EP3510449B1 - Hemmungsmechanismus - Google Patents

Hemmungsmechanismus Download PDF

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Publication number
EP3510449B1
EP3510449B1 EP17761283.5A EP17761283A EP3510449B1 EP 3510449 B1 EP3510449 B1 EP 3510449B1 EP 17761283 A EP17761283 A EP 17761283A EP 3510449 B1 EP3510449 B1 EP 3510449B1
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EP
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Prior art keywords
release
escape
mobile
wheel
release mobile
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Active
Application number
EP17761283.5A
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English (en)
French (fr)
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EP3510449A1 (de
Inventor
Dominique Renaud
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Freymond Eric
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Dominique Renaud SA
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    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00—Escapements
    • G04B15/06—Free 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
    • G04B15/14—Component parts or constructional details, e.g. construction of the lever or the escape wheel

Definitions

  • the present invention relates to the field of watchmaking. It relates to an escape mechanism and, more particularly, to a direct impulse free escape mechanism.
  • the escapement is an essential part of mechanical watch movements. It is generally placed between a gear train and an oscillator.
  • the cog transmits to the exhaust a torque coming from the energy source, which maintains and counts the oscillations of the oscillator.
  • the detent escapement is the one of the two that has the best energy efficiency.
  • Different examples of detent escapements are for example described in the documents CH 704 151 B1 , EP 1,538,491 A1 our still EP 1,710,636 A1 .
  • the detent escapements are sensitive to strong accelerations and to shocks with significant risks of galloping and tripping. As a result, the detent escapement is not widespread because it can not bear being worn and difficult to couple with high frequency oscillators, which today tend to impose themselves because of their better precision.
  • the anchor escapement does not know these risks but has the drawback of higher energy consumption because of the more numerous shocks, inertia and greater friction at the level of the anchor.
  • the present invention aims to remedy the aforementioned drawbacks by proposing an exhaust which is compatible with strong accelerations of an oscillator at high frequency and to the constraints of carrying on the wrist while maintaining a low energy consumption.
  • the exhaust mechanism of the invention is designed so that the release mobile and the unidirectional drive device are arranged to cooperate with means configured to accumulate only a portion of the energy supplied by a pulse from the oscillator during the disengagement of the disengagement mobile on the one hand and to restore it in the form of an acceleration of the escape wheel during a transmission by the escape wheel of a pulse at the oscillator on the other hand.
  • the release mobile and the wheeled mobile are arranged relative to each other so that there is a zero or negative draft between the two.
  • the gear train and the release mobile are arranged so that said portion of energy transmitted by the oscillator during the release phase is accumulated in elastic form before contributing to the acceleration of said wheel exhaust.
  • the exhaust mechanism comprises a positioning stop capable of positioning the release mobile in the engagement position, said stop being if necessary fixed with reference to the axis of rotation of the release mobile.
  • the axes of rotation of the gear train, of the escapement wheel and of the release gear are parallel and coplanar.
  • the oscillator is movable in rotation about an axis and in that the axes of rotation of the oscillator, of the gear train, of the escape wheel and of the release motive are parallel and coplanar when the engagement mobile is in the engagement position.
  • the unidirectional drive device comprises a plurality of flexible blades each arranged in abutment on a ratchet stop, said flexible blades and ratchet stops being arranged radially in a regular angular distribution.
  • the unidirectional drive device is integral with the release mobile or the oscillator.
  • the release mobile is coaxial with the escape wheel.
  • the exhaust mechanism comprises an elastic member, in particular a return spring, mounted between the release mobile and the escape wheel, and which tends to bring the mobile back in its engagement position, preferably against the positioning stop in the engagement position.
  • the release mobile comprises rest pins, in that the gear mobile includes rest pads, in that the trajectories of the rest pads and rest pins are intersecting and in that the mechanism is arranged so that the rest studs meet the rest pins by causing the gear train to stop when the engagement mobile is in the engagement position.
  • the unidirectional drive device is integral with the escape wheel.
  • the escapement wheel is mounted movable on the release movable and the escapement wheel comprises rest teeth intended to come into abutment against a fixed rest pallet with reference to the frame of the timepiece.
  • the release mobile also advantageously consists of a rocker pivoted on the axis of the gear train.
  • the springs of the trigger flip-flops are designed to exert a low restoring force.
  • the increase in this restoring force would make it possible to reduce the sensitivity to shock and to support high frequencies by accelerating the return of the rocker in its rest position but would have the disadvantage of increasing the energy consumption during the release.
