EP3032349B1 - Drive mechanism of a skipping member - Google Patents

Drive mechanism of a skipping member Download PDF

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Publication number
EP3032349B1
EP3032349B1 EP15196125.7A EP15196125A EP3032349B1 EP 3032349 B1 EP3032349 B1 EP 3032349B1 EP 15196125 A EP15196125 A EP 15196125A EP 3032349 B1 EP3032349 B1 EP 3032349B1
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EP
European Patent Office
Prior art keywords
cam
drive wheel
wheel
seconds
jumping
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.)
Active
Application number
EP15196125.7A
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German (de)
French (fr)
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EP3032349A1 (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.)
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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
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    • GPHYSICS
    • G04HOROLOGY
    • G04BMECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00Escapements
    • G04B15/14Component parts or constructional details, e.g. construction of the lever or the escape wheel
    • GPHYSICS
    • G04HOROLOGY
    • G04BMECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B13/00Gearwork
    • G04B13/002Gearwork where rotation in one direction is changed into a stepping movement
    • GPHYSICS
    • G04HOROLOGY
    • G04BMECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00Escapements
    • G04B15/06Free escapements
    • G04B15/08Lever escapements
    • GPHYSICS
    • G04HOROLOGY
    • G04BMECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00Escapements
    • G04B15/10Escapements with constant impulses for the regulating mechanism
    • GPHYSICS
    • G04HOROLOGY
    • G04BMECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B19/00Indicating the time by visual means
    • G04B19/02Back-gearing arrangements between gear train and hands
    • GPHYSICS
    • G04HOROLOGY
    • G04BMECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B13/00Gearwork

