EP3869279A1 - Auspuffanlage mit optimierter drehmomentübertragung - Google Patents

Auspuffanlage mit optimierter drehmomentübertragung Download PDF

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Publication number
EP3869279A1
EP3869279A1 EP21169122.5A EP21169122A EP3869279A1 EP 3869279 A1 EP3869279 A1 EP 3869279A1 EP 21169122 A EP21169122 A EP 21169122A EP 3869279 A1 EP3869279 A1 EP 3869279A1
Authority
EP
European Patent Office
Prior art keywords
escape wheel
impulse
anchor
face
pallet
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.)
Pending
Application number
EP21169122.5A
Other languages
English (en)
French (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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Richemont International SA filed Critical Richemont International SA
Publication of EP3869279A1 publication Critical patent/EP3869279A1/de
Pending legal-status Critical Current

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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
    • G04B15/14—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, 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, has an anchor which intermittently blocks an escape wheel, and transmits energy from the finishing gear to the gear. regulating organ when the wheel is released. Oscillations of the regulating member, such as a sprung balance, actuate the anchor in order to effect this periodic release of the escape wheel, and again provide an impulse to the regulating member to maintain its oscillations.
  • the anchor has at least two vanes, one - input - located upstream with respect to the direction of rotation of the escape wheel, the other - output - located downstream.
  • the pallet which is engaged with the escape wheel is raised, releasing the escape wheel and transmitting an impulse to the regulating organ via an