  • the present invention implements a particular escape mechanism in which it is sought to recover the energy necessary for the release rather than to reduce it. Like any detent escapement, this mechanism has a single rest position, the release and the impulse take place alternately in two, the other being a knockout.
  • the mechanism comprises a gear train 1 kinematically connected to an escape wheel 2 and forming with it a train driven by a drive member not shown, typically a barrel.
  • the escape wheel has impulse teeth 3 intended to periodically give impulse to an oscillator here taking the form of a pendulum of which only the plate 4 and the pin 5 are represented.
  • the gear train 1 comprises rest pads 6 arranged in a circle at the end of the arm extending radially.
  • the exhaust mechanism further comprises a release mobile 7 taking the form of a wheel pivoted on the same axis as the wheel. exhaust.
  • the release mobile 7 comprises rest pins 8 and a unidirectional drive device formed by flexible blades 9 extending radially and bearing against ratchet stops 10 in their rest position.
  • the pawl stops 10 are adjacent to the rest pins but it could be otherwise as will be seen later.
  • the angular amplitude of the rotation of the release mobile 7 relative to the escape wheel 2 is limited by a positioning stop 11, integral with the release mobile 7.
  • a return spring 12 disposed between the escape wheel 2 and the release mobile 7 tends to return the release mobile 7 to an angular position defined with reference to the escape wheel 2.
  • the figure 2 represents the exhaust mechanism at rest, the balance coming from freely traversing the additional arc and the pin 5 preparing to come into contact with a flexible blade 9 of the release mobile 7.
  • the train is stopped, a rest pad 6 of the gear train bearing against a rest pin 8 of the release track 7.
  • the figure 3 represents the escape mechanism during the disengagement phase during which the disengagement mobile 7 moves from an engagement position to a disengagement position under the impulse of the pendulum transmitted via the flexible blade 9.
  • the flexible blade 9 is in abutment against the pawl stop 10 by forming a pawl mechanism so that the impulse of the pendulum causes the release mobile 7 to rotate counterclockwise as shown in the figures.
  • the bearing surfaces of the rest pad 6 and the rest pin 8 slide against one another.
  • the contact surfaces of the rest pegs 8 are cylinder portions with a circular base coaxial with the pivot axis of the release mobile 7 so that the release of the release mobile 7 does not cause advance nor of retraction of the gear train 1. This configuration corresponds to a zero pulling angle.
  • the surface of the rest pegs could have a positive pull angle to secure the blocking of the release mobile 7 or on the contrary a negative pull angle to facilitate its release.
  • the flexible arms 9 and the rest pins 8 are arranged radially at a regular angular distribution so that the release mobile 7 is balanced on its axis of rotation and, therefore, not very sensitive to the accelerations undergone by the timepiece. Furthermore, the return spring 12 tends to keep the release mobile 7 in abutment against the escape wheel 2 in its engagement position. Thus, it is not necessary to provide a positive pull angle to further secure the release mobile 7, which makes it possible to minimize the disturbances caused to the oscillator during the release.
  • the figure 4 represents the escape mechanism in the impulse phase.
  • the figure 5 represents the escape mechanism at the end of the impulse phase and immediately before stopping the train caused by the meeting of a rest pad 6 with a rest pin 8.
  • the circular paths of the rest pads and rest pins are intersecting and the mechanism is arranged so that a stud 6 meets a pin 8 when the release mobile 7 is in the engagement position, that is to say when the escape wheel 2 has caught up the release mobile 7, the positioning stop 11 pressing against the escape wheel 2. Consequently, the advance of the train is limited when the release mobile is in the engagement position.
  • the figure 6 represents the exhaust mechanism at rest at the time of the blow lost during the next alternation.
  • the balance pivots counterclockwise and the pin 5 spreads the flexible arm 9 without driving the release mobile 7 in rotation.
  • the flexible blade 9 constitutes, with the ratchet stop 10, a ratchet-type unidirectional drive system.
  • the back of the impulse teeth has a circular profile conforming to the shape of the balance plate to prevent accidental retraction of the escape wheel while the balance traverses the additional arc.
  • the train is driven by a double motorization: the motor member which propels the train in a conventional manner, and the return spring 12 which tows the escape wheel 2 when it starts up.
  • the action of the return spring 12 is all the more effective when it is fixed on the release mobile 7 which is itself driven in rotation by the oscillator. A portion of the energy contributing to the acceleration of the train therefore comes from the oscillator which goes against the generally accepted idea that it is necessary to avoid braking the oscillator so as not to disturb its isochronism and limit energy consumption.
  • the transfer of energy from the oscillator to the gear train is optimized thanks to the movable release 7 and the return spring 12 which acts as a shock absorber and limits the loss of energy when the ankle hits the flexible arm.
  • the acceleration of the train is therefore given smoothly, but since it is stronger than that which would be given by a single drive member, the time required for the escape wheel 2 to catch up with the ankle 5 of the balance wheel is reduced.
  • the device can operate at higher frequencies but also that the pulse angle traveled by the balance in the pulse phase is greater.