Definitions

  • the invention relates to the field of mechanical watchmaking. It relates, more particularly, to a mechanism for driving a jumping member in a timepiece comprising a drive wheel arranged to rotate at 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 according to an oscillating movement so as to release the member jumping once per unit time.
  • the present invention also relates to a timepiece comprising such a mechanism for driving a jumping member.
  • a deadbeat seconds mechanism includes a deadbeat seconds indicator, usually a large hand in the center of the dial, which makes 1 jump per second.
  • Some of these mechanisms are powered by a second energy source, specific to the deadbeat seconds mechanism, in addition to the main energy source, necessary for the movement.
  • the dead seconds cam comprises a large number of teeth (30), involving small angular steps, which makes the jumps very sensitive to imperfections in the dead seconds cam.
  • the same pallet of the deadbeat seconds anchor is used both to cooperate with the deadbeat seconds cam and the seconds wheel.
  • the deadbeat seconds anchor blocks the jumping member under the effect of the force of the coupling spring and friction. These frictions absorb a relatively large power, so that the energy consumption by the deadbeat seconds mechanism is high.
  • the constant force device disclosed in the document EP 2 166 419 A1 which does not include a deadbeat seconds mechanism by means of a jumping member, is on the other hand a timepiece comprising a timepiece movement provided with a going train powered by an energy source and an escapement wheel , comprising a mechanism for driving a jumping member comprising a drive wheel, a jumping member coaxial with said drive wheel to which said jumping member is coupled by a spring, a cam, integral with a drive wheel of cam, arranged to control an anchor, said cam having a profile arranged to tilt the anchor according to an oscillating movement so as to release the jumping member once per unit of time, the cam and the jumping member having axes of separate pivoting mechanisms, said drive mechanism further comprising an intermediate gear train kinematically linking the drive wheel to the cam, and the anchor having four separate arms, two of the four arms constituting feelers rs arranged to cooperate with the cam and the two other arms constituting escapement arms arranged to successively block and release once per unit time the body jumping alternately
  • the object of the invention is in particular to overcome the various drawbacks of the known mechanisms.
  • an object of the invention is to provide a mechanism for driving a jumping member, and in particular a dead seconds mechanism, reliable, making it possible to have precise jumps at each unit of time, and in particular at each second.
  • Another object of the invention is to provide a mechanism for driving a jumping member, and in particular a deadbeat seconds mechanism allowing regular jumps throughout its life.
  • the invention also aims to provide a mechanism for driving a jumping member, and in particular a mechanism for deadbeat seconds, allowing reduced energy consumption, authorizing the use of the same energy source as that of the movement.
  • the present invention relates to a timepiece as defined in appended claim 1.
  • the intermediate gear train may comprise an intermediate wheel set formed of an intermediate pinion arranged to cooperate with the drive wheel and of an intermediate wheel arranged to cooperate with a cam drive wheel integral with the cam.
  • the intermediate gear train can be dimensioned so that the cam comprises less than thirty teeth, each tooth having a forward ramp, and performs more than one revolution per minute.
  • the unit of time is the second, the drive wheel being arranged to complete one revolution in 60 seconds, and the indicator being a dead second indicator, the cam can include ten teeth and be arranged to perform three rotations per minute, each tooth having a forward ramp breaking down into six steps.
  • the front ramp of each tooth of the cam has, over the last three pitches of the tooth, a slope greater than the slope of the front ramp over the first three pitches of the tooth.
  • the four arms of the anchor can be arranged so as to form substantially an X, the feeler arm positioned to cooperate with the cam being arranged opposite with respect to the pivot point of the anchor to the arm escapement positioned to release the jumping organ.
  • 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 press against the first stop and limit the travel 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 press against the second stop and limit the travel of the drive wheel when the jumping member is stopped.
  • said first and second bearing means may comprise a pin.
  • the first and second bearing means may comprise an eccentric.
  • the jumping member can be a wheel having at least two recessed zones 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 abutments on which the first and second bearing means are capable of resting respectively.
  • the drive mechanism of a jumping member according to the invention makes it possible to have precise jumps at each unit of time while allowing reduced energy consumption. In addition, the jumps will be regular, throughout the life of the mechanism.
  • the drive wheel of the deadbeat seconds mechanism can be powered by the energy source of the movement.
  • the drive wheel can be the second wheel of the going train.
  • the following description relates to an embodiment of the invention for which the unit of time is the second.
  • the drive mechanism then constitutes a “dead seconds mechanism”, and will be referred to by this expression below.
  • the deadbeat seconds mechanism is integrated into a mechanical timepiece, comprising a timepiece movement provided with a going train powered by an energy source, such as a barrel.
  • the going train traditionally comprises a second wheel 1, comprising 60 teeth and arranged to complete one revolution in 60 seconds.
  • the movement also traditionally comprises an escape pinion 2 and an escape wheel 3 as well as an escape lever and a balance wheel.
  • the frequency of the balance wheel is advantageously chosen at 3 Hz, as will be understood below.
  • the deadbeat seconds mechanism comprises a drive wheel constituted more specifically here by the seconds wheel 1 of the going train.
  • the deadbeat seconds mechanism also includes a jumping member 6, such as a wheel, integral with a deadbeat seconds indicator, such as a hand (not shown).
  • the jumping member 6 is loosely mounted 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.
  • the 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 onto the second wheel 1 and on the other hand fixed to the jumping member 6.
  • the spring -hairspring 8 comprises at its end intended to be fixed on the jumping member 6, a fixing notch 9 in which is inserted a holding stud 11 provided on the jumping member.
  • the spiral spring 8 comprises at its end intended to be fixed on the jumping member 6, a double fixing notch 32 having two housings or notches.
  • the jumping member 6 is provided with two retaining pins 34, each retaining pin 34 being intended to be inserted into one of the housings of the double fixing notch 32.
  • the retaining pins 34 are arranged to limit the axial play . More particularly, each retaining stud 34 has a groove around which each notch is positioned.
  • the jumping member 6 is a wheel comprising 30 teeth and making one revolution in 60 seconds.
  • the deadbeat second mechanism also comprises a deadbeat second cam mobile formed by a cam driving wheel 10 and a deadbeat second cam 12, integral with said cam driving wheel 10.
  • the cam driving wheel 10 is arranged to cooperate with the escapement pinion 2. More particularly, the cam driving wheel 10 is in direct engagement with the escapement pinion 2.
  • the seconds wheel 1 and the cam driving wheel 10 are pivotally mounted on the frame of the movement so as to have separate pivot axes, so that the dead seconds cam 12 and the jumping member 6 (or second wheel 1) are not coaxial.
  • the second wheel 1 and the cam driving wheel 10 are kinematically connected by an intermediate gear train, and more particularly an intermediate mobile comprising an intermediate pinion 14 meshing with the second wheel 1 and an intermediate wheel 16, integral with said intermediate pinion 14, and meshing with the cam driving wheel 10.
  • an intermediate mobile comprising an intermediate pinion 14 meshing with the second wheel 1 and an intermediate wheel 16, integral with said intermediate pinion 14, and meshing with the cam driving wheel 10.
  • the main kinematic chain of the movement goes from the wheel 1 to the escape pinion 2 passing successively through the intermediate gear train and the cam drive wheel 10, without direct engagement between the drive pinion and the second wheel.
  • the dimensions and the number of teeth of the intermediate wheel set are provided such that the cam drive wheel 10 and the dead seconds cam 12 perform one revolution per 20 seconds, i.e. 3 revolutions per minute, the cam driving wheel 10 comprising 66 teeth and the dead second cam 12 comprising 10 teeth 18.
  • the deadbeat seconds mechanism also comprises a deadbeat seconds anchor 20 pivotally mounted at a pivot point A on the movement frame, and controlled by the deadbeat seconds cam 12 to release and cause the jumping member 6 to jump once per second. .
  • the jumping member 6 thus constitutes a deadbeat seconds escape wheel.
  • deadbeat seconds anchor 20 comprises four distinct arms 20a, 20b, 20c and 20d.
  • the end of each of the arms acts as a pallet.
  • the term “pallet” is used to designate the end of an arm 20a, 20b, 20c and 20d, the pallet therefore forming a single piece with the corresponding arm.
  • deadbeat seconds anchor 20 is made in one piece and made by LIGA.
  • the upper arm 20a and the lower arm 20b constitute upper and lower feelers arranged to cooperate with the cam of deadbeat seconds 12.
