EP3206088B1 - Hemmungsmechanismus - Google Patents

Hemmungsmechanismus Download PDF

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Publication number
EP3206088B1
EP3206088B1 EP16154993.6A EP16154993A EP3206088B1 EP 3206088 B1 EP3206088 B1 EP 3206088B1 EP 16154993 A EP16154993 A EP 16154993A EP 3206088 B1 EP3206088 B1 EP 3206088B1
Authority
EP
European Patent Office
Prior art keywords
escapement
mobile
wheel
anchor
oscillatory
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
EP16154993.6A
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English (en)
French (fr)
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EP3206088A1 (de
Inventor
Serge MENSAH
Andreas PAGNOTTA
Kéwin Bas
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.)
Cartier International AG
Original Assignee
Cartier International AG
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Publication date
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Priority to EP16154993.6A priority Critical patent/EP3206088B1/de
Publication of EP3206088A1 publication Critical patent/EP3206088A1/de
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Publication of EP3206088B1 publication Critical patent/EP3206088B1/de
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Classifications

    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00—Escapements
    • G04B15/06—Free escapements
    • G04B15/08—Lever escapements
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00—Escapements
    • G04B15/10—Escapements with constant impulses for the regulating mechanism
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/20—Compensation of mechanisms for stabilising frequency
    • G04B17/26—Compensation of mechanisms for stabilising frequency for the effect of variations of the impulses
    • 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
    • G04B17/00—Mechanisms for stabilising frequency
    • G04B17/20—Compensation of mechanisms for stabilising frequency
    • G04B17/28—Compensation of mechanisms for stabilising frequency for the effect of imbalance of the weights, e.g. tourbillon
    • G04B17/285—Tourbillons or carrousels

