sautant, et notamment un mécanisme de seconde morte permettant d'avoir des sauts réguliers durant toute sa durée de vie.The invention also aims to provide a mechanism for driving a jumping member, and in particular a second dead mechanism for having regular jumps throughout its life.

L'invention a également pour objectif de fournir un mécanisme d'entrainement d'un organe sautant, et notamment un mécanisme de seconde morte, permettant une consommation d'énergie réduite, autorisant l'utilisation de la même source d'énergie que celle du mouvement.The invention also aims to provide a mechanism for driving a jumping member, and in particular a mechanism for second dead, allowing a reduced energy consumption, allowing the use of the same source of energy as that of the movement.

A cet effet, la présente invention concerne un mécanisme d'entrainement d'un organe sautant comprenant une roue d'entrainement agencée pour tourner à vitesse constante, un indicateur d'une unité de temps, un organe sautant solidaire dudit indicateur et coaxial à ladite roue d'entrainement à laquelle ledit organe sautant est accouplé par un ressort, une came agencée pour commander une ancre, ladite came présentant un profil agencé pour faire basculer l'ancre selon un mouvement oscillant de manière à libérer l'organe sautant une fois par unité de temps.For this purpose, the present invention relates to a drive mechanism of a jumping member comprising a drive wheel arranged to rotate at a constant speed, an indicator of a unit of time, a jumping member integral with said indicator and coaxial with said driving wheel to which said jumping member is coupled by a spring, a cam arranged to control an anchor, said cam having a profile arranged to tilt the anchor in an oscillating motion so as to release the jumping member once by unit of time.

Selon l'invention, la came et l'organe sautant présentent des axes de pivotement distincts, ledit mécanisme d'entrainement comprenant en outre un rouage intermédiaire liant cinématiquement la roue d'entrainement à la came, et l'ancre présente quatre bras distincts, deux des quatre bras constituant des palpeurs agencés pour coopérer avec la came et les deux autres bras constituant des bras d'échappement agencés pour successivement bloquer et libérer une fois par unité de temps l'organe sautant en alternance.According to the invention, the cam and the jumping member have distinct pivoting axes, said drive mechanism further comprising an intermediate gear cinematically linking the drive wheel to the cam, and the anchor has four distinct arms, two of the four arms constituting feelers arranged to cooperate with the cam and the other two arms constituting exhaust arms arranged to successively block and release once per unit of time alternating jumping member.

D'une manière avantageuse, le rouage intermédiaire peut comprendre un mobile intermédiaire formé d'un pignon intermédiaire agencé pour coopérer avec la roue d'entrainement et d'une roue intermédiaire agencée pour coopérer avec une roue entraineuse de came solidaire de la came.Advantageously, the intermediate wheel may comprise an intermediate mobile formed of an intermediate gear arranged to cooperate with the drive wheel and an intermediate wheel arranged to cooperate with a camming wheel integral with the cam.

De préférence, le rouage intermédiaire peut être dimensionné pour que la came comprenne moins de trente dents, chaque dent présentant une rampe avant, et effectue plus d'un tour par minute.Preferably, the intermediate gear can be sized so that the cam comprises less than thirty teeth, each tooth having a front ramp, and performs more than one revolution per minute.

D'une manière avantageuse, selon une variante de réalisation, l'unité de temps est la seconde, la roue d'entrainement étant agencée pour faire un tour en 60 secondes, et l'indicateur étant un indicateur de seconde morte, la came peut comprendre dix dents et être agencée pour effectuer trois tours par minute, chaque dent présentant une rampe avant se décomposant en six pas.Advantageously, according to an alternative embodiment, the unit of time is the second, the drive wheel being arranged to turn in 60 seconds, and the indicator being a second dead indicator, the cam can include ten teeth and be arranged to perform three revolutions per minute, each tooth having a front ramp decomposing in six steps.

De préférence, la rampe avant de chaque dent de la came présente, sur les trois derniers pas de la dent, une pente supérieure à la pente de la rampe avant sur les trois premiers pas de la dent.Preferably, the forward ramp of each tooth of the cam has, on the last three steps of the tooth, a slope greater than the slope of the front ramp on the first three steps of the tooth.

D'une manière avantageuse, les quatre bras de l'ancre peuvent être disposés de manière à former sensiblement un X, le bras palpeur positionné pour coopérer avec la came étant disposé de manière opposée par rapport au point de pivotement de l'ancre au bras d'échappement positionné pour libérer l'organe sautant.Advantageously, the four arms of the anchor can be arranged to form substantially an X, the probe arm positioned to cooperate with the cam being disposed opposite to the pivot point of the anchor to the arm exhaust positioned to release the jumping member.

D'une manière avantageuse, ledit mécanisme d'entrainement comprend également un mécanisme de sécurisation de la position relative de la roue d'entrainement et de l'organe sautant.Advantageously, said drive mechanism also comprises a mechanism for securing the relative position of the drive wheel and the jumping member.

De préférence, le mécanisme de sécurisation de la position relative de la roue d'entrainement et de l'organe sautant peut comprendre des premiers moyens d'appui prévus sur la roue d'entrainement et une première butée prévue sur l'organe sautant, lesdits premiers moyens d'appui étant agencés pour s'appuyer sur la première butée et limiter la course de l'organe sautant, lorsque la roue d'entrainement et l'organe sautant tournent dans des sens opposés.Preferably, the mechanism for securing the relative position of the drive wheel and the jumping member may comprise first support means provided on the drive wheel and a first stop provided on the jumping member, said first support means being arranged to bear on the first stop and limit the stroke of the jumping member, when the drive wheel and the jumping member rotate in opposite directions.

De préférence, le mécanisme de sécurisation de la position relative de la roue d'entrainement et de l'organe sautant peut comprendre des seconds moyens d'appui prévus sur la roue d'entrainement et une seconde butée prévue sur l'organe sautant, lesdits seconds moyens d'appui étant agencés pour s'appuyer sur la seconde butée et limiter la course de la roue d'entrainement lorsque l'organe sautant est arrêté.Preferably, the mechanism for securing the relative position of the drive wheel and the jumping member may comprise second support means provided on the drive wheel and a second stop provided on the jumping member, said second support means being arranged to rest on the second stop and limit the travel of the drive wheel when the jumping member is stopped.

D'une manière avantageuse, lesdits premiers et seconds moyens d'appui peuvent comprendre une goupille. Dans une autre variante, les premiers et seconds moyens d'appui peuvent comprendre un excentrique.Advantageously, said first and second support means may comprise a pin. In another variant, the first and second support means may comprise an eccentric.

D'une manière avantageuse, l'organe sautant peut être une roue présentant au moins deux zones évidées séparées par au moins un bras, et les premiers et seconds moyens d'appui sont disposés de part et d'autre du bras, ledit bras constituant au moins l'une des première et seconde butées sur lesquelles les premiers et seconds moyens d'appui sont susceptibles de s'appuyer respectivement.Advantageously, the jumping member may be a wheel having at least two recessed areas separated by at least one arm, and the first and second support means are arranged on either side of the arm, said arm constituting at least one of the first and second stops on which the first and second support means are able to rely respectively.