  • the upper arm 20c and the lower arm 20d constitute upper and lower escapement arms arranged to successively block and release, once per second, the jumping member 6 alternately.
  • the four arms 20a, 20b, 20c and 20d are positioned with respect to the pivot point A so as to substantially form an X, the end of each arm being curved in order to be able to cooperate either with the dead second cam 12 or with the jumping member 6.
  • the arms 20a, 20b, 20c and 20d work in opposition with respect to the pivot point A.
  • the upper feeler arm 20a is positioned to be controlled by the profile of the tooth 18 of the deadbeat seconds cam 12 while the opposite escapement arm with respect to the pivot point A, namely the lower escapement arm 20d , is positioned to release the jumping member 6.
  • Each tooth 18 of the deadbeat second cam 12 has a profile defined by a front ramp 18a, the functional part of the tooth on which the end or the pallet of the feeler arms 20a, 20b rubs, as well as a reverse 18b.
  • the frequency of the balance is chosen at 3 Hz (i.e. 6 vibrations per second) so that each front ramp 18a can be broken down into six steps, each step corresponding to a rotation angle of 3° of the cam dead second. It is quite obvious that another frequency could be chosen.
  • a movement along the front ramp 18a of a tooth 18 therefore corresponding to an angle of rotation of 18° of the deadbeat seconds cam.
  • the front ramp 18a of each tooth 18 has a slope which is higher over the last three steps corresponding to an angle of rotation of the dead seconds cam of between 9° and 18°, i.e. moment close to the jump, only on the first three steps corresponding to an angle of rotation of the deadbeat seconds cam of between 0° and 9°.
  • 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 seconds cam , the height a of the tooth corresponding to the third pitch, i.e.
  • an angle of rotation of 9° of the deadbeat seconds cam is between 10% and 15% of the height h
  • the height b of the tooth corresponding to the fifth pitch i.e. an angle of rotation of 15° from the deadbeat seconds cam, is between 55% and 60% of the height h.
  • the profile of the reverse 18b makes it possible to avoid premature jumping of the deadbeat seconds 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 deadbeat seconds cam 12, a constant clearance is maintained between the deadbeat seconds cam 12 and the passive palette of the other feeler arm (that is to say the palette of the feeler arm which is not in contact with the ramp before a tooth).
  • a mechanism for securing the relative position of the seconds wheel 1 and the jumping member 6 in order to ensure permanent indexing of the seconds wheel 1 and the jumping member 6, including when the drive mechanism of the jumping member has stopped following the stopping of the movement.
  • 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 onto the second wheel 1. Said pins 30 and 36 are represented 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 separating arms 6a.
  • the first pin 30 is positioned so as to be at the front of the separating 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 operation normal of the mechanism.
  • the first pin 30, integral with the seconds wheel 1 comes to bear on the separating arm 6a of the jumping member 6, the separating arm 6a then constituting a stop for the first pin 30.
  • the first pin 30, continuing its movement with the second wheel 1, causes the separation arm 6a and therefore the jumping member 6 in its movement, so that the second wheel 1 and the jumping member 6 move back together and remain indexed, particularly when setting the time.
  • the second pin 36 is positioned so as to be at the rear of the separating arm 6a of the jumping member 6 when the seconds wheel 1 and the jumping member 6 rotate in the same direction, in particular during normal operation of the mechanism .
  • a margin of at least one pitch, and preferably equal to one pitch, is provided.
  • the first and second bearing means comprise an eccentric 38, 40 instead of the first pin 30 and the second pin 36 respectively, their operation being similar.
  • the advantage of the eccentrics 38 and 40 compared to the pins 30, 36, is that the watchmaker can move them and position to adjust the play between the two eccentrics 38, 40 and the separating arm 6a of the jumping member 6. This makes it possible to depend less on manufacturing tolerances.
  • the first support means are positioned so as to be in front of one of the arms separating the jumping member 6 when the second wheel 1 and the jumping member 6 rotate in the same direction
  • the second support means are positioned so as to be at the rear of another arm separating the jumper 6 when the second wheel 1 and the jumper 6 rotate in the same way.
  • one of the separating arms of the jumping member 6 constitutes the first abutment on which the first bearing means are capable of resting and the other separating arm of the jumping member 6 constitutes the second abutment. on which the second support means are likely to rely.
  • the first and second abutments are not constituted by the separating arms of the jumping member but are parts driven onto 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 operation of the deadbeat seconds mechanism is as follows: with reference to the figures 1 to 5 , the second wheel 1 drives the intermediate pinion 14 and therefore the intermediate wheel 16, which in turn drives the cam driving wheel 10 and therefore the dead second cam 12. Said dead second cam 12, by rotating, allows the front ramp 18a of a tooth 18 to act on the pallet of the upper feeler arm 20a of the deadbeat seconds anchor 20, so that said anchor 20 swings around its pivot point A to cause it to come out, at the opposite, the palette of the lower escapement arm 20d of the deadbeat second anchor 20 of the toothing of the jumping member 6.
  • step 0 represented on the figure 1
  • step 5 the fifth step of the front ramp 18a of the tooth concerned (i.e. for an angle of rotation of the dead second cam 12 of 15°, cf. figure 5 )
  • the pallet of the lower escapement arm 20d does not come out of the toothing of the jumping member 6, regardless of the backlash.
  • the asymmetrical profile of each tooth 18 of the deadbeat seconds cam 12 is such that the lifting of the anchor is done gradually with the pallet of the upper feeler arm 20a while the pallet of the lower feeler arm 20b descends without touching the deadbeat seconds cam 12.
  • the jumping member 6 has not yet jumped, and is still blocked by the pallet of the lower escapement arm 20d.
  • the pallet of the upper feeler arm 20a has reached the fifth pitch of the front ramp 18a, if the deadbeat seconds anchor 20 undergoes play compensation following a shock for example, the pallet of the lower feeler arm 20b is positioned in contact of the back 18b of the relevant tooth 18 of the deadbeat seconds cam 12, as shown in the picture 3 .
  • the jumping member 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 the sixth pitch.
  • the jumping member 6 When the pallet of the upper feeler arm 20a arrives at the sixth step of the front ramp 18a, as shown in the figure 4 , the jumping member 6 has jumped.
  • the deadbeat seconds anchor having swung, the pallet of the lower escapement arm 20d emerged from the jumping member 6 and released it.
  • the jumping organ is then again blocked by this time the pallet of the upper escapement arm 20c, on which it is held in contact by means of the spiral spring 8, as shown in the figure 4 .
  • the movement of the deadbeat seconds anchor is an alternating movement which makes it possible to release, tooth after tooth, the jumping member 6, once with the pallet of the upper escapement arm 20c, then with the pallet of the upper escapement arm 20c. lower exhaust 20d, successively and alternately. Accordingly, the dead second indicator advances in increments of 1 second.
  • the deadbeat seconds mechanism of the invention makes it possible to have precise jumps every second with less energy consumption. Indeed, the mechanism of the invention is powered by the same energy source as the going train. A second power source is not required. Furthermore, the arrangement on separate axes of the jumping organ and the deadbeat seconds cam makes it possible to provide optimized shapes for the pallets of the escapement arms on the one hand and for the pallets of the feeler arms on the other hand. , in connection with optimized forms of the teeth of the deadbeat seconds cam. Energy consumption due to the spiral spring between the seconds wheel and the jumping organ is almost nil. In particular, the steeper the slope of the ramp before the teeth of the deadbeat seconds cam over the last three steps of the tooth, the more the jump will be marked and therefore precise.
  • a lower slope on the first three pitches of the tooth means that the angular pitch of the deadbeat seconds anchor is relatively low over this period. Torque consumption is therefore low.
  • the slope over the last three steps is, on the contrary, greater but must nevertheless remain measured in order to avoid overconsumption of torque on the deadbeat second cam mobile.
  • the angular pitch of the deadbeat seconds anchor is higher over the last three pitches, which allows execution of the jump over a greater measurement range, and consequently increases the precision of the jump.
  • the use of a dead second cam having only 10 teeth makes it possible to obtain larger angular steps, and therefore jumps less sensitive to imperfections in 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 deadbeat seconds anchor with which it is in contact.
  • the arrangement on separate axes of the jumping organ and the deadbeat seconds cam means that a large number of parts are not added on the same axis and therefore limits 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 the parts.
  • the dead second mechanism described above can be adapted to a unit of time other than the second.
  • the mechanism for driving 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.
  • a person skilled in the art knows how to adapt the number of teeth on the cam as well as on the jumping member accordingly, as well as the gear ratios in the going train.