  • the stopping of the train is caused by the meeting of two mobile elements with reference to the frame, kinematically linked in a discontinuous manner.
  • the release mobile Unlike a trigger rocker which performs a back and forth movement by dissipating the energy it receives from the balance, the release mobile always pivots in the same direction which is also that of the impulse given by the oscillator as well as the displacement of the escape wheel.
  • the energy accumulated in elastic form at each release in the return spring is restored when the escape wheel starts.
  • the recovery of part of the energy taken from the oscillator in the release phase characterizes a new type of exhaust that can be designated by the term of "turbo-expansion", This one presenting interesting performances in terms of energy efficiency as well as frequency and dependability.
  • the balance plate comprises a pin which performs the release and a pulse pallet, distinct from the pin, arranged to receive the pulse of the escape wheel.
  • the respective angular and radial positions of the dowel and the pallet with respect to the pendulum axis define the start of the release and impulse phases and the angular speeds of release and impulse.
  • the angular speed of the escape wheel is higher than the speed reached by the escape wheel at the start of the pulse.
  • the mechanism of exhaust according to the invention can be arranged so that the kinetic energy acquired by the release mobile during the release phase is at least partially restored and contributes to the acceleration of the train.
  • the unidirectional drive device could be placed on the oscillator.
  • the release mobile could be connected to the escape wheel by flexible elements.
  • the disengagement movement of the disengagement mobile under the action of the oscillator could be assimilated to a rotation or to any other trajectory adapted to the disengagement of the rest pins.
  • These same flexible elements could also play the role of return spring.
  • the Figures 7 to 12 represent a second embodiment of an exhaust mechanism according to the invention.
  • the mechanism also includes a unidirectional drive device composed of a plurality of flexible blades 9 abutting on ratchet stops 10.
  • the unidirectional drive device is here mounted integral with the escape wheel 2. In an original way the wheel is not pivoted on the frame of the timepiece but on the release mobile 7 which here takes the form of a rocker pivoted on the same axis as the gear train 1.
  • the mechanism also includes a positioning stop 11 able to position the release mobile 7 in an engagement position in which the rotation of the escape wheel is limited.
  • a positioning stop 11 able to position the release mobile 7 in an engagement position in which the rotation of the escape wheel is limited.
  • the figure 9 represents the escape mechanism in the release phase.
  • the plate pin 5 struck a flexible blade 9 bearing on a ratchet stop 10.
  • the rotation of the escape wheel 2 being hampered by the rest pallet 13, it is the assembly composed of the release mobile 7 , of the escape wheel 2 and of the gear train 1 which is rotated counterclockwise around the pivot axis of the gear train.
  • the retraction of the train in the disengagement phase causes the motor organ to be rearmed so that the energy supplied by the oscillator during the disengagement is stored in elastic form by the motor organ before being returned to propel the cog.
  • the escape wheel 2 and the gear train are released.
  • the train accelerates and the release mobile 7 returns to its position of engagement against the positioning stop 11.
  • the rest plane of the rest pallet is preferably an orthoradial plane with reference to the axis of rotation of the release mobile which corresponds to a zero drawing angle. Alternatively, the rest plane may have a different inclination or a non-rectilinear profile.
  • the figure 10 represents the escape mechanism in the impulse phase after the release mobile 7 has returned to its engagement position in abutment against the positioning stop 11 and that a pulse tooth 3 of the escape wheel 2 caught up with the pendulum pin 5.
  • the figure 11 represents the mechanism at the end of the pulse phase and just before stopping the train caused by the meeting of the next pulse tooth 3 with the rest pallet 13.
  • the figure 12 shows the mechanism at rest during the lost blow when the pendulum returns when the ratchet passes.
  • the energy supplied by the oscillator during the release is at least partially returned to drive the train.
  • this second embodiment directly uses the motor member to temporarily store, in elastic form, the energy coming from the oscillator during the release. It is also the driving force which keeps the release mobile 7 in the engagement position. Note that in the exhausts of the prior art, the gear train recedes slightly during the release when the pull angle is positive, this arrangement having the aim of securing the trigger and not of recovering energy.
  • the unidirectional drive device could comprise only one pawl and be secured to the release mobile or to the oscillator.
  • the release and impulse functions could be provided by separate teeth on the escape wheel and by separate paddles on the oscillator.
  • the exhaust mobile could be translated rather than rotated. It could also be connected to the frame by a flexible element.
  • the release mobile could have a counterweight so that the mobile assembly that it composes with the escape wheel is balanced on its axis of rotation.
  • the mechanism could include a second stop to limit the amplitude of the movement of the release mobile as well as a return spring to accelerate the return of the release mobile to its engagement position.
  • the mechanism could also include a safety device which would limit the movement of the release mobile in the free oscillation phases of the oscillator.