Le mécanisme d'entrainement d'un organe sautant selon l'invention permet d'avoir des sauts précis à chaque unité de temps tout en permettant une consommation d'énergie réduite. En outre, les sauts seront réguliers, pendant toute la durée de vie du mécanisme.The drive mechanism of a jumping member according to the invention allows to have precise jumps at each unit of time while allowing a reduced power consumption. In addition, jumps will be regular throughout the life of the mechanism.

La présente invention concerne également une pièce d'horlogerie comprenant un mouvement horloger pourvu d'un rouage de finissage alimenté par une source d'énergie, ainsi qu'un mécanisme d'entrainement d'un organe sautant tel que défini ci-dessus.The present invention also relates to a timepiece comprising a watch movement provided with a finishing gear powered by a power source, and a drive mechanism of a jumping member as defined above.

D'une manière avantageuse, la roue d'entrainement du mécanisme de seconde morte peut être alimentée par la source d'énergie du mouvement.Advantageously, the drive wheel of the second dead mechanism can be powered by the energy source of the movement.

De préférence, la roue d'entrainement peut être la roue de seconde du rouage de finissage.Preferably, the drive wheel may be the second wheel of the work train.

Description sommaire des dessinsBrief description of the drawings

D'autres caractéristiques et avantages de l'invention apparaîtront plus clairement à la lecture de la description suivante d'un mode de réalisation particulier de l'invention, donné à titre de simple exemple illustratif et non limitatif, et des figures annexées, parmi lesquelles :

  • les figures 1 à 4 représentent une vue de dessus d'un mécanisme de seconde morte conforme à l'invention, l'ancre de seconde morte occupant différentes positions en fonction des pas d'une dent de la came de seconde morte,
  • la figure 5 représente une vue du profil d'une dent de la came de seconde morte,
  • la figure 6 est une vue en perspective d'une variante de réalisation du mécanisme de sécurisation de la position relative de la roue d'entrainement et de l'organe sautant, et
  • la figure 7 est une vue en perspective de la fixation du ressort-spiral sur l'organe sautant.
Other features and advantages of the invention will appear more clearly on reading the following description of a particular embodiment of the invention, given by way of a simple illustrative and nonlimiting example, and the appended figures, among which: :
  • the Figures 1 to 4 represent a view from above of a dead second mechanism according to the invention, the dead second anchor occupying different positions according to the steps of a tooth of the dead second cam,
  • the figure 5 represents a profile view of a tooth of the dead second cam,
  • the figure 6 is a perspective view of an alternative embodiment of the mechanism for securing the relative position of the drive wheel and the jumping member, and
  • the figure 7 is a perspective view of the attachment of the spiral spring to the jumping member.

Description détaillée d'un mode de réalisation préféréDetailed description of a preferred embodiment

La description qui suit concerne un mode de réalisation de l'invention pour lequel l'unité de temps est la seconde. Le mécanisme d'entrainement constitue alors « un mécanisme de seconde morte », et sera désigné par la suite sous cette expression.The following description relates to an embodiment of the invention for which the unit of time is the second. The training mechanism then constitutes "a second dead mechanism", and will be designated thereafter under this expression.

En référence à la figure 1, le mécanisme de seconde morte selon l'invention est intégré à une pièce d'horlogerie mécanique, comprenant un mouvement horloger pourvu d'un rouage de finissage alimenté par une source d'énergie, telle qu'un barillet. Le rouage de finissage comprend traditionnellement une roue de seconde 1, comprenant 60 dents et agencée pour faire une tour en 60 secondes. Le mouvement comprend aussi traditionnellement un pignon d'échappement 2 et une roue d'échappement 3 ainsi qu'une ancre d'échappement et un balancier. Ces éléments sont connus de l'homme du métier et ne nécessitent pas de description détaillée. On notera toutefois que la fréquence du balancier est avantageusement choisie à 3 Hz, comme on le comprendra ci-après.With reference to the figure 1 , the second dead mechanism according to the invention is integrated in a mechanical timepiece, comprising a watch movement provided with a finishing gear powered by a power source, such as a barrel. The finishing gear train traditionally comprises a second wheel 1 comprising 60 teeth and arranged to turn in 60 seconds. The movement also traditionally includes an escape pinion 2 and an escape wheel 3 as well as an escapement anchor and a pendulum. These elements are known to those skilled in the art and do not require a detailed description. Note however that the frequency of the balance is advantageously chosen at 3 Hz, as will be understood below.

Le mécanisme de seconde morte comprend une roue d'entrainement constituée plus spécifiquement ici par la roue de seconde 1 du rouage de finissage.The second dead mechanism comprises a drive wheel constituted more specifically here by the second wheel of the finishing gear.

Le mécanisme de seconde morte comprend également un organe sautant 6, tel qu'une roue, solidaire d'un indicateur de seconde morte, tel qu'une aiguille (non représenté). L'organe sautant 6 est monté fou sur l'axe de la roue de seconde 1, de sorte que l'organe sautant 6 est coaxial à la roue de seconde 1 et non solidaire de cette dernière. L'organe sautant 6 est relié élastiquement à la roue de seconde 1 au moyen d'un ressort spiral 8, qui est d'une part chassé sur la roue de seconde 1 et d'autre part fixé sur l'organe sautant 6. Selon une première variante, le ressort-spiral 8 comprend à son extrémité destinée à être fixée sur l'organe sautant 6, une encoche de fixation 9 dans laquelle est inséré un tenon de maintien 11 prévu sur l'organe sautant. Selon une deuxième variante représentée sur la figure 7, le ressort-spiral 8 comprend à son extrémité destinée à être fixée sur l'organe sautant 6, une double encoche de fixation 32 présentant deux logements ou encoches. L'organe sautant 6 est pourvu de deux tenons de maintien 34, chaque tenon de maintien 34 étant destiné à être inséré dans l'un des logements de la double encoche de fixation 32. Les tenons de maintien 34 sont agencés pour limiter le jeu axial. Plus particulièrement, chaque tenon de maintien 34 comporte une gorge autour de laquelle se positionne chaque encoche. Ainsi, la double encoche de fixation permet de garantir que la planéité du ressort-spiral 8 est conservée lors du fonctionnement du mécanisme. L'organe sautant 6 est une roue comprenant 30 dents et faisant un tour en 60 secondes.The dead second mechanism also comprises a jumping member 6, such as a wheel, secured to a dead second indicator, such as a needle (not shown). The jumping member 6 is mounted loosely on the axis of the second wheel 1, so that the jumping member 6 is coaxial with the second wheel 1 and not integral with the latter. Jumping organ 6 is elastically connected to the second wheel 1 by means of a spiral spring 8, which is on the one hand driven on the second wheel 1 and secondly fixed on the jumping member 6. According to a first variant, the spring -spiral 8 comprises at its end intended to be fixed on the jumping member 6, a fixing notch 9 in which is inserted a holding pin 11 provided on the jumping member. According to a second variant represented on the figure 7 , the spiral spring 8 comprises at its end intended to be fixed on the jumper member 6, a double fixing notch 32 having two housings or notches. The jumping member 6 is provided with two holding lugs 34, each holding lug 34 being intended to be inserted into one of the housings of the double fixing notch 32. The holding lugs 34 are arranged to limit the axial clearance. . More particularly, each holding pin 34 has a groove around which is positioned each notch. Thus, the double fastening notch ensures that the flatness of the spiral spring 8 is retained during operation of the mechanism. The jumping member 6 is a wheel comprising 30 teeth and making a turn in 60 seconds.