Definitions

  • the present invention relates to an escapement mechanism for a timepiece. More particularly, the present invention relates to a translation escapement mechanism.
  • oscillations of the oscillating mobile acting regulating member are maintained by a pulse of the escape wheel transmitted by the anchor to the axis of the regulating organ.
  • the document FR 1 009 853 discloses a conventional anchor escapement comprising two escape wheels connected to each other by a constant force spring.
  • the displacements or translations of the equilibrium point of the regulating organ intervene at regular intervals and have the same duration and the same amplitude.
  • the duration of execution of a displacement or translation of the equilibrium point of the oscillatory mobile depends on the energy supplied to the escape mechanism. In a timepiece comprising a mechanical movement powered by a barrel, this duration will depend on the winding of the mainspring and therefore vary according to the power reserve. This variation has obvious drawbacks of chronometry.
  • the object of the present invention is to overcome the above drawbacks and to provide an escape mechanism and in particular a translational escapement mechanism which makes it possible to substantially always have the same energy transmitted to the oscillating mobile so as to improve the timekeeping.
  • the present invention relates to a translation escapement mechanism according to claim 1.
  • the present invention also relates to a timepiece according to claim 8.
  • the exhaust mechanism according to the invention is a constant force translation escapement mechanism. It is intended to equip a timepiece including a watch movement.
  • the escapement mechanism according to the invention comprises a mobile of constant force, an escape mobile, an oscillating mobile and an anchor mobile.
  • the escape mobile illustrated at figure 3a comprises an exhaust pinion 6 secured to an exhaust pin 7 pivoted on a fixed piece 8 of the plate or movement of the timepiece.
  • a first escape wheel 9 is also integral with the exhaust shaft 7.
  • the constant-force mobile illustrated at figure 2 comprises an input pinion 1 engaged with the work train of the timepiece, a second escape wheel 2 secured to the input pinion 1 and a spring of constant force 3.
  • the input pinion 1 pivots about the axis 4 of an intermediate wheel 5.
  • the constant force spring 3 is fixed to its outer end 3a at an attachment point 2a of the second escape wheel 2, while its inner end is fixed to the axis 4 of the intermediate wheel 5.
  • the torque of the wheel of the movement of the timepiece is transmitted from the input gear 1 to the intermediate wheel 5 by the constant force spring 3 which is permanently energized.
  • the intermediate wheel 5 of the mobile of constant force meshes with the exhaust pinion 6 of the mobile escape.
  • the oscillatory mobile illustrated at figure 3b comprises a rocker 10 and a hairspring 11, one end, preferably the inner end, is fixed to the rocker 10 while the other end, preferably the one outside, is fixed to an external attachment point 12 secured to 7.
  • the oscillatory wheel which is the regulating member of the exhaust mechanism according to the invention, pivots concentrically to the escapement wheel.
  • the oscillating wheel pivots on the piece 8.
  • the oscillatory motive does not appear in the Figures 5 to 13 , only the external attachment point 12 carried by the exhaust shaft 7 is visible and serves to illustrate the forces exerted on the hairspring 11 of the oscillating mobile and on the exhaust shaft 7 and the first escape wheel 9.
  • the anchor mobile illustrated at figure 4 comprises an anchor shank 13 on which are rotated a first anchor 15 and a second anchor 14.
  • the first and second anchors 15, 14 are integral in rotation.
  • the first anchor 15 is intended to cooperate with the first escape wheel 9 while the second anchor 14 is intended to cooperate with the second escape wheel 2.
  • Each of the first and second anchors 15, 14 comprises two arms terminated respectively by an input pallet 15a, 14a and an output pallet 15b, 14b.
  • the first and second anchors 15, 14 are coaxial and arranged on the anchor shank 13 so that the first anchor 15 is at the same height as the first escape wheel 9 while the second anchor 15 is at the same height as the first escape wheel 9 while the second anchor 15 is anchor 14 is at the same height as the second escape wheel 2.
  • the entry pallet 14a and the output pallet 14b of the second anchor 14 each comprise a bevelled end 141, 142 connecting the outer side 143, 144 to the inner side 145, 146 of said entry pallet 14a. respectively of said output pallet 14b.
  • the outer edge 143 of the entry pallet 14a and the inner side 146 of the output pallet 14b of the second anchor 14 form a rest plane.
  • the entry pallet 15a of the first anchor 15 illustrated in detail at the figure 6 has an inner flank 151 followed by a tapered end 150 and a flat portion 152, connecting said inner flank 151 to the outer flank of the input pallet 15a.
  • This outer edge of the entry pallet 15a comprises a first rest plane 153 substantially parallel to the inner side 151 of the entry pallet 15 and a resting notch which is preferably formed of a second rest plane 154 inclined and a third plane of rest 155 connecting the second rest plane 154 to the plane portion 142.