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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 mechanism for driving a jumping member in a timepiece comprising a drive wheel arranged to rotate at 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 according to an oscillating movement so as to release the member jumping once per unit 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 driving wheel makes one revolution per minute, the unit of time can be the second. The drive mechanism can then constitute a deadbeat seconds mechanism, arranged to release the jumping member once per second. A deadbeat seconds mechanism includes a deadbeat seconds indicator, usually a large hand in the center of the dial, which makes 1 jump per second. These mechanisms are extremely complicated to produce. However, they sometimes lack precision, the jumps taking place in some cases at 5/6 of a second. They are also very energy consuming.

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 energy source, specific to the deadbeat seconds mechanism, in addition to the main energy source, necessary for the 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 311 865 . In these mechanisms, the dead seconds cam comprises a large number of teeth (30), involving small angular steps, which makes the jumps very sensitive to imperfections in the dead seconds cam. Moreover, the same pallet of the deadbeat seconds anchor is used both to cooperate with the deadbeat seconds cam and the seconds wheel. The deadbeat seconds anchor blocks the jumping member under the effect of the force of the coupling spring and friction. These frictions absorb a relatively large power, so that the energy consumption by the deadbeat seconds mechanism is high.

Le dispositif à force constante divulgué dans le document EP 2 166 419 A1 , qui ne comprend pas de mécanisme de seconde morte au moyen d'un organe sautant, est en revanche une pièce d'horlogerie comprenant un mouvement horloger pourvu d'un rouage de finissage alimenté par une source d'énergie et une roue d'échappement, comportant un mécanisme d'entraînement d'un organe sautant comprenant une roue d'entraînement, un organe sautant coaxial à ladite roue d'entraînement à laquelle ledit organe sautant est accouplé par un ressort, une came, solidaire d'une roue entraineuse de came, agencée pour commander une ancre, ladite came présentant un profil agence pour faire basculer l'ancre selon un mouvement oscillant de manière à libérer l'organe sautant une fois par unité de temps, la came et l'organe sautant présentant des axes de pivotement distincts, ledit mécanisme d'entraînement comprenant en outre un rouage intermédiaire liant cinématiquement la roue d'entraînement à la came, et l'ancre présentant 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.The constant force device disclosed in the document EP 2 166 419 A1 , which does not include a deadbeat seconds mechanism by means of a jumping member, is on the other hand a timepiece comprising a timepiece movement provided with a going train powered by an energy source and an escapement wheel , comprising a mechanism for driving a jumping member comprising a drive wheel, a jumping member coaxial with said drive wheel to which said jumping member is coupled by a spring, a cam, integral with a drive wheel of cam, arranged to control an anchor, said cam having a profile arranged to tilt the anchor according to an oscillating movement so as to release the jumping member once per unit of time, the cam and the jumping member having axes of separate pivoting mechanisms, said drive mechanism further comprising an intermediate gear train kinematically linking the drive wheel to the cam, and the anchor having four separate arms, two of the four arms constituting feelers rs arranged to cooperate with the cam and the two other arms constituting escapement arms arranged to successively block and release once per unit time the body jumping alternately.