Le mécanisme de seconde morte comprend également un mobile de came de seconde morte formé d'une roue entraineuse de came 10 et d'une came de seconde morte 12, solidaire de ladite roue entraineuse de came 10. La roue entraineuse de came 10 est agencée pour coopérer avec le pignon d'échappement 2. Plus particulièrement, la roue entraineuse de came 10 est en prise directe avec le pignon d'échappement 2.The dead second mechanism also comprises a dead second cam mobile formed of a cam drive wheel 10 and a second dead cam 12, integral with said cam drive wheel 10. The cam drive wheel 10 is arranged to cooperate with the escape pinion 2. More particularly, the cam drive wheel 10 is in direct contact with the escape pinion 2.

Selon l'invention, la roue de seconde 1 et la roue entraineuse de came 10 sont montées pivotantes sur le bâti du mouvement de manière à présenter des axes de pivotement distincts, de sorte que la came de seconde morte 12 et l'organe sautant 6 (ou la roue de seconde 1) ne sont pas coaxiaux.According to the invention, the second wheel 1 and the cam drive wheel 10 are pivotally mounted on the frame of the movement so as to have separate pivot axes, so that the dead second cam 12 and the jumping member 6 (or the second wheel 1) are not coaxial.

De plus, la roue de seconde 1 et la roue entraineuse de came 10 sont reliées cinématiquement par un rouage intermédiaire, et plus particulièrement un mobile intermédiaire comprenant un pignon intermédiaire 14 engrenant avec la roue de seconde 1 et une roue intermédiaire 16, solidaire dudit pignon intermédiaire 14, et engrenant avec la roue entraineuse de came 10. Ainsi, la chaine cinématique principale du mouvement va de la roue de seconde 1 au pignon d'échappement 2 en passant successivement par le rouage intermédiaire et la roue entraineuse de came 10, sans prise directe entre le pignon d'entrainement et la roue de seconde. Selon un mode de réalisation préféré, les dimensions et le nombre de dents du mobile intermédiaire sont prévus de telle sorte que la roue entraineuse de came 10 et la came de seconde morte 12 effectuent un tour par 20 secondes, soit 3 tours par minutes, la roue entraineuse de came 10 comprenant 66 dents et la came de seconde morte 12 comprenant 10 dents 18. Il est bien évident que la vitesse de la roue entraineuse de came et de la came de seconde morte, ainsi que le nombre de dents peuvent être modifiés sans sortir du cadre de la présente invention. On pourra choisir par exemple une période de 16 secondes, avec une came de seconde morte comprenant 8 dents.In addition, the second wheel 1 and the cam drive wheel 10 are kinematically connected by an intermediate wheel, and more particularly an intermediate mobile comprising an intermediate gear 14 meshing with the second wheel 1 and an intermediate wheel 16, integral with said intermediate gear 14, and meshing with the driving cam wheel 10. Thus, the main kinematic chain of the movement goes from the wheel from second 1 to the escape gear 2 passing successively by the intermediate gear and the cam drive wheel 10, without a direct connection between the drive pinion and the second wheel. According to a preferred embodiment, the dimensions and the number of teeth of the intermediate mobile are provided so that the cam drive wheel 10 and the dead second cam 12 perform one revolution per 20 seconds, ie 3 revolutions per minute, the cam driving wheel 10 comprising 66 teeth and the dead second cam 12 comprising 10 teeth 18. It is obvious that the speed of the cam driving wheel and the dead second cam, as well as the number of teeth can be modified without departing from the scope of the present invention. We can choose for example a period of 16 seconds, with a second dead cam with 8 teeth.

Le mécanisme de seconde morte comprend également une ancre de seconde morte 20 montée pivotante en un point de pivotement A sur le bâti du mouvement, et commandée par la came de seconde morte 12 pour libérer et faire sauter l'organe sautant 6 une fois par seconde. L'organe sautant 6 constitue ainsi une roue d'échappement de seconde morte.The dead second mechanism also includes a second dead anchor 20 pivotally mounted at a pivot point A on the movement frame, and controlled by the second dead cam 12 to release and blow the jumping member 6 once per second. . The jumping member 6 thus constitutes a dead second escape wheel.

Conformément à l'invention, l'ancre de seconde morte 20 comporte quatre bras distincts 20a, 20b, 20c et 20d. L'extrémité de chacun des bras fait fonction de palette. Dans la suite de la description, le terme « palette » est utilisé pour désigner l'extrémité d'un bras 20a, 20b, 20c et 20d, la palette formant donc une seule pièce avec le bras correspondant. D'une manière avantageuse, l'ancre de seconde morte 20 est monobloc et réalisée par LIGA. Le bras supérieur 20a et le bras inférieur 20b constituent des palpeurs supérieur et inférieur agencés pour coopérer avec la came de seconde morte 12. Le bras supérieur 20c et le bras inférieur 20d constituent des bras d'échappement supérieur et inférieur agencés pour successivement bloquer et libérer, une fois par seconde, l'organe sautant 6 en alternance. Les quatre bras 20a, 20b, 20c et 20d sont positionnés par rapport au point de pivotement A de manière à former sensiblement un X, l'extrémité de chaque bras étant courbée pour pouvoir coopérer soit avec la came de seconde morte 12 soit avec l'organe sautant 6. Les bras 20a, 20b, 20c et 20d travaillent en opposition par rapport au point de pivotement A. Par exemple, comme le montre la figure 1, le bras palpeur supérieur 20a est positionné pour être commandé par le profil de la dent 18 de la came de seconde morte 12 tandis que le bras d'échappement opposé par rapport au point de pivotement A, à savoir le bras d'échappement inférieur 20d, est positionné pour libérer l'organe sautant 6.According to the invention, the dead second anchor 20 comprises four separate arms 20a, 20b, 20c and 20d. The end of each arm acts as a pallet. In the following description, the term "pallet" is used to designate the end of an arm 20a, 20b, 20c and 20d, the pallet thus forming a single piece with the corresponding arm. Advantageously, the second dead anchor 20 is monobloc and made by LIGA. The upper arm 20a and the lower arm 20b constitute upper and lower probes arranged to cooperate with the cam of second dead 12. The upper arm 20c and the lower arm 20d are upper and lower exhaust arms arranged to successively block and release, once a second, the jumping member 6 alternately. The four arms 20a, 20b, 20c and 20d are positioned relative to the pivot point A so as to form substantially an X, the end of each arm being bent to cooperate with either the dead second cam 12 or with the Jumping member 6. The arms 20a, 20b, 20c and 20d work in opposition to the pivot point A. For example, as shown in FIG. figure 1 the upper feeler arm 20a is positioned to be controlled by the tooth profile 18 of the dead second cam 12 while the exhaust arm opposite from the pivot point A, namely the lower exhaust arm 20d. , is positioned to release the jumping member 6.