  • the intersection of the second and third rest planes 154, 155 forms a line of rest 156 of the input pallet 15a.
  • the end of the output pallet 15b of the first anchor 15 illustrated in FIG. figure 6 has a beveled end 157 connecting the outer side 158 to the inner side 159 of the output pallet 15b.
  • the spring of constant force 3 which is reassembled at each oscillation of the oscillatory mobile, makes it possible to filter the torque variations of the gear train of the workpiece mechanism. clock on the mobile exhaust.
  • the torque of the train tends to rotate the input gear 1 and the second escapement wheel 2 counterclockwise (it will be associated with a negative sign).
  • the constant force spring 3 it is arranged so that its torque tends to rotate the intermediate wheel 5 counterclockwise (thus also has a negative sign). Consequently, the torque due to the constant force spring 3 and acting on the first escape wheel 9 tends to rotate it clockwise and this torque opposite the torque of the constant force spring 3 therefore has a positive sign.
  • the oscillatory mobile exerts a torque on the outer attachment point 12 of the exhaust shaft 7 which tends to rotate the first escape wheel 9 clockwise during the first half cycle (positive torque) and counterclockwise during the second half cycle (negative torque).
  • the escape mechanism according to the invention is in a first blocking phase A illustrated in FIG. figure 5 .
  • the oscillating mobile and in particular the hairspring 11 exert a torque on the outer attachment point 12 of the exhaust shaft 7 which tends to rotate the first escape wheel 9 in the clockwise.
  • the resultant pairs of the spring 11 and the constant force spring 3 acting on the first escape wheel 9 tends to rotate it clockwise.
  • the escape mechanism according to the invention is arranged so that the only mobile moving is the oscillatory mobile which performs its first alternation.
  • the input pinion 1 and the second escape wheel 2 are locked by the second anchor 14, a tooth of said second escape wheel 2 being in abutment against the rest plane 143 of the entry pallet 14a of the second anchor 14.
  • the escape wheel comprising the escape pinion 6 and the first escape wheel 9 are in turn blocked by the first anchor 15, whose entry pallet 15a is in contact with a tooth of the first escape wheel 9. More precisely, as illustrated in FIG.
  • the oscillatory mobile 10, 11 changes direction for its second alternation.
  • the barrel 10 then rotates counterclockwise and the torque of the spring 11 exerted on the outer attachment point 12 of the exhaust shaft 7 tends to rotate the first escape wheel 9 counterclockwise.
  • a second blocking phase B in which the pair of the spiral 11 is negative as illustrated in the graph of the figure 14 but is always greater than the torque of the constant force spring 3.
  • the other components of the escapement mechanism according to the invention apart from the oscillatory mobile remain in the same position as for the first phase of blocking A ( figure 5 ), that is to say blocked by the anchor mobile which is itself held in abutment against the first fixed pin.
  • a first phase of clearance C illustrated in FIG. figure 7 starts when the pair of the spring 11 equals and then becomes less than the torque of the constant force spring 3.
  • the resultant of these two pairs on the first wheel Exhaust 9 tends to rotate it counterclockwise.
  • the escape wheel and in particular the first escape wheel 9 is not blocked in the counterclockwise direction, they begin to rotate.
  • the intermediate wheel 5 rotates clockwise driven by the exhaust pinion 6.
  • the input pinion 1 and the second escape wheel 2 are in turn always blocked by the second anchor 14. Even if the first anchor 15 is now released from the first escape wheel 9, the anchor mobile remains stationary and bears against the first fixed pin.
  • This first release phase C lasts until a tooth of the first escape wheel 9 comes into contact with the outer blank 158 of the output pallet 15b of the first anchor 15. This contact marks the beginning of the second phase of release D illustrated in the figure 8 .
  • the second release phase D lasts until the torque of the spiral 11 again becomes greater than the torque of the spring of constant force 3. At this point, the first pulse phase E, illustrated in FIG. figure 9 .
  • the first escape wheel 9 drives the outer attachment point 12 of the exhaust axis 7 which moves "pulls" on the spring 11 and moves its equilibrium point which has the effect of raising the spiral 11 and thus to maintain the oscillations of the balance 10.
  • This phase marks the beginning of the pulse.
  • the pulse lasts until the next oscillation of the oscillatory mobile.
  • the first escape wheel 9 drives the intermediate wheel 5 counter-clockwise via the exhaust pinion 6.
  • the first pulse phase E is extended until a tooth of the first escape wheel 9 comes into contact with the beveled end 158 of the output pallet 15b of the first anchor 15. There then begins a first release phase F illustrated in the figure 10 .