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

Claims (15)

  1. Freier Hemmungsmechanismus mit verlorenem Schlag für ein Zeitmessgerät, wobei das Zeitmessgerät folgendes umfasst:
    - ein Räderwerk, das dazu bestimmt ist, von einem Antriebsorgan angetrieben zu werden, und das ein um eine Drehachse drehbares, in kinematischer Verbindung mit mindestens einem Hemmungsrad des Hemmungsmechanismus angeordnetes Zahnrad (1) umfasst,
    - einen Oszillator, der einen Impuls des Hemmungsrads (2) aufnehmen kann, um seine Schwingungen aufrechtzuerhalten, wobei der Hemmungsmechanismus des Weiteren folgendes umfasst:
    - ein Freigaberad (7), das so angeordnet ist, dass es bei der Drehung mit dem Hemmungsrad zusammenwirkt und sich in einer Ausrückphase unter einem Impuls des Oszillators zwischen einer Einrückstellung, in der der Vorschub des Räderwerks blockiert ist, und einer Ausrückstellung, in der der Vorschub des Räderwerks frei ist, bewegt, und
    - eine unidirektionale Antriebsvorrichtung des Freigaberads (7), die so angeordnet ist, dass sie den Oszillatorimpuls an das Freigaberad (7) überträgt, um es von der Einrückstellung auf die Ausrückstellung zu bringen,
    wobei der Hemmungsmechanismus dadurch gekennzeichnet ist, dass das Freigaberad (7) und die unidirektionale Antriebsvorrichtung so angeordnet sind, dass sie mit Mitteln (10, 12) zusammenwirken, die so ausgebildet sind, dass sie einerseits einen Teil der von einem Oszillatorimpuls gelieferten Energie beim Ausrücken des Freigaberads (7) ansammeln und andererseits diese in Form einer Beschleunigung des Hemmungsrads (2) bei der Übertragung eines Impulses durch das Hemmungsrads (2) auf den Oszillator wiederherstellen.
  2. Hemmungsmechanismus nach Anspruch 1, dadurch gekennzeichnet, dass das Freigaberad (7) und das Zahnrad (1) relativ zueinander so angeordnet sind und dass zwischen ihnen kein oder ein negativer Zug besteht.
  3. Hemmungsmechanismus nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, dass das Zahnrad (1) und das Freigaberad (7) so angeordnet sind, dass der Teil der Energie, der vom Oszillator in der Ausrückphase übertragen wird, in elastischer Form angesammelt wird, bevor sie zur Beschleunigung des Freigaberads (2) beiträgt.
  4. Hemmungsmechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass er einen Positionierungsanschlag (11) umfasst, der in der Lage ist, das Freigaberad (7) in der Ausrückstellung zu positionieren.
  5. Hemmungsmechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Drehachsen des Zahnrads (1), des Hemmungsrads (2) und des Freigaberads (7) parallel und koplanar sind.
  6. Hemmungsmechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Oszillator um eine Achse drehbar ist und die Drehachsen des Oszillators, des Zahnrades (1), des Hemmungsrades (2) und des Freigaberads (7) parallel und koplanar sind, wenn sich das Eingriffsrad (7) in der Einrückstellung befindet.
  7. Hemmungsmechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die unidirektionale Antriebsvorrichtung eine Vielzahl flexibler Lamellen (9) umfasst, die jeweils so angeordnet sind, dass sie auf einem Sperrklinkenanschlag (10) anliegen, wobei die flexiblen Lamellen (9) und die Sperrklinkenanschläge (10) radial in einer regelmäßigen Winkelverteilung angeordnet sind.
  8. Hemmungsmechanismus nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die unidirektionale Antriebsvorrichtung fest mit dem Freigaberad (7) oder dem Oszillator verbunden ist.
  9. Hemmungsmechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Freigaberad (7) koaxial zum Hemmungsrad (2) angeordnet ist.
  10. Hemmungsmechanismus nach Anspruch 9 und Anspruch 4, dadurch gekennzeichnet, dass er ein elastisches Element, insbesondere eine Rückholfeder (12) umfasst, die zwischen dem Freigaberad (7) und dem Hemmungsrad (2) montiert ist und das Freigaberad (7) in seine Einrückstellung zurückzubringt, vorzugsweise gegen den Positionierungsanschlag (11) in der Einrückstellung.
  11. Hemmungsmechanismus nach einem der Ansprüche 9 oder 10, dadurch gekennzeichnet, dass das Freigaberad (7) Auflagezapfen (8) umfasst, dass das Zahnrad (1) Auflageblöcke (6) aufweist, dass sich die Wege der Auflageblöcke (6) und der Auflagezapfen (8) schneiden und dass der Mechanismus so angeordnet ist, dass die Auflageblöcke (6) auf die Auflagezapfen (8) treffen, wodurch das Räderwerk angehalten wird, wenn sich das Eingriffsrad (7) in Einrückstellung befindet.
  12. Hemmungsmechanismus nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass das unidirektionale Antriebssystem fest mit dem Hemmungsrad (2) verbunden ist.
  13. Hemmungsmechanismus nach einem der Ansprüche 1 bis 10 oder nach Anspruch 12, dadurch gekennzeichnet, dass das Hemmungsrad (2) beweglich auf dem Freigaberad (7) montiert ist und das Hemmungsrad (2) Auflagezähne (3) umfasst, die dazu bestimmt sind, an einer in Bezug auf den Rahmen des Zeitmessgeräts feststehenden Ruhepalette (13) anzuliegen.
  14. Hemmungsmechanismus nach Anspruch 13, dadurch gekennzeichnet, dass das Freigaberad (7) eine Wippe ist, die um die Achse des Zahnrads schwenkt.
  15. Hemmungsmechanismus nach den Ansprüchen 4 bis 14, dadurch gekennzeichnet, dass der Positionierungsanschlag (11) auf dem Freigaberad (7) angeordnet ist.
EP17761283.5A 2016-09-07 2017-09-06 Hemmungsmechanismus Active EP3510449B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP16187711.3A EP3293583A1 (de) 2016-09-07 2016-09-07 Hemmungsmechanismus
PCT/EP2017/072392 WO2018046563A1 (fr) 2016-09-07 2017-09-06 Mecanisme d'echappement