Chaque dent 18 de la came de seconde morte 12 présente un profil défini par une rampe avant 18a, partie fonctionnelle de la dent sur laquelle l'extrémité ou la palette des bras palpeurs 20a, 20b frotte, ainsi qu'un revers 18b. D'une manière avantageuse, la fréquence du balancier est choisie à 3 Hz (soit 6 alternances par seconde) de sorte que chaque rampe avant 18a peut être décomposée en six pas, chaque pas correspondant à un angle de rotation de 3°de la came de seconde morte. Il est bien évident qu'une autre fréquence pourra être choisie. Un déplacement le long de la rampe avant 18a d'une dent 18 correspondant donc à un angle de rotation de 18° de la came de seconde morte. Afin d'avoir un saut précis, la rampe avant 18a de chaque dent 18 présente une pente qui est plus élevée sur les trois derniers pas correspondant à un angle de rotation de la came de seconde morte compris entre 9° et 18°, soit au moment proche du saut, que sur les trois premiers pas correspondant à un angle de rotation de la came de seconde morte compris entre 0° et 9°. Comme le montre plus précisément la figure 5, en déterminant qu'à l'origine de la dent, pour un angle de 0° la hauteur est égale à 0, et que la hauteur totale de la dent h correspond à un angle de rotation de 18° de la came de seconde morte, la hauteur a de la dent correspondant au troisième pas, soit un angle de rotation de 9° de la came de seconde morte, est comprise entre 10% et 15% de la hauteur h, et la hauteur b de la dent correspondant au cinquième pas, soit un angle de rotation de 15° de la came de seconde morte, est comprise entre 55% et 60% de la hauteur h.Each tooth 18 of the dead second cam 12 has a profile defined by a front ramp 18a, the functional portion of the tooth on which the end or the pallet of the feeler arms 20a, 20b rubs, and a reverse 18b. Advantageously, the frequency of the balance is chosen at 3 Hz (or 6 alternations per second) so that each front ramp 18a can be decomposed into six steps, each step corresponding to a rotation angle of 3 ° of the cam second dead. It is obvious that another frequency can be chosen. A displacement along the front ramp 18a of a tooth 18 corresponding to a rotation angle of 18 ° of the second dead cam. In order to have a precise jump, the front ramp 18a of each tooth 18 has a slope which is higher on the last three steps corresponding to a rotation angle of the second dead cam between 9 ° and 18 °, ie at moment close to the jump, that on the first three steps corresponding to an angle of rotation of the dead second cam between 0 ° and 9 °. As shown more specifically figure 5 , by determining that at the origin of the tooth, for an angle of 0 ° the height is equal to 0, and that the total height of the tooth h corresponds to an angle of rotation of 18 ° of the dead second cam , the height is of the tooth corresponding to the third step, ie a rotation angle of 9 ° of the dead second cam, is between 10% and 15% of the height h, and the height b of the tooth corresponding to the fifth pitch, an angle of rotation 15 ° of the dead second cam, is between 55% and 60% of the height h.

Le profil du revers 18b permet d'éviter le saut prématuré de l'ancre de seconde morte. Ce profil est la résultante du profil de la rampe avant 18a, de manière à ce que, lorsque la palette de l'un des bras palpeurs est en contact avec la rampe avant 18a d'une dent 18 de la came de seconde morte 12, un jeu constant est conservé entre la came de seconde morte 12 et la palette, passive, de l'autre bras palpeur (c'est-à-dire la palette du bras palpeur qui n'est pas au contact de la rampe avant d'une dent).The profile of the reverse 18b avoids the premature jump of the second dead anchor. This profile is the result of the profile of the front ramp 18a, so that when the pallet of one of the feeler arms is in contact with the front ramp 18a of a tooth 18 of the dead second cam 12, a constant clearance is maintained between the dead second cam 12 and the passive pallet of the other probe arm (that is to say the pallet of the probe arm which is not in contact with the ramp before a tooth).

En outre, il est prévu un mécanisme de sécurisation de la position relative de la roue de seconde 1 et de l'organe sautant 6 afin d'assurer un indexage permanent de la roue de seconde 1 et de l'organe sautant 6, y compris lorsque le mécanisme d'entrainement de l'organe sautant s'est arrêté suite à l'arrêt du mouvement. En référence à la figure 4, ledit mécanisme de sécurisation de la position relative de la roue de seconde 1 et de l'organe sautant 6 comprend une première goupille 30 et une seconde goupille 36 chassées sur la roue de seconde 1. Lesdites goupilles 30 et 36 sont représentées uniquement sur la figure 4 pour simplifier les dessins. De plus, l'organe sautant 6 est une roue dentée présentant quatre zones évidées dont les bords forment quatre bras de séparation 6a, 6b, 6c, 6d. Les goupilles 30 et 36 sont positionnées sur la roue de seconde 1 de part et d'autre de l'un des bras de séparation 6a. Plus particulièrement, la première goupille 30 est positionnée de manière à être à l'avant du bras de séparation 6a de l'organe sautant 6 lorsque la roue de seconde 1 et l'organe sautant 6 tournent dans le même sens, notamment lors du fonctionnement normal du mécanisme. Lorsque la roue de seconde 1 tourne dans un sens opposé à celui de l'organe sautant 6, notamment lors de la mise à l'heure du mouvement, la première goupille 30, solidaire de la roue de seconde 1, vient s'appuyer sur le bras de séparation 6a de l'organe sautant 6, le bras de séparation 6a constituant alors une butée pour la première goupille 30. La première goupille 30, continuant son déplacement avec la roue de seconde 1, entraine le bras de séparation 6a et donc l'organe sautant 6 dans son déplacement, de sorte que la roue de seconde 1 et l'organe sautant 6 reculent ensemble et restent indexés, notamment lors de la mise à l'heure.In addition, there is provided a mechanism for securing the relative position of the second wheel 1 and the jumping member 6 to ensure permanent indexing of the second wheel 1 and the jumping member 6, including when the driving mechanism of the jumping member has stopped following the cessation of movement. With reference to the figure 4 , said mechanism for securing the relative position of the second wheel 1 and the jumper member 6 comprises a first pin 30 and a second pin 36 driven on the second wheel 1. Said pins 30 and 36 are shown only on the figure 4 to simplify the drawings. In addition, the jumping member 6 is a toothed wheel having four recessed areas whose edges form four separation arms 6a, 6b, 6c, 6d. The pins 30 and 36 are positioned on the second wheel 1 on either side of one of the separation arms 6a. More particularly, the first pin 30 is positioned so as to be in front of the separation arm 6a of the jumping member 6 when the second wheel 1 and the jumping member 6 rotate in the same direction, especially during operation. normal mechanism. When the second wheel 1 rotates in a direction opposite to that of the jumping member 6, especially when the setting of the time of the movement, the first pin 30, secured to the second wheel 1, is supported on the separation arm 6a of the jumping member 6, the separation arm 6a then constituting a stop for the first pin 30. The first pin 30, continuing its movement with the second wheel 1, drives the separation arm 6a and thus the jumping member 6 in its displacement, so that the second wheel 1 and the jumping member 6 recoil together and remain indexed, especially when setting the time.