  • the first escape wheel 9 drives the first anchor 15 counterclockwise.
  • the second anchor 14 secured to the first anchor 15 then also turns into the counterclockwise direction and the entry pallet 14a of the second anchor 14 progressively leaves the toothing of the second escape wheel 2.
  • the escapement wheel is always moving in the clockwise direction (the torque of the spiral 11 is always greater than the torque of the constant force spring 3) and continues to transmit the pulse to the oscillatory wheel in moving the outer end of the hairspring 11 via the external attachment point 12.
  • the intermediate wheel 5 is therefore always driven in the counterclockwise direction.
  • the first release phase F continues until the entry pallet 14a of the second anchor 14 is completely disengaged from the toothing of the second escape wheel 2.
  • This second release phase G continues until a tooth of the second escape wheel 2 comes into contact with the output pallet 14b of the second anchor 14, this contact marking the beginning of a third phase of blocking H.
  • This fourth blocking phase H is illustrated in FIG. figure 12 .
  • the second escape wheel 2 and the input pinion 1 are thus blocked again by the second anchor 14.
  • the anchor wheel and in particular the pallet 15b of the first anchor 15 have moved to a position in which they are no longer in the path of the first escape wheel 9 which continues to rotate in the clockwise direction (the pulse is always transmitted to the mobile oscillatory).
  • the anchor mobile stops once the output pallet 14b of the second anchor 14 in contact with the second escape wheel 2 and once the anchor mobile abuts with the first fixed pin not shown.
  • the fourth locking phase H continues until a tooth d of the first escape wheel 9 comes into contact with the second inclined rest plane 154 of the entry pallet 15a of the first anchor 15.
  • a last phase of release I occurs at the end of the second alternation of the oscillatory mobile, before a new oscillation.
  • This last phase of liberation I is illustrated in figure 13a .
  • the first escape wheel 9 is always driven in the clockwise direction by the torque due to the constant force spring 3 which is greater than the torque of the hairspring 11. Thanks to the profile of the entry pallet 15a of the first anchor 15 and its rest notch 154, 155, 156, the first escape wheel 9 bearing against said input pallet 15a will rotate the anchor wheel clockwise. More precisely, the tooth d of the first escape wheel 9 slides on the second inclined plane of repose 154 of the entry pallet 15a of the first anchor 15, the inclination of said second rest plane 154 causing the rotation of the first anchor 15 clockwise ( figure 13b ). Following the rotation of the anchor wheel clockwise, the second anchor 14 releases again the second escape wheel 2 and the input gear 1 which start to turn counterclockwise under the action of the gear train of the movement of the timepiece. The constant force spring 3 is thus again partially recharged.
  • This last release phase I lasts until the tooth d of the first escape wheel 9 comes into contact with the rest line 156 of the rest notch 154, 155 of the entry pallet 15a of the first anchor 15. At this time, the first escape wheel 9 and the escape mobile are again blocked by the anchor mobile. This completes the impulse.
  • the anchor wheel and in particular the profile of the entry pallet 15a of the first anchor 15 are shaped so that at the moment when the tooth d of the first wheel 9 comes into contact with the rest line 156, the second anchor 14 has pivoted in a position in which the input pallet 14a of the second anchor 14 again cooperates with the second escape wheel 2 to block the second and the input pinion 1.
  • the escape mechanism has thus found the configuration of the first phase of blocking A described above and illustrated in FIG. figure 5 .
  • the oscillatory mobile 10, 11 can initiate a new oscillation.
  • the pulse is transmitted to the oscillating mobile 10, 11 from the first pulse phase E until the end of the last release phase I during the second alternation.
  • oscillating mobile oscillator 10, 11. the exhaust mechanism described above is a lost-blow exhaust mechanism.
  • the mobile of constant force could be coaxial with the mobile of escape.
  • the inner end of the hairspring 11 can be fixed to the escapement and the outer end of the hairspring 11 can be fixed to the balance 10.
  • the hairspring can also have a shape (for example, cylindrical or spherical) which does not necessarily have inner and outer ends.
  • escapement with a constant force translation is thus achieved which has the advantage of improving the chronometry of a standard translation escapement by making the torque transmitted to the oscillatory wheel constant and independent of the energy transmitted by the wheel and the body. motor of the movement of the timepiece (winding of the mainspring, for example).
  • the escapement mechanism according to the invention is independent of the oscillating mobile, which can be a traditional balance spring system as described above or a suspended balance system.
  • the exhaust mechanism according to the invention is also suitable for a high frequency oscillating mobile.