Résumé de l'inventionSummary of the invention

L'invention a notamment pour objectif de pallier les différents inconvénients des mécanismes connus.The object of the invention is in particular to overcome the various drawbacks 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 seconds mechanism, reliable, making it possible 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.Another object of the invention is to provide a mechanism for driving a jumping member, and in particular a deadbeat seconds mechanism allowing 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 deadbeat seconds, allowing reduced energy consumption, authorizing the use of the same energy source as that of the movement.

A cet effet, la présente invention concerne une pièce d'horlogerie telle que définie dans la revendication 1 annexée.To this end, the present invention relates to a timepiece as defined in appended claim 1.

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 gear train may comprise an intermediate wheel set formed of an intermediate pinion arranged to cooperate with the drive wheel and of an intermediate wheel arranged to cooperate with a cam drive 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 train can be dimensioned so that the cam comprises less than thirty teeth, each tooth having a forward 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 a variant embodiment, the unit of time is the second, the drive wheel being arranged to complete one revolution in 60 seconds, and the indicator being a dead second indicator, the cam can include ten teeth and be arranged to perform three rotations per minute, each tooth having a forward ramp breaking down into 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 front ramp of each tooth of the cam has, over the last three pitches of the tooth, a slope greater than the slope of the front ramp over the first three pitches 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 so as to form substantially an X, the feeler arm positioned to cooperate with the cam being arranged opposite with respect to the pivot point of the anchor to the arm escapement positioned to release the jumping organ.

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 press against the first stop and limit the travel 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 press against 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 bearing means may comprise a pin. In another variant, the first and second bearing 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 can be a wheel having at least two recessed zones 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 abutments on which the first and second bearing means are capable of resting 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 makes it possible to have precise jumps at each unit of time while allowing reduced energy consumption. In addition, the jumps will be regular, throughout the life of the mechanism.

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 deadbeat seconds 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 can be the second wheel of the going 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 characteristics 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 simple illustrative and non-limiting example, and the appended figures, among which :
  • THE figures 1 to 4 show a top view of a dead seconds mechanism in accordance with the invention, the dead seconds anchor occupying different positions depending on the pitches of a tooth of the dead seconds cam,
  • there figure 5 represents a view of the profile of a tooth of the deadbeat seconds cam,
  • there 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
  • there figure 7 is a perspective view of the attachment of the hairspring 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 drive mechanism then constitutes a “dead seconds mechanism”, and will be referred to by this expression below.

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 deadbeat seconds mechanism according to the invention is integrated into a mechanical timepiece, comprising a timepiece movement provided with a going train powered by an energy source, such as a barrel. The going train traditionally comprises a second wheel 1, comprising 60 teeth and arranged to complete one revolution in 60 seconds. The movement also traditionally comprises an escape pinion 2 and an escape wheel 3 as well as an escape lever and a balance wheel. These elements are known to those skilled in the art and do not require a detailed description. It will however be noted that the frequency of the balance wheel 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 deadbeat seconds mechanism comprises a drive wheel constituted more specifically here by the seconds wheel 1 of the going train.