La seconde goupille 36 est positionnée de manière à être à l'arrière du bras de séparation 6a de l'organe sautant 6 lorsque la roue de seconde 1 et l'organe sautant 6 tournent dans le même sens, notamment lors du fonctionnement normal du mécanisme. Une marge d'au moins un pas, et de préférence égale à un pas, est prévue. Lorsque l'organe sautant 6 est arrêté, par exemple lors de l'aiguillage, la seconde goupille 36, solidaire de la roue de seconde 1, en se déplaçant dans le sens normal, vient s'appuyer sur le bras de séparation 6a de l'organe sautant 6, le bras de séparation 6a constituant alors une butée pour la seconde goupille 36. La seconde goupille 36 bute contre l'organe sautant 6 arrêté, de sorte que la roue de seconde 1 s'arrête et en conséquence le reste du mécanisme. Ainsi, la roue de seconde 1 et l'organe sautant 6 sont tous les deux arrêtés et restent indexés, notamment lors de l'aiguillage.The second pin 36 is positioned so as to be at the rear of the separation arm 6a of the jumping member 6 when the second wheel 1 and the jumping member 6 rotate in the same direction, in particular during the normal operation of the mechanism . A margin of at least one step, and preferably equal to one step, is provided. When the jumping member 6 is stopped, for example during the switching, the second pin 36, integral with the second wheel 1, moving in the normal direction, is supported on the separation arm 6a of the jumping member 6, the separating arm 6a then constituting a stop for the second pin 36. The second pin 36 abuts against the jumping member 6 stopped, so that the second wheel 1 stops and consequently the rest of the mechanism. Thus, the second wheel 1 and the jumping member 6 are both stopped and remain indexed, especially when switching.

Ainsi, la position relative de la roue de seconde 1 et de l'organe sautant 6 est sécurisée, de sorte qu'il n'y a pas de perte d'armage sur le ressort-spiral 8.Thus, the relative position of the second wheel 1 and the jumping member 6 is secured, so that there is no loss of arming on the spiral spring 8.

En référence à la figure 6, une autre variante du mécanisme de sécurisation est représentée. Selon cette variante, les premiers et seconds moyens d'appui comprennent un excentrique 38, 40 en lieu et place de la première goupille 30 et de la seconde goupille 36 respectivement, leur fonctionnement étant similaire. L'avantage des excentriques 38 et 40 par rapport aux goupilles 30, 36, est que l'horloger peut les déplacer et les positionner pour régler le jeu entre les deux excentriques 38, 40 et le bras de séparation 6a de l'organe sautant 6. Cela permet de moins dépendre des tolérances de fabrication.With reference to the figure 6 another variant of the securing mechanism is shown. According to this variant, the first and second support means comprise an eccentric 38, 40 in place of the first pin 30 and the second pin 36 respectively, their operation being similar. The advantage of the eccentrics 38 and 40 with respect to the pins 30, 36 is that the watchmaker can move them and position to adjust the clearance between the two eccentric 38, 40 and the separation arm 6a of the jumping member 6. This allows less depend on manufacturing tolerances.

Selon une autre variante de réalisation non représentée, les premiers moyens d'appui sont positionnés de manière à être à l'avant de l'un des bras de séparation de l'organe sautant 6 lorsque la roue de seconde 1 et l'organe sautant 6 tournent dans le même sens, et les seconds moyens d'appui sont positionnés de manière à être à l'arrière d'un autre bras de séparation de l'organe sautant 6 lorsque la roue de seconde 1 et l'organe sautant 6 tournent dans le même sens. Ainsi, l'un des bras de séparation de l'organe sautant 6 constitue la première butée sur laquelle les premiers moyens d'appui sont susceptibles de s'appuyer et l'autre bras de séparation de l'organe sautant 6 constitue la seconde butée sur laquelle les seconds moyens d'appui sont susceptibles de s'appuyer.According to another variant embodiment not shown, the first support means are positioned so as to be in front of one of the separation arms of the jumping member 6 when the second wheel 1 and the jumping member 6 rotate in the same direction, and the second support means are positioned to be at the rear of another separation arm of the jumping member 6 when the second wheel 1 and the jumping member 6 rotate in the same way. Thus, one of the separation arms of the jumping member 6 constitutes the first stop on which the first support means are able to rest and the other separation arm of the jumping member 6 constitutes the second stop on which the second support means are able to rely.

Dans une autre variante de réalisation non représentée, les première et seconde butées ne sont pas constituées par les bras de séparation de l'organe sautant mais sont des pièces chassées sur l'organe sautant 6 et disposées de manière à pouvoir entrer en contact avec leurs moyens d'appui respectifs, notamment des goupilles ou des excentriques, prévus sur la roue d'entrainement.In another variant embodiment not shown, the first and second stops are not constituted by the separating arms of the jumping member but are parts driven on the jumping member 6 and arranged so as to be able to come into contact with their respective bearing means, in particular pins or eccentrics, provided on the drive wheel.

Le fonctionnement du mécanisme de seconde morte est le suivant : en référence aux figures 1 à 5, la roue de seconde 1 entraine le pignon intermédiaire 14 et donc la roue intermédiaire 16, qui entraine à son tour la roue entraineuse de came 10 et donc la came de seconde morte 12. Ladite came de seconde morte 12, en tournant, permet à la rampe avant 18a d'une dent 18 d'agir sur la palette du bras palpeur supérieur 20a de l'ancre de seconde morte 20, de sorte que ladite ancre 20 bascule autour de son point de pivotement A pour faire sortir, à l'opposé, la palette du bras d'échappement inférieur 20d de l'ancre de seconde morte 20 de la denture de l'organe sautant 6.The operation of the second dead mechanism is as follows: Figures 1 to 5 , the second wheel 1 drives the intermediate gear 14 and thus the intermediate wheel 16, which in turn drives the cam drive wheel 10 and thus the dead second cam 12. Said dead second cam 12, turning, allows the front ramp 18a of a tooth 18 to act on the pallet of the upper probe arm 20a of the dead second anchor 20, so that said anchor 20 tilts around its pivot point A to exit, to the opposite, the pallet of the lower exhaust arm 20d of the second dead anchor 20 of the toothing of the jumping member 6.

Plus précisément, entre le pas 0, représenté sur la figure 1, et le cinquième pas de la rampe avant 18a de la dent concernée (soit pour un angle de rotation de la came de seconde morte 12 de 15°, cf. figure 5), la palette du bras d'échappement inférieur 20d ne sort pas de la denture de l'organe sautant 6, quel que soit le rattrapage de jeu. Le profil asymétrique de chaque dent 18 de la came de seconde morte 12 est tel que la levée de l'ancre se fait progressivement avec la palette du bras palpeur supérieur 20a pendant que la palette du bras palpeur inférieur 20b descend sans toucher la came de seconde morte 12.More precisely, between step 0, represented on the figure 1 , and the fifth step of the ramp before 18a of the tooth concerned (ie for an angle of rotation of the dead second cam 12 of 15 °, cf. figure 5 ), the pallet of the lower exhaust arm 20d does not come out of the toothing of the jumping member 6, regardless of the clearance clearance. The asymmetric profile of each tooth 18 of the second dead cam 12 is such that the raising of the anchor is done progressively with the pallet of the upper probe arm 20a while the pallet of the lower probe arm 20b descends without touching the dead second cam 12.

