EP3542224B1 - Echappement d'horlogerie a transmission de couple optimise - Google Patents

Echappement d'horlogerie a transmission de couple optimise Download PDF

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Publication number
EP3542224B1
EP3542224B1 EP17801690.3A EP17801690A EP3542224B1 EP 3542224 B1 EP3542224 B1 EP 3542224B1 EP 17801690 A EP17801690 A EP 17801690A EP 3542224 B1 EP3542224 B1 EP 3542224B1
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EP
European Patent Office
Prior art keywords
escapement
face
impulsion
escapement wheel
anchor
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
EP17801690.3A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3542224A1 (fr
Inventor
Alexis HERAUD
Valentin MOLINA
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.)
Richemont International SA
Original Assignee
Richemont International SA
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Filing date
Publication date
Application filed by Richemont International SA filed Critical Richemont International SA
Priority to EP21169122.5A priority Critical patent/EP3869279A1/fr
Publication of EP3542224A1 publication Critical patent/EP3542224A1/fr
Application granted granted Critical
Publication of EP3542224B1 publication Critical patent/EP3542224B1/fr
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Classifications

    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00—Escapements
    • G04B15/14—Component parts or constructional details, e.g. construction of the lever or the escape wheel
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B15/00—Escapements
    • G04B15/06—Free escapements
    • G04B15/08—Lever escapements