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 deadbeat seconds mechanism also includes a jumping member 6, such as a wheel, integral with a deadbeat seconds indicator, such as a hand (not shown). The jumping member 6 is loosely mounted 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. The 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 onto the second wheel 1 and on the other hand fixed to the jumping member 6. According to a first variant, the spring -hairspring 8 comprises at its end intended to be fixed on the jumping member 6, a fixing notch 9 in which is inserted a holding stud 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 jumping member 6, a double fixing notch 32 having two housings or notches. The jumping member 6 is provided with two retaining pins 34, each retaining pin 34 being intended to be inserted into one of the housings of the double fixing notch 32. The retaining pins 34 are arranged to limit the axial play . More particularly, each retaining stud 34 has a groove around which each notch is positioned. Thus, the double fixing notch makes it possible to guarantee that the flatness of the hairspring 8 is preserved during operation of the mechanism. The jumping member 6 is a wheel comprising 30 teeth and making one revolution 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 deadbeat second mechanism also comprises a deadbeat second cam mobile formed by a cam driving wheel 10 and a deadbeat second cam 12, integral with said cam driving wheel 10. The cam driving wheel 10 is arranged to cooperate with the escapement pinion 2. More particularly, the cam driving wheel 10 is in direct engagement with the escapement 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 seconds wheel 1 and the cam driving wheel 10 are pivotally mounted on the frame of the movement so as to have separate pivot axes, so that the dead seconds cam 12 and the jumping member 6 (or 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 driving wheel 10 are kinematically connected by an intermediate gear train, and more particularly an intermediate mobile comprising an intermediate pinion 14 meshing with the second wheel 1 and an intermediate wheel 16, integral with said intermediate pinion 14, and meshing with the cam driving wheel 10. Thus, the main kinematic chain of the movement goes from the wheel 1 to the escape pinion 2 passing successively through the intermediate gear train and the cam drive wheel 10, without direct engagement between the drive pinion and the second wheel. According to a preferred embodiment, the dimensions and the number of teeth of the intermediate wheel set are provided such that the cam drive wheel 10 and the dead seconds cam 12 perform one revolution per 20 seconds, i.e. 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 of the dead seconds cam, as well as the number of teeth can be modified without departing from the scope of the present invention. For example, a period of 16 seconds could be chosen, with a deadbeat seconds cam comprising 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 deadbeat seconds mechanism also comprises a deadbeat seconds anchor 20 pivotally mounted at a pivot point A on the movement frame, and controlled by the deadbeat seconds cam 12 to release and cause the jumping member 6 to jump once per second. . The jumping member 6 thus constitutes a deadbeat seconds 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.In accordance with the invention, deadbeat seconds anchor 20 comprises four distinct arms 20a, 20b, 20c and 20d. The end of each of the arms acts as a pallet. In the rest of the description, the term “pallet” is used to designate the end of an arm 20a, 20b, 20c and 20d, the pallet therefore forming a single piece with the corresponding arm. Advantageously, deadbeat seconds anchor 20 is made in one piece and made by LIGA. The upper arm 20a and the lower arm 20b constitute upper and lower feelers arranged to cooperate with the cam of deadbeat seconds 12. The upper arm 20c and the lower arm 20d constitute upper and lower escapement arms arranged to successively block and release, once per second, the jumping member 6 alternately. The four arms 20a, 20b, 20c and 20d are positioned with respect to the pivot point A so as to substantially form an X, the end of each arm being curved in order to be able to cooperate either with the dead second cam 12 or with the jumping member 6. The arms 20a, 20b, 20c and 20d work in opposition with respect to the pivot point A. For example, as shown in figure 1 , the upper feeler arm 20a is positioned to be controlled by the profile of the tooth 18 of the deadbeat seconds cam 12 while the opposite escapement arm with respect to the pivot point A, namely the lower escapement 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 deadbeat second cam 12 has a profile defined by a front ramp 18a, the functional part of the tooth on which the end or the pallet of the feeler arms 20a, 20b rubs, as well as a reverse 18b. Advantageously, the frequency of the balance is chosen at 3 Hz (i.e. 6 vibrations per second) so that each front ramp 18a can be broken down into six steps, each step corresponding to a rotation angle of 3° of the cam dead second. It is quite obvious that another frequency could be chosen. A movement along the front ramp 18a of a tooth 18 therefore corresponding to an angle of rotation of 18° of the deadbeat seconds cam. In order to have a precise jump, the front ramp 18a of each tooth 18 has a slope which is higher over the last three steps corresponding to an angle of rotation of the dead seconds cam of between 9° and 18°, i.e. moment close to the jump, only on the first three steps corresponding to an angle of rotation of the deadbeat seconds cam of between 0° and 9°. As shown more precisely by 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 seconds cam , the height a of the tooth corresponding to the third pitch, i.e. an angle of rotation of 9° of the deadbeat seconds cam, is between 10% and 15% of the height h, and the height b of the tooth corresponding to the fifth pitch, i.e. an angle of rotation of 15° from the deadbeat seconds 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 makes it possible to avoid premature jumping of the deadbeat seconds 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 deadbeat seconds cam 12, a constant clearance is maintained between the deadbeat seconds cam 12 and the passive palette of the other feeler arm (that is to say the palette of the feeler 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, a mechanism is provided for securing the relative position of the seconds wheel 1 and the jumping member 6 in order to ensure permanent indexing of the seconds wheel 1 and the jumping member 6, including when the drive mechanism of the jumping member has stopped following the stopping of the movement. With reference to the figure 4 , 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 onto the second wheel 1. Said pins 30 and 36 are represented 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 separating arms 6a. More particularly, the first pin 30 is positioned so as to be at the front of the separating 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 operation normal of the mechanism. When the seconds wheel 1 rotates in a direction opposite to that of the jumping member 6, in particular when setting the time of the movement, the first pin 30, integral with the seconds wheel 1, comes to bear on the separating arm 6a of the jumping member 6, the separating arm 6a then constituting a stop for the first pin 30. The first pin 30, continuing its movement with the second wheel 1, causes the separation arm 6a and therefore the jumping member 6 in its movement, so that the second wheel 1 and the jumping member 6 move back together and remain indexed, particularly 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 separating arm 6a of the jumping member 6 when the seconds wheel 1 and the jumping member 