Lorsque la palette du bras palpeur supérieur 20a arrive au cinquième pas de la rampe avant 18a, comme le montre la figure 2, l'organe sautant 6 n'a pas encore sauté, et est toujours bloqué par la palette du bras d'échappement inférieur 20d. Une fois la palette du bras palpeur supérieur 20a arrivée au cinquième pas de la rampe avant 18a, si l'ancre de seconde morte 20 subit un rattrapage de jeu suite à un choc par exemple, la palette du bras palpeur inférieur 20b se positionne au contact du revers 18b de la dent 18 concernée de la came de seconde morte 12, comme le montre la figure 3. Même dans cette configuration, l'organe sautant 6 n'a pas sauté, mais reste à la limite de sauter. L'organe sautant 6 saute lorsque la palette du bras palpeur supérieur 20a se déplace entre le cinquième et le sixième pas. Lorsque la palette du bras palpeur supérieur 20a arrive au sixième pas de la rampe avant 18a, comme le montre la figure 4, l'organe sautant 6 a sauté. L'ancre de seconde morte ayant basculé, la palette du bras d'échappement inférieur 20d s'est dégagée de l'organe sautant 6 et l'a libéré. L'organe sautant 6, rappelé par le ressort spiral 8 fixé sur la roue de seconde 1, tourne de 6°, soit un avancement ou un saut d'une seconde de l'indicateur de seconde morte. L'organe sautant est ensuite de nouveau bloqué par cette fois la palette du bras d'échappement supérieur 20c, sur laquelle il est maintenu en appui grâce au ressort spiral 8, comme le montre la figure 4. C'est la palette du bras palpeur inférieur 20b, à l'opposé par rapport au point de pivotement A, qui va entrer au contact de la rampe avant 18a d'une dent de la came de seconde morte 12, pour faire basculer l'ancre de seconde morte 20 dans l'autre sens et de nouveau libérer l'organe sautant. Ainsi, le mouvement de l'ancre de seconde morte est un mouvement alternatif qui permet de libérer, dent après dent, l'organe sautant 6, une fois avec la palette du bras d'échappement supérieur 20c, puis avec la palette du bras d'échappement inférieur 20d, de manière successive et alternée. En conséquence, l'indicateur de seconde morte avance par incrément de 1 seconde.When the pallet of the upper arm 20a reaches the fifth step of the ramp before 18a, as shown in FIG. figure 2 , the jumping member 6 has not yet jumped, and is still blocked by the pallet of the lower exhaust arm 20d. Once the pallet of the upper probe arm 20a has arrived at the fifth step of the ramp before 18a, if the dead second anchor 20 undergoes a catch of play following a shock for example, the pallet of the lower probe arm 20b is positioned at the contact 18b of the corresponding tooth 18 of the dead second cam 12, as shown in FIG. figure 3 . Even in this configuration, the jumping organ 6 has not jumped, but remains at the limit of jumping. The jumping member 6 jumps when the pallet of the upper feeler arm 20a moves between the fifth and sixth steps. When the pallet of the upper probe arm 20a arrives at the sixth step of the ramp before 18a, as shown in FIG. figure 4 the jumping organ 6 has jumped. With the dead second anchor tilted, the lower exhaust arm pad 20d disengaged from the jumping member 6 and released it. The jumping member 6, recalled by the spiral spring 8 attached to the second wheel 1, rotates 6 °, either a progress or a jump of one second of the second dead indicator. The jumping member is then again locked this time the pallet of the upper exhaust arm 20c, on which it is held in support by the spiral spring 8, as shown in FIG. figure 4 . This is the pallet of the lower probe arm 20b, opposite to the pivot point A, which will come into contact with the ramp before 18a of a tooth of the dead second cam 12, to tilt the second dead anchor 20 in the other direction and again release the jumping member. Thus, the movement of the dead second anchor is a reciprocating movement that releases, tooth by tooth, the jumping member 6, once with the pallet of the upper exhaust arm 20c, then with the pallet of the arm lower exhaust 20d, successively and alternately. As a result, the dead second indicator advances in increments of 1 second.

Le mécanisme de seconde morte de l'invention permet d'avoir des sauts précis chaque seconde avec une moindre consommation d'énergie. En effet, le mécanisme de l'invention est alimenté par la même source d'énergie que le rouage de finissage. Une deuxième source d'énergie n'est pas nécessaire. Par ailleurs, la disposition sur des axes distincts de l'organe sautant et de la came de seconde morte permet de prévoir des formes optimisées pour les palettes des bras d'échappement d'une part et pour les palettes des bras palpeurs d'autre part, en liaison avec des formes optimisées des dents de la came de seconde morte. La consommation d'énergie due au ressort spiral entre la roue de seconde et l'organe sautant est presque nulle. Notamment, plus la pente de la rampe avant des dents de la came de seconde morte sera élevée sur les trois derniers pas de la dent, plus le saut sera marqué et de ce fait précis. Une pente plus faible sur les trois premiers pas de la dent fait que le pas angulaire de l'ancre de seconde morte est relativement faible sur cette période. La consommation de couple est donc faible. La pente sur les trois derniers pas est au contraire plus importante mais doit toutefois restée mesurée afin d'éviter une surconsommation de couple sur le mobile de came de seconde morte. De ce fait, le pas angulaire de l'ancre de seconde morte est plus élevé sur les trois derniers pas, ce qui permet l'exécution du saut sur une plus grande plage de mesure, et d'augmenter en conséquence la précision du saut. De plus, l'utilisation d'une came de seconde morte présentant seulement 10 dents permet d'obtenir des pas angulaires plus grands, et donc des sauts moins sensibles aux imperfections de la came de seconde morte.The second dead mechanism of the invention allows for precise jumps every second with less energy consumption. Indeed, the mechanism of the invention is powered by the same source of energy as the finishing gear. A second source of energy is not necessary. Furthermore, the arrangement on separate axes of the jumper member and the dead second cam provides optimized shapes for the vanes of the exhaust arms on the one hand and for the pallets of the feeler arms on the other hand , in connection with optimized shapes of the teeth of the dead second cam. The energy consumption due to the spiral spring between the second wheel and the jumping member is almost zero. In particular, the higher the slope of the front ramp of the teeth of the second dead cam will be high on the last three steps of the tooth, the more the jump will be marked and therefore accurate. A lower slope on the first three steps of the tooth makes the angular pitch of the second dead anchor relatively low over this period. The torque consumption is therefore low. The slope on the last three steps is on the contrary more important but must however remain measured in order to avoid over-consumption of torque on the mobile cam second dead. As a result, the angular pitch of the dead second anchor is higher on the last three steps, which allows the jump to be performed over a larger measurement range, and consequently increases the jump accuracy. In addition, the use of a dead second cam with only 10 teeth makes it possible to obtain larger angular steps, and therefore less sensitive jumps to the imperfections of the dead second cam.