Publications (2)

Publication Number Publication Date
EP3510449A1 EP3510449A1 (de) 2019-07-17
EP3510449B1 true EP3510449B1 (de) 2020-07-08

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EP16187711.3A Withdrawn EP3293583A1 (de) 2016-09-07 2016-09-07 Hemmungsmechanismus
EP17761283.5A Active EP3510449B1 (de) 2016-09-07 2017-09-06 Hemmungsmechanismus

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EP16187711.3A Withdrawn EP3293583A1 (de) 2016-09-07 2016-09-07 Hemmungsmechanismus

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WO (1) WO2018046563A1 (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020007619A2 (fr) * 2018-07-02 2020-01-09 Complitime Sa Mecanisme d'echappement horloger
DE102018212113A1 (de) * 2018-07-20 2020-01-23 Creaditive Ag Hemmungssystem und das Hemmungssystem umfassendes Messgerät
EP4250019A1 (de) * 2022-03-21 2023-09-27 Patek Philippe SA Genève Uhr-oszillator für ein ultraflaches uhrwerk

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1538491B1 (de) * 2003-12-04 2010-11-10 Montres Breguet S.A. Chronometerhemmung für Uhren
EP1538490B1 (de) * 2003-12-04 2007-05-30 Montres Breguet S.A. Chronometerhemmung für Armbanduhren
EP1710636A1 (de) * 2005-04-06 2006-10-11 Daniel Rochat Hemmung für eine Uhr
EP1770452A1 (de) * 2005-09-30 2007-04-04 Peter Baumberger Chronometerhemmung für Uhren
EP2199875B1 (de) * 2008-12-16 2014-09-24 Rolex Sa Chronometerhemmung
JP5366319B2 (ja) * 2009-09-14 2013-12-11 セイコーインスツル株式会社 デテント脱進機およびそれを有する機械式時計

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None *

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EP3510449A1 (de) 2019-07-17
WO2018046563A1 (fr) 2018-03-15
EP3293583A1 (de) 2018-03-14

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