6 rotate in the same direction, in particular during normal operation of the mechanism . A margin of at least one pitch, and preferably equal to one pitch, is provided. When the jumping member 6 is stopped, for example during switching, the second pin 36, integral with the second wheel 1, moving in the normal direction, comes to rest on the separating arm 6a of the jumping member 6, the separation 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, in particular during 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 seconds wheel 1 and the jumping member 6 is secured, so that there is no loss of winding on the hairspring 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 security mechanism is represented. According to this variant, the first and second bearing means comprise an eccentric 38, 40 instead of the first pin 30 and the second pin 36 respectively, their operation being similar. The advantage of the eccentrics 38 and 40 compared to the pins 30, 36, is that the watchmaker can move them and position to adjust the play between the two eccentrics 38, 40 and the separating arm 6a of the jumping member 6. This makes it possible to depend less 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 arms separating 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 so as to be at the rear of another arm separating the jumper 6 when the second wheel 1 and the jumper 6 rotate in the same way. Thus, one of the separating arms of the jumping member 6 constitutes the first abutment on which the first bearing means are capable of resting and the other separating arm of the jumping member 6 constitutes the second abutment. on which the second support means are likely 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 abutments are not constituted by the separating arms of the jumping member but are parts driven onto 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 deadbeat seconds mechanism is as follows: with reference to the figures 1 to 5 , the second wheel 1 drives the intermediate pinion 14 and therefore the intermediate wheel 16, which in turn drives the cam driving wheel 10 and therefore the dead second cam 12. Said dead second cam 12, by rotating, allows the front ramp 18a of a tooth 18 to act on the pallet of the upper feeler arm 20a of the deadbeat seconds anchor 20, so that said anchor 20 swings around its pivot point A to cause it to come out, at the opposite, the palette of the lower escapement arm 20d of the deadbeat second 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 front ramp 18a of the tooth concerned (i.e. for an angle of rotation of the dead second cam 12 of 15°, cf. figure 5 ), the pallet of the lower escapement arm 20d does not come out of the toothing of the jumping member 6, regardless of the backlash. The asymmetrical profile of each tooth 18 of the deadbeat seconds cam 12 is such that the lifting of the anchor is done gradually with the pallet of the upper feeler arm 20a while the pallet of the lower feeler arm 20b descends without touching the deadbeat seconds 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 feeler arm 20a arrives at the fifth step of the front ramp 18a, as shown in the figure 2 , the jumping member 6 has not yet jumped, and is still blocked by the pallet of the lower escapement arm 20d. Once the pallet of the upper feeler arm 20a has reached the fifth pitch of the front ramp 18a, if the deadbeat seconds anchor 20 undergoes play compensation following a shock for example, the pallet of the lower feeler arm 20b is positioned in contact of the back 18b of the relevant tooth 18 of the deadbeat seconds cam 12, as shown in the picture 3 . Even in this configuration, the jumping member 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 the sixth pitch. When the pallet of the upper feeler arm 20a arrives at the sixth step of the front ramp 18a, as shown in the figure 4 , the jumping member 6 has jumped. The deadbeat seconds anchor having swung, the pallet of the lower escapement arm 20d emerged from the jumping member 6 and released it. The jumping member 6, returned by the spiral spring 8 fixed to the seconds wheel 1, rotates by 6°, ie an advancement or a jump of one second of the deadbeat seconds indicator. The jumping organ is then again blocked by this time the pallet of the upper escapement arm 20c, on which it is held in contact by means of the spiral spring 8, as shown in the figure 4 . It is the pallet of the lower sensor arm 20b, opposite with respect to the pivot point A, which will come into contact with the ramp before 18a of a tooth of the deadbeat seconds cam 12, to tilt the deadbeat seconds anchor 20 in the other direction and again release the jumping member. Thus, the movement of the deadbeat seconds anchor is an alternating movement which makes it possible to release, tooth after tooth, the jumping member 6, once with the pallet of the upper escapement arm 20c, then with the pallet of the upper escapement arm 20c. lower exhaust 20d, successively and alternately. Accordingly, 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 deadbeat seconds mechanism of the invention makes it possible to have precise jumps every second with less energy consumption. Indeed, the mechanism of the invention is powered by the same energy source as the going train. A second power source is not required. Furthermore, the arrangement on separate axes of the jumping organ and the deadbeat seconds cam makes it possible to provide optimized shapes for the pallets of the escapement arms on the one hand and for the pallets of the feeler arms on the other hand. , in connection with optimized forms of the teeth of the deadbeat seconds cam. Energy consumption due to the spiral spring between the seconds wheel and the jumping organ is almost nil. In particular, the steeper the slope of the ramp before the teeth of the deadbeat seconds cam over the last three steps of the tooth, the more the jump will be marked and therefore precise. A lower slope on the first three pitches of the tooth means that the angular pitch of the deadbeat seconds anchor is relatively low over this period. Torque consumption is therefore low. The slope over the last three steps is, on the contrary, greater but must nevertheless remain measured in order to avoid overconsumption of torque on the deadbeat second cam mobile. As a result, the angular pitch of the deadbeat seconds anchor is higher over the last three pitches, which allows execution of the jump over a greater measurement range, and consequently increases the precision of the jump. Moreover, the use of a dead second cam having only 10 teeth makes it possible to obtain larger angular steps, and therefore jumps less sensitive to imperfections in 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 the parts of the deadbeat seconds mechanism directly linked to the deadbeat seconds indicator are hollowed out, in order to lighten them as much as possible and reduce inertia as well as torque consumption. In addition, these recesses make it possible to balance the parts, in order to obtain an unbalance 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 deadbeat seconds anchor with which it is in contact. As a result, when the deadbeat seconds anchor tilts, the jumping member does not move, which ensures the stability of the deadbeat seconds 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 organ and the deadbeat seconds cam means that a large number of parts are not added on the same axis and therefore limits 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 the 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 quite obvious that the dead second mechanism described above can be adapted to a unit of time other than the second. Thus, the mechanism for driving 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, a person skilled in the art knows how to adapt the number of teeth on the cam as well as on the jumping member accordingly, as well as the gear ratios in the going train.