Toutes les pièces du mécanisme de seconde morte directement liées à l'indicateur de seconde morte sont évidées, ceci afin de les alléger au maximum et de réduire l'inertie ainsi que la consommation de couple. De plus, ces évidements permettent d'équilibrer les pièces, afin d'obtenir un balourd proche de zéro.All parts of the second dead mechanism directly related to the dead second indicator are hollowed out, in order to lighten them to the maximum and reduce inertia as well as torque consumption. Moreover, these recesses make it possible to balance the parts, in order to obtain an imbalance close to zero.

Par ailleurs, le rayon formant le flanc de la denture de l'organe sautant est choisi pour être concentrique et égal à celui de l'ancre de seconde morte avec lequel il est en contact. De ce fait, lorsque l'ancre de seconde morte bascule, l'organe sautant ne bouge pas, ce qui assure la stabilité de l'indicateur de seconde morte.Furthermore, the radius forming the flank of the toothing of the jumping member is chosen to be concentric and equal to that of the second dead anchor with which it is in contact. As a result, when the dead second anchor tilts, the jumping member does not move, which ensures the stability of the second dead indicator.

Enfin, la disposition sur des axes distincts de l'organe sautant et de la came de seconde morte permet de ne pas additionner un grand nombre de pièces sur un même axe et donc de limiter l'accumulation des tolérances et le désaxage des mobiles, contrairement aux mécanismes coaxiaux de l'art antérieur. La précision sur l'axe de l'organe sautant est donc plus importante tout en simplifiant l'assemblage des pièces.Finally, the arrangement on separate axes of the jumping member and the second dead cam makes it possible not to add a large number of parts on the same axis and therefore to limit the accumulation of tolerances and the misalignment of the mobiles, unlike to the coaxial mechanisms of the prior art. The precision on the axis of the jumping member is therefore greater while simplifying the assembly of parts.

Il est bien évident que le mécanisme de seconde morte décrit ci-dessus peut être adapté à une autre unité de temps que la seconde. Ainsi, le mécanisme d'entrainement d'un organe sautant selon l'invention peut être adapté à l'affichage de n'importe quelle unité de temps : seconde, minute, dizaine de seconde, dizaine de minute, etc. Pour ce faire, l'homme du métier sait adapter en conséquence le nombre de dents sur la came ainsi que sur l'organe sautant, ainsi que les rapports d'engrenage dans le rouage de finissage.It is obvious that the second dead mechanism described above can be adapted to another unit of time than the second. Thus, the drive mechanism of a jumping member according to the invention can be adapted to the display of any unit of time: second, minute, ten seconds, ten minutes, etc. To do this, the skilled person knows how to adapt accordingly the number of teeth on the cam and the jumping member, as well as the gear ratios in the gear train.

Claims (15)