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

Claims (8)

  1. Hemmungsmechanismus mit Translation, der ein erstes Hemmungsrad (9), ein zweites Hemmungsrad (2), ein schwingendes Drehteil (10, 11) und ein Ankerdrehteil (15, 14) umfasst, wobei das erste Hemmungsrad (9) gestaltet ist, um mit dem schwingenden Drehteil (10, 11) zusammenzuwirken, um den Gleichgewichtspunkt des schwingenden Drehteils (10, 11) bei jeder Schwingung des Drehteils (10, 11) um eine vorbestimmte Schwingungsweite zu verlagern, um die Schwingungen des schwingenden Drehteils (10, 11) aufrecht zu erhalten, wobei das Ankerdrehteil (15, 14) gestaltet ist, um mit dem ersten Hemmungsrad (9) und dem zweiten Hemmungsrad (2) zusammenzuwirken, dadurch gekennzeichnet, dass der Hemmungsmechanismus ferner eine Feder (3) mit konstanter Kraft, die das erste Hemmungsrad (9) mit dem zweiten Hemmungsrad (2) verbindet, und ein Zwischenrad (5) umfasst, das in einen Hemmungstrieb (6) eingreift, der fest mit dem ersten Hemmungsrad (9) verbunden ist; und dadurch, dass ein Ende der Feder (3) mit konstanter Kraft an dem Zwischenrad (5) befestigt ist, während das zweite Ende (3a) der Feder (3) mit kontanter Kraft an dem zweiten Hemmungsrad (2, 2a) befestigt ist.
  2. Hemmungsmechanismus nach Anspruch 1, dadurch gekennzeichnet, dass das erste und das zweite Hemmungsrad (9, 2) koaxial sind.
  3. Hemmungsmechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das schwingende Drehteil (10, 11) koaxial mit dem ersten Hemmungsrad (9) ist.
  4. Hemmungsmechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das schwingende Drehteil (10, 11) vom Typ Unruh-Spiralfeder ist, das eine Unruh (10) und eine Spiralfeder (11) umfasst.
  5. Hemmungsmechanismus nach dem vorhergehenden Anspruch, dadurch gekennzeichnet, dass das innere Ende der Spiralfeder (11) an der Unruh (10) befestigt ist, während das äußere Ende der Spiralfeder (11) fest mit dem ersten Hemmungsrad (9, 12) verbunden ist.
  6. Hemmungsmechanismus nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Ankerdrehteil (15, 14) eine erste und eine zweite Eingangspalette (15a, 14a) und eine erste und eine zweite Ausgangspalette (15b, 14b) umfasst, wobei die ersten Eingangs- und Ausgangspaletten (15a, 15b) mit dem ersten Hemmungsrad (9) zusammenwirken und die zweiten Eingangs- und Ausgangspaletten (14a, 14b) mit dem zweiten Hemmungsrad (2) zusammenwirken.
  7. Hemmungsmechanismus nach dem vorhergehenden Anspruch, dadurch gekennzeichnet, dass die erste Eingangspalette (15a) auf ihrer äußeren Flanke (153) eine Ruhekerbe umfasst, wobei die Ruhekerbe eine erste geneigte Ruheebene (154) und eine zweite Ruheebene (155) umfasst, wobei die Überschneidung der Ruheebenen eine Ruhelinie (156) bildet, wobei die Ruhekerbe angepasst ist, damit, wenn das erste Hemmungsrad (9) sich in einer ersten Richtung dreht und ein Zahn des ersten Hemmungsrads (9) mit der ersten geneigten Ruheebene (154) in Kontakt gelangt, der Zahn entlang der ersten geneigten Ruheebene (154) gleitet und das Ankerdrehteil (15, 14) in einer ersten Richtung drehbar mitnimmt, bis der Zahn mit der Ruhelinie (156) in Kontakt gelangt, wobei das erste Hemmungsrad (9) dann dazu neigt, das Ankerdrehteil in eine zweite, der ersten entgegengesetzte Richtung zu drehen.
  8. Uhr, die einen Hemmungsmechanismus nach einem der vorhergehenden Ansprüche umfasst.
EP16154993.6A 2016-02-10 2016-02-10 Hemmungsmechanismus Active EP3206088B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP16154993.6A EP3206088B1 (de) 2016-02-10 2016-02-10 Hemmungsmechanismus

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Application Number Priority Date Filing Date Title
EP16154993.6A EP3206088B1 (de) 2016-02-10 2016-02-10 Hemmungsmechanismus

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EP3206088A1 EP3206088A1 (de) 2017-08-16
EP3206088B1 true EP3206088B1 (de) 2019-01-02

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Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH715023A1 (fr) 2018-05-25 2019-11-29 Sa De La Manufacture Dhorlogerie Audemars Piguet & Cie Échappement à détente auto-démarrant et sécurisé pour pièce d'horlogerie
WO2020007619A2 (fr) 2018-07-02 2020-01-09 Complitime Sa Mecanisme d'echappement horloger
JP6748318B1 (ja) * 2020-01-29 2020-08-26 セイコーウオッチ株式会社 脱進調速機、時計用ムーブメントおよび時計

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE50739C (de) * S. RIEFLE^ in München, Karlsplatz 29/I Doppelradhemmung für Chronoi^ mit vollkommen freier Unruhe und für Pe*1 . uhren mit freiem Pendel
FR1009853A (fr) * 1948-07-02 1952-06-04 Mécanisme d'échappement perfectionné

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
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