Definitions

  • the present invention relates to the field of watchmaking. It relates, more particularly, to an exhaust with optimized torque transmission.
  • a conventional escapement such as a Swiss lever escapement, English lever escapement, Daniels escapement, or the like, comprises a lever which intermittently locks an escape wheel, and transmits energy from the going train to the regulating organ when the wheel is released. Oscillations of the regulating organ, such as a balance-spring, actuate the anchor in order to perform this periodic release of the escape wheel, and again supply an impulse to the regulating organ to maintain its oscillations.
  • the anchor comprises at least two pallets, one - entry - located upstream with respect to the direction of rotation of the escape wheel, the other - exit - located downstream.
  • the pallet which is engaged with the escapement wheel is raised, releasing the escapement wheel and transmitting an impulse to the regulating organ via an impulse face that includes each palette.
  • the other pallet is moved into the path of the teeth of the escape wheel, and blocks it. Then, the cycle starts again for the other pallet.
  • impulse faces consist of planes. Although these simple shapes are easy to manufacture, the torque transmission varies along the pulse phase, which is detrimental to the performance of the escapement.
  • planar impulse faces often give rise to detachment of the pallet, in particular when it makes the transition from the impulse phase on the pallet to the impulse phase on the tooth, which also impairs the exhaust performance.
  • the document CH702689 describes an escapement in which the output vane and/or the input vane has an impulse face which is curved such that, during a whole part of the impulse phase, the angle defined by the impulse faces of the tooth and the pallet at the point of contact between these faces is at most equal to 7°.
  • This certainly represents an improvement over flat impulse faces, but the shape chosen does not eliminate variations in torque transmission.
  • a modeling study has shown that the derivative of the torque ratio between that of the lever and that of the escape wheel with respect to the angle of the escape wheel changes sign several times, and said torque ratio varies on the order of 25% to 35% along the concave part of the vane.
  • the convex part at the start of the pulse face has an entirely conventional radius of curvature, which results from current manufacturing methods, and has in no way been optimized.
  • the object of the present invention is therefore to at least partially overcome the drawbacks mentioned above.
  • the invention relates to an escapement for a timepiece.
  • This escapement comprises an escapement wheel mounted to pivot around an axis of rotation and intended to be driven by a driving source, said escapement wheel comprising a plurality of teeth.
  • the escapement further comprises an anchor mounted pivoting around an axis of rotation, and comprises an input pallet as well as an output pallet.
  • Each pallet comprises a rest face arranged to block said escapement wheel during rest phases, as well as an impulse face arranged to interact with said escapement wheel in order to transmit impulses received from the latter to a member regulator arranged to perform oscillations, said lever being arranged to release said escape wheel periodically under the control of said regulating member.
  • the escape wheel comprises teeth having convex impulse faces.
  • the transition between the various phases is thus smoothed, which prevents the pallet from lifting off the wheel during the cycle.
  • the invention also relates to an escapement which comprises an escapement wheel mounted to pivot around an axis of rotation and intended to be driven by a power source, said escapement wheel comprising a plurality of teeth.
  • the escapement further comprises an anchor mounted pivoting around an axis of rotation, and comprises an input pallet as well as an output pallet.
  • Each pallet comprises a rest face arranged to block said escapement wheel as well as an impulse face arranged to interact with said escapement wheel in order to transmit impulses received from the latter to a regulating member arranged to perform oscillations , said anchor being arranged to release said escape wheel periodically under the control of said regulating member.
  • said Threshold value is a function of the first derivative of the speed ratio of the anchor on the escape wheel during the impulse on the beak of said pallet.
  • this value can be set arbitrarily.
  • the escapement according to the invention comprises each of the aforementioned optimizations, that is to say that relating to the impulse faces of the pallets, as well as that relating to the impulse face of the teeth of the wheel. exhaust.
  • the invention also relates to a timepiece movement comprising an escapement as defined above, as well as to a timepiece comprising such a movement.
  • the figure 1 illustrates an escapement 1 according to the invention.
  • This escapement 1 takes the general form of a Swiss lever escapement, in which each pallet takes part in providing an impulse to the regulating organ.
  • the escapement includes an escape wheel 3, arranged to be driven by a power source not shown.
  • This driving source can be for example a mainspring or an electric motor, which is in kinematic connection with the escapement wheel 3 via a going train (also not shown).
  • the escapement wheel 3 is pivotally mounted on a shaft (not shown), the theoretical axis of which is indicated by the reference sign 5.
  • the teeth of the escapement wheel 7 each have an upstream face 7a, which interacts with the pallets when the escape wheel 3 is blocked, and an impulse face.
  • the invention applies to other shapes of escape wheel, for example with pointed teeth (English lever escapement), or to less conventional shapes.
  • the teeth 7 of the escape wheel 3 interact in a known way with an anchor 9, which pivots around a theoretical axis of rotation 11.
  • this theoretical axis 11 coincides with a shaft (not illustrated), but an anchor of the “suspended” type as described in the document CH708113 , or any other suitable type is also possible.
  • the line joining the axis of rotation 5 of the escape wheel 3 and that of the lever defines a center distance 12.
  • the general shape of the illustrated anchor 9 is conventional. To this end, it comprises a rod 9a extending from the axis of rotation 11 and ending in a fork 9c, which interacts with a regulating member (not shown) in a known manner in order to cause it to oscillate with a predetermined periodicity, which need not be described here in detail. Furthermore, a pair of arms 9b extend on either side of the axis of rotation 11 in directions substantially perpendicular to the rod 9a, and end in pallets 13, 15. It goes without saying that d other forms of anchor less usual can also be used within the scope of the invention.
  • Each of these pallets 13, 15 is arranged to block and to periodically release the escape wheel, the latter being blocked by one of the pallets 13, 15, then re-blocked by the other, in sequence.
  • Pallet 13 shown on the right in the figure 1 is the input pallet, located upstream with respect to the direction of rotation of the escape wheel 3 indicated by the arrow, and the pallet 15, located downstream, is the output pallet.
  • each pallet 13, 15 comprises, as generally known, a rest face 13a respectively 15a, and a pulse face 13b respectively 15b.
  • the rest faces 13a, 15a serve to block the escape wheel 3 during phases of rest, and the impulse faces 13b, 15b cooperate with the teeth 7 to transmit an impulse to the lever and thus to the regulating organ during the impulse phase.