Mécanisme d'entrainement d'un organe sautant dans une pièce d'horlogerie comprenant une roue d'entrainement (1), un indicateur d'une unité de temps, un organe sautant (6) solidaire dudit indicateur et coaxial à ladite roue d'entrainement (1) à laquelle ledit organe sautant (6) est accouplé par un ressort (8), une came (12) agencée pour commander une ancre (20), ladite came (12) présentant un profil agencé pour faire basculer l'ancre (20) selon un mouvement oscillant de manière à libérer l'organe sautant (6) une fois par unité de temps, caractérisé en ce que la came (12) et l'organe sautant (6) présentent des axes de pivotement distincts, ledit mécanisme d'entrainement comprenant en outre un rouage intermédiaire liant cinématiquement la roue d'entrainement (1) à la came (12), et en ce que l'ancre (20) présente quatre bras (20a, 20b, 20c, 20d) distincts, deux (20a, 20b) des quatre bras constituant des palpeurs agencés pour coopérer avec la came (12) et les deux autres bras (20c, 20d) constituant des bras d'échappement agencés pour successivement bloquer et libérer une fois par unité de temps l'organe sautant (6) en alternance.Mechanism for driving a jumping member in a timepiece comprising a driving wheel (1), an indicator of a time unit, a jumping member (6) integral with said indicator and coaxial with said wheel of drive (1) to which said jumping member (6) is coupled by a spring (8), a cam (12) arranged to control an anchor (20), said cam (12) having a profile arranged to tilt the anchor (20) according to an oscillating movement so as to release the jumping member (6) once per unit of time, characterized in that the cam (12) and the jumping member (6) have distinct pivot axes, said driving mechanism further comprising an intermediate gear kinematically connecting the drive wheel (1) to the cam (12), and in that the anchor (20) has four arms (20a, 20b, 20c, 20d) separate , two (20a, 20b) of the four arms constituting probes arranged to cooperate with the cam (12) and the two aut res bras (20c, 20d) constituting exhaust arms arranged to successively block and release once per unit time the jumping member (6) alternately. Mécanisme selon la revendication 1, caractérisé en ce que le rouage intermédiaire comprend un mobile intermédiaire formé d'un pignon intermédiaire (14) agencé pour coopérer avec la roue d'entrainement (1) et d'une roue intermédiaire (16) agencée pour coopérer avec une roue entraineuse de came (10) solidaire de la came (12).Mechanism according to claim 1, characterized in that the intermediate gear comprises an intermediate mobile formed of an intermediate gear (14) arranged to cooperate with the drive wheel (1) and an intermediate wheel (16) arranged to cooperate with a cam drive wheel (10) integral with the cam (12). Mécanisme selon l'une quelconque des revendications précédentes, caractérisé en ce que le rouage intermédiaire est dimensionné pour que la came (12) comprenne moins de trente dents (18), chaque dent (18) présentant une rampe avant (18a), et effectue plus d'un tour par minute.Mechanism according to any one of the preceding claims, characterized in that the intermediate gear is sized so that the cam (12) comprises less than thirty teeth (18), each tooth (18) having a front ramp (18a), and performs more than one turn per minute. Mécanisme selon l'une quelconque des revendications précédentes, caractérisé en ce que, l'unité de temps étant la seconde, la roue d'entrainement (1) étant agencée pour faire un tour en 60 secondes, et l'indicateur étant un indicateur de seconde morte, la came (12) comprend dix dents (18) et est agencée pour effectuer trois tours par minute, chaque dent (18) présentant une rampe avant (18a) se décomposant en six pas.Mechanism according to any one of the preceding claims, characterized in that , the unit of time being the second, the drive wheel (1) being arranged to turn in 60 seconds, and the indicator being an indicator of second dead, the cam (12) comprises ten teeth (18) and is arranged to perform three revolutions per minute, each tooth (18) having a front ramp (18a) decomposing in six steps. Mécanisme selon la revendication 3 ou 4, caractérisé en ce que la rampe avant (18a) de chaque dent (18) de la came (12) présente, sur les trois derniers pas de la dent (18), une pente supérieure à la pente de la rampe avant (18a) sur les trois premiers pas de la dent (18).Mechanism according to claim 3 or 4, characterized in that the front ramp (18a) of each tooth (18) of the cam (12) has, on the last three steps of the tooth (18), a slope greater than the slope the front ramp (18a) on the first three steps of the tooth (18). Mécanisme selon l'une quelconque des revendications précédentes, caractérisé en ce que les quatre bras (20a, 20b, 20c, 20d) de l'ancre (20) sont disposés de manière à former sensiblement un X, le bras palpeur (20a, 20b) positionné pour coopérer avec la came (12) étant disposé de manière opposée par rapport au point de pivotement de l'ancre (20) au bras d'échappement (20c, 20d) positionné pour libérer l'organe sautant (6).Mechanism according to any one of the preceding claims, characterized in that the four arms (20a, 20b, 20c, 20d) of the anchor (20) are arranged to form substantially an X, the probe arm (20a, 20b ) positioned to cooperate with the cam (12) being oppositely disposed with respect to the pivot point of the anchor (20) to the exhaust arm (20c, 20d) positioned to release the jumping member (6). Mécanisme selon l'une quelconque des revendications précédentes, caractérisé en ce qu'il comprend un mécanisme de sécurisation de la position relative de la roue d'entrainement (1) et de l'organe sautant (6)Mechanism according to any one of the preceding claims, characterized in that it comprises a mechanism for securing the relative position of the drive wheel (1) and the jumping member (6) Mécanisme selon la revendication 7, caractérisé en ce que le mécanisme de sécurisation de la position relative de la roue d'entrainement (1) et de l'organe sautant (6) comprend des premiers moyens d'appui prévus sur la roue d'entrainement (1) et une première butée prévue sur l'organe sautant (6), lesdits premiers moyens d'appui étant agencés pour s'appuyer sur la première butée lorsque la roue d'entrainement (1) et l'organe sautant (6) tournent dans des sens opposés.Mechanism according to claim 7, characterized in that the mechanism for securing the relative position of the drive wheel (1) and the jumping member (6) comprises first support means provided on the drive wheel. (1) and a first stop provided on the jumping member (6), said first support means being arranged to bear on the first stop when the drive wheel (1) and the jumping member (6) turn in opposite directions. Mécanisme selon l'une des revendications 7 et 8, caractérisé en ce que le mécanisme de sécurisation de la position relative de la roue d'entrainement (1) et de l'organe sautant (6) comprend des seconds moyens d'appui prévus sur la roue d'entrainement (1) et une seconde butée prévue sur l'organe sautant (6), lesdits seconds moyens d'appui étant agencés pour s'appuyer sur la seconde butée lorsque l'organe sautant (6) est arrêté.Mechanism according to one of claims 7 and 8, characterized in that the mechanism for securing the relative position of the drive wheel (1) and the jumping member (6) comprises second support means provided on the drive wheel (1) and a second stop provided on the jumping member (6), said second support means being arranged to rest on the second stop when the jumping member (6) is stopped. Mécanisme selon l'une des revendications 7 à 9, caractérisé en ce que les premiers et seconds moyens d'appui comprennent une goupille (30, 36).Mechanism according to one of claims 7 to 9, characterized in that the first and second bearing means comprise a pin (30, 36). Mécanisme selon l'une des revendications 7 à 10, caractérisé en ce que les premiers et seconds moyens d'appui comprennent un excentrique (38, 40).Mechanism according to one of claims 7 to 10, characterized in that the first and second support means comprise an eccentric (38, 40). Mécanisme selon l'une des revendications 7 à 11, caractérisé en ce que l'organe sautant (6) est une roue présentant au moins deux zones évidées séparées par au moins un bras de séparation (6a), et en ce que les premiers et seconds moyens d'appui sont disposés de part et d'autre dudit au moins un bras de séparation (6a), ledit bras de séparation (6a) constituant au moins l'une des première et secondes butées sur lesquelles les premiers et seconds moyens d'appui sont susceptibles de s'appuyer respectivement.Mechanism according to one of claims 7 to 11, characterized in that the jumping member (6) is a wheel having at least two recessed areas separated by at least one separation arm (6a), and in that the first and second support means are arranged on either side of said at least one separation arm (6a), said separation arm (6a) constituting at least one of the first and second stops on which the first and second means of support are likely to be based respectively. Pièce d'horlogerie comprenant un mouvement horloger pourvu d'un rouage de finissage alimenté par une source d'énergie, caractérisée en ce qu'elle comprend un mécanisme d'entrainement d'un organe sautant selon l'une quelconque des revendications 1 à 12.Timepiece comprising a watch movement provided with a finishing gear powered by an energy source, characterized in that it comprises a mechanism for driving a jumping member according to any one of Claims 1 to 12 . Pièce d'horlogerie selon la revendication 13, caractérisée en ce que la roue d'entrainement (1) est alimentée par la source d'énergie du mouvement.Timepiece according to claim 13, characterized in that the drive wheel (1) is powered by the energy source of the movement. Pièce d'horlogerie selon la revendication 13 ou 14, caractérisée en ce que la roue d'entrainement (1) est la roue de seconde du rouage de finissage.Timepiece according to claim 13 or 14, characterized in that the drive wheel (1) is the second wheel of the work train.
EP15196125.7A 2014-12-11 2015-11-24 Drive mechanism of a skipping member Active EP3032349B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
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EP14197490.7A EP3032348A1 (en) 2014-12-11 2014-12-11 Drive mechanism of a skipping member
CH3562015 2015-03-16
EP15196125.7A EP3032349B1 (en) 2014-12-11 2015-11-24 Drive mechanism of a skipping member

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EP3032349A1 true EP3032349A1 (en) 2016-06-15
EP3032349B1 EP3032349B1 (en) 2023-02-22

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US (1) US9429914B2 (en)
EP (1) EP3032349B1 (en)
JP (1) JP6297535B2 (en)
CN (1) CN105700324B (en)
CH (1) CH710477B1 (en)
HK (1) HK1225816B (en)
RU (1) RU2739148C2 (en)

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US10579018B2 (en) 2017-03-30 2020-03-03 Richemont International S.A. Timepiece with digital time display
CH719389A1 (en) * 2022-01-28 2023-08-15 Richemont Int Sa Drive mechanism for a jumping indicator for integration into clocks.

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CN112567298B (en) * 2018-07-19 2022-04-12 沃纳·詹纳 Multi-cam continuous driving escapement
CN112177869B (en) * 2020-09-29 2024-01-30 重庆科技学院 Random environmental energy collecting and stable releasing device for friction nano generator
EP3979007A1 (en) * 2020-10-02 2022-04-06 Montres Breguet S.A. Watch with mechanical movement with force control mechanism
EP4134754A1 (en) * 2021-08-13 2023-02-15 ETA SA Manufacture Horlogère Suisse Inertial mass provided with a flexible inertial element, in particular for timepieces

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CH719389A1 (en) * 2022-01-28 2023-08-15 Richemont Int Sa Drive mechanism for a jumping indicator for integration into clocks.

Also Published As

Publication number Publication date
CH710477A2 (en) 2016-06-15
RU2015153133A3 (en) 2019-05-16
CN105700324A (en) 2016-06-22
JP6297535B2 (en) 2018-03-20
US9429914B2 (en) 2016-08-30
EP3032349B1 (en) 2023-02-22
US20160170374A1 (en) 2016-06-16
RU2015153133A (en) 2017-06-16
JP2016114605A (en) 2016-06-23
HK1225816B (en) 2017-09-15
RU2739148C2 (en) 2020-12-21
CH710477B1 (en) 2024-11-15
CN105700324B (en) 2018-01-02

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