Claims (14)

  1. Timepiece comprising a horological movement provided with a going train powered by an energy source, an escapement pinion (2) and an escapement wheel (3), said timepiece including a drive mechanism for driving a jumping element comprising a drive wheel (1), an indicator of a unit of time, a jumping element (6) integral with said indicator and coaxial to said drive wheel (1) to which said jumping element (6) is coupled by a spring (8), a cam (12), integral with a cam drive wheel (10), arranged to control a pallet-lever (20), said cam (12) having a profile arranged to cause the pallet-lever (20) to rock in an oscillating motion so as to release the jumping element (6) once per unit of time, the cam (12) and the jumping element (6) having distinct pivot arbours, said drive mechanism, further comprising an intermediate train kinematically connecting the drive wheel (1) to the cam (12), and the pallet-lever (20) having four distinct arms (20a, 20b, 20c, 20d), two (20a, 20b) of the four arms forming feelers arranged to cooperate with the cam (12) and the other two arms (20c, 20d) forming escapement arms arranged to successively block and release the jumping element (6) once per unit of time, alternately, and said cam drive wheel (10) being directly engaged with the escapement pinion.
  2. Timepiece according to claim 1, characterised in that the intermediate train comprises an intermediate wheel set formed of an intermediate pinion (14) arranged to cooperate with the drive wheel (1) and an intermediate wheel (16) arranged to cooperate with the cam drive wheel (10) integral with the cam (12).
  3. Timepiece according to any of the preceding claims, characterised in that the intermediate train is dimensioned such that the cam (12) comprises less than thirty teeth (18), with each tooth (18) having a front ramp (18a), and makes more than one revolution per minute.
  4. Timepiece according to any of the preceding claims, characterised in that, the unit of time being the second, the drive wheel (1) being arranged to make one revolution in 60 seconds, and the indicator being a deadbeat seconds indicator, the cam (12) comprises ten teeth (18) and is arranged to make three revolutions per minute, each tooth (18) having a front ramp (18a) divided into six steps.
  5. Timepiece according to claim 3 or 4, characterised 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 greater slope than the slope of the front ramp (18a) on the first three steps of the tooth (18).
  6. Timepiece according to any of the preceding claims, characterised in that the four arms (20a, 20b, 20c, 20d) of the pallet-lever (20) are arranged substantially to form an X-shape, the feeler arm (20a, 20b) positioned to cooperate with the cam (12) being arranged oppositely, relative to the pivot point of the pallet-lever (20), to the escape arm (20c, 20d) positioned to release the jumping element (6).
  7. Timepiece according to any of the preceding claims, characterised in that the timepiece comprises a mechanism for securing the relative position of the drive wheel (1) and the jumping element (6).
  8. Timepiece according to claim 7, characterised in that the mechanism for securing the relative position of the drive wheel (1) and the jumping element (6) comprises first means of abutment provided on the drive wheel (1) and a first stop member provided on the jumping element (6), said first means of abutment being arranged to abut on the first stop member when the drive wheel (1) and the jumping element (6) rotate in opposite directions.
  9. Timepiece according to any of claims 7 and 8, characterised in that the mechanism for securing the relative position of the drive wheel (1) and the jumping element (6) comprises second means of abutment provided on the drive wheel (1) and a second stop member provided on the jumping element (6), said second means of abutment being arranged to abut on the second stop member when the jumping element (6) is stopped.
  10. Timepiece according to claims 8 and 9, characterised in that the first and second means of abutment comprise a pin (30, 36).
  11. Timepiece according to claims 8 and 9, or claim 10, characterised in that the first and second means of abutment comprise an eccentric (38, 40).
  12. Timepiece according to claims 8 and 9, or claims 10 or 11, characterised in that the jumping element (6) is a wheel having at least two recessed areas separated by at least one separating arm (6a), and in that the first and second means of abutment are disposed on either side of said at least one separating arm (6a), said separating arm (6a) forming at least one of the first and second stop members on which the first and second means of abutment are respectively capable of abutting.
  13. Timepiece according to any of claims 1 to 12, characterised in that the drive wheel (1) is powered by the energy source of the movement.
  14. Timepiece according to any of claims 1 to 13, characterised in that the drive wheel (1) is the fourth wheel of the going train.
EP15196125.7A 2014-12-11 2015-11-24 Drive mechanism of a skipping member Active EP3032349B1 (en)

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EP3824352A4 (en) * 2018-07-19 2022-03-16 Janer, Werner Multi-cam, continuous-drive escapement mechanism
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HK1225816B (en) 2017-09-15
US20160170374A1 (en) 2016-06-16
JP2016114605A (en) 2016-06-23
CH710477A2 (en) 2016-06-15
RU2015153133A (en) 2017-06-16
EP3032349A1 (en) 2016-06-15
RU2015153133A3 (en) 2019-05-16
JP6297535B2 (en) 2018-03-20
CN105700324B (en) 2018-01-02
US9429914B2 (en) 2016-08-30
CN105700324A (en) 2016-06-22
RU2739148C2 (en) 2020-12-21

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