  • Each of these teeth 7 comprises a resting beak 7c, which interacts with the resting faces 13a, 15a of the pallets 13, 15, as well as an oblique impulse face 7b.
  • the resting beak 7c which is located between the upstream face 7a and the impulse face 7b, as well as this impulse face 7b, contribute to transmitting an impulse to the anchor 9.
  • the rest faces 13a, 15a are typically planes, the angle of which is chosen so that, during the phases of rest, the force F resulting from the contact between the rest face 13a, 15a and tooth 7 comprises a component which tends to keep pallet 13 or 15, as the case may be, engaged with escape wheel 3.
  • This force F consequently generates a torque around the axis of rotation 11 of the anchor 9 which tends to cause the anchor to rotate counterclockwise (depending on the orientation of the figure 1 ) when the input paddle 13 is engaged, and clockwise when the output paddle 15 is engaged.
  • the impulse faces of the pallets 13b, 15b are typically planes, which leads, during the impulses, to a reduction in the torque transmitted from the escapement wheel 3 to the lever 9 along of each pulse phase. This torque variation is inefficient, and limits the performance of exhaust 1.
  • the invention therefore relates mainly to the shape of the impulse faces 13b, 15b of the pallets 13, 15, as well as that of the impulse face 7b of the teeth 7 of the escape wheel 3. Since the active faces 13a, 13b, 15a, 15b of the paddles are not, or at least should not be, planar, the terminology of "face” is used instead of the usual formulation "plane of".
  • the figure 4 illustrates schematic modeling that can be used to calculate the shape of vane impulse faces.
  • the geometric relationship between the point of contact C' between the impulse face 13b of the input pallet and a tooth 7 of the escapement wheel 3, the escapement wheel 3, and center distance 12 is shown.
  • ⁇ is the angle between a line joining said point of contact and the axis of rotation of said escape wheel 3, and said center distance 12, defined mathematically. This angle therefore decreases along the pulse phase on the input paddle 13 since the point of contact C′ approaches the center distance 12 when the wheel exhaust 3 spins.
  • COF is the trigonometric tangent (in radians) of the coefficient of friction between the escapement wheel and said impulse face, that is to say tan( ⁇ ) according to conventional notation
  • R is the distance between the axis of rotation of said escape wheel and said point of contact, with a tolerance of +/- 10%, preferably +/- 7%, more preferably +/- 5% or even +/- 3% or +/- 2% in order to present realistic manufacturing tolerances
  • C is the torque ratio between that of the anchor relative to that of the escape wheel, ie C anchor / C wheel
  • L is the length of said center distance 12.
  • the invention encompasses a family of possible curves. This is inevitable given the manufacturing tolerances, since it is very difficult to manufacture, in a reproducible manner, a curve which is mathematically perfect.
  • the figure 5 illustrates, in an exaggerated way, the development of ⁇ orientation of the impulse face 13b of the input pallet 13 along its impulse phase. It is clear that, when the escape wheel 3 rotates and the contact point C′ evolves along an arc of a circle, that the orientation angle ⁇ increases when ⁇ decreases for the reasons explained above.
  • the figure 7 illustrates this growth as a function of the angle a(t) of the contact point C' over time, and the values of the orientation angle ⁇ thus calculated at a plurality of points can be used to define tangents which can be combined in a smoothed manner to define the shape of the impulse face 13b of the input vane 13, over at least part of its length. This part can extend over for example at least 20%, at least 40%, at least 50%, at least 60% or even at least 80% or 90% of the length of said pulse face 13b. From these figures, it is clear that said impulse face 13 will be convex.
  • the figure 6 illustrates, also exaggeratedly, the development of ⁇ orientation of the impulse face 15b of the output vane 15 along its pulse phase.
  • the orientation angle ⁇ decreases.
  • the figure 8 illustrates this decrease as a function of the angle ⁇ of the contact point C′; indeed during the movement a moves away from the center distance or ⁇ is strictly negative in the counterclockwise sense, so ⁇ (t) decreases during the movement.
  • the angles ⁇ orientation thus calculated can be used to define tangents which can be combined in order to define the shape of the impulse face 15b of the output vane 15, over at least part of its length.
  • This part can extend over for example at least 20%, at least 40%, at least 50%, at least 60% or even at least 80% or 90% of the length of said pulse face 15b.
  • the angle ⁇ increases during the corresponding pulse phase, since the point of contact C' moves away from the center distance 12. From these figures, it is clear that said impulse face 15 will be concave.
  • the shapes of the impulse planes 13b, 15b, of the pallets can be determined for an escapement having a given geometry, and this by taking into account the shape of the impulse faces 7b of the teeth 7 of the escapement wheel 3, which determines the development of the position of the point of contact with the pallets 13, 15 along the impulse phases.
  • ⁇ orientation represents the angle formed between the tangent of the impulse face 7b of the tooth 7 at the contact point C' and the center distance 12, the other variables being as described above in the context of the profile of the impulse faces 13b, 15b of the vanes 13, 15.
  • the value C must be lower than a predefined threshold value (see below).
  • the angle ⁇ orientation can be calculated at several points, in order to determine the profile of said impulse face 7b in the manner mentioned above.
  • the figure 11 is a normalized graph illustrating a comparison of the speed ratio of the lever 9 on the escapement wheel 3 on a clearance and an impulse, for a conventional escapement (“Rv Standard Profiles”) and an escapement according to the invention (“ Rv Curved profiles”).
  • This graph illustrates both the effect of the shape of the impulse faces 13b, 15b which ensures constant torque transmission during the impulse phase on the impulse face 7b of a tooth 7, as well as the effect of the curved profile of the teeth 7 of the escape wheel.
  • This graph also illustrates the effect of the curved profile of the impulse face 7b of the teeth 7 of the escapement wheel 3. Since this face 7b is curved, the slope of the gear ratio curve has a slope significantly less than that which occurs in the classic case “Rv standard profiles”. Detachment can thus be avoided.
  • the anchor 9 and/or the escape wheel 3 described above can, for example, be manufactured by micro-machining processes, such as LIGA, 3D printing, masking and engraving from a slab of material, stereolithography, or the like.
  • Suitable materials can, for example, be chosen from monocrystalline, polycrystalline or amorphous metals (such as steel, nickel-phosphorus, brass or similar), non-metals such as silicon, its oxide, its nitride or its carbide, alumina in all its forms, diamond (including adamantine carbon), these non-metallic materials being monocrystalline or polycrystalline. All these materials may optionally be coated with another hard and/or anti-friction material, such as adamantine carbon or silicon oxide.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Gears, Cams (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Vibration Dampers (AREA)
  • Table Equipment (AREA)
  • Mechanical Operated Clutches (AREA)
EP17801690.3A 2016-11-17 2017-11-16 Echappement d'horlogerie a transmission de couple optimise Active EP3542224B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP21169122.5A EP3869279A1 (fr) 2016-11-17 2017-11-16 Échappement à transmission de couple optimisé

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH01521/16A CH713143A1 (fr) 2016-11-17 2016-11-17 Échappement pour pièce d'horlogerie.
PCT/EP2017/079518 WO2018091616A1 (fr) 2016-11-17 2017-11-16 Echappement d'horlogerie a transmission de couple optimise

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP21169122.5A Division-Into EP3869279A1 (fr) 2016-11-17 2017-11-16 Échappement à transmission de couple optimisé
EP21169122.5A Division EP3869279A1 (fr) 2016-11-17 2017-11-16 Échappement à transmission de couple optimisé

Publications (2)

Publication Number Publication Date
EP3542224A1 EP3542224A1 (fr) 2019-09-25
EP3542224B1 true EP3542224B1 (fr) 2022-05-18

Family

ID=57485268

Family Applications (2)

Application Number Title Priority Date Filing Date
EP21169122.5A Withdrawn EP3869279A1 (fr) 2016-11-17 2017-11-16 Échappement à transmission de couple optimisé
EP17801690.3A Active EP3542224B1 (fr) 2016-11-17 2017-11-16 Echappement d'horlogerie a transmission de couple optimise

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP21169122.5A Withdrawn EP3869279A1 (fr) 2016-11-17 2017-11-16 Échappement à transmission de couple optimisé

Country Status (6)

Country Link
US (1) US11480923B2 (zh)
EP (2) EP3869279A1 (zh)
JP (1) JP7016360B2 (zh)
CN (1) CN109997084B (zh)
CH (1) CH713143A1 (zh)
WO (1) WO2018091616A1 (zh)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7103041B2 (ja) * 2018-08-03 2022-07-20 セイコーエプソン株式会社 アンクル、ムーブメント、時計

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH9351A (de) * 1894-10-15 1895-05-31 Hermann Fischer Verbesserter Anker für Uhren aller Art
US3538705A (en) * 1968-11-07 1970-11-10 Hamilton Watch Co Escapement
US3628327A (en) * 1969-04-14 1971-12-21 Suwa Seikosha Kk Clubtooth lever escapement
EP1770452A1 (fr) * 2005-09-30 2007-04-04 Peter Baumberger Echappement à detente pour pièce d'horlogerie
CH702689B1 (fr) * 2006-11-13 2011-08-31 Patek Philippe Sa Geneve Echappement à ancre.
CN201083966Y (zh) * 2007-07-02 2008-07-09 天津中鸥表业集团有限公司 机械手表的擒纵机构
CH708113B1 (de) 2007-09-13 2014-12-15 Stéphane Von Gunten Anker für eine Uhrenhemmung.
EP2336832B1 (fr) * 2009-12-21 2020-12-02 Rolex Sa Échappement à ancre suisse
US8882339B2 (en) * 2010-04-01 2014-11-11 Rolex S.A. Immobilizing device for a toothed wheel
EP2431823A1 (fr) * 2010-09-16 2012-03-21 Blancpain S.A. Echappement blancpain à ancre amélioré pour mouvement d'horlogerie
JP5485859B2 (ja) * 2010-11-17 2014-05-07 セイコーインスツル株式会社 アンクル脱進機及びこれを備えた機械式時計
CH704764A2 (fr) * 2011-03-31 2012-10-15 Cartier Creation Studio Sa Mécanisme d'échappement notamment pour mouvement d'horlogerie.
EP2607968B1 (fr) * 2011-12-21 2014-10-08 Vaucher Manufacture Fleurier S.A. Mécanisme d'échappement
JP5891076B2 (ja) * 2012-03-09 2016-03-22 セイコーインスツル株式会社 がんぎ歯、該がんぎ歯を備えたがんぎ車、アンクル脱進器、ムーブメント、並びに機械式時計及びトルク伝達方法
EP2706416B1 (fr) * 2012-09-07 2015-11-18 The Swatch Group Research and Development Ltd Ancre flexible à force constante

Also Published As

Publication number Publication date
CN109997084A (zh) 2019-07-09
US11480923B2 (en) 2022-10-25
CH713143A1 (fr) 2018-05-31
JP2019536031A (ja) 2019-12-12
EP3542224A1 (fr) 2019-09-25
EP3869279A1 (fr) 2021-08-25
US20200064776A1 (en) 2020-02-27
JP7016360B2 (ja) 2022-02-21
WO2018091616A1 (fr) 2018-05-24
CN109997084B (zh) 2021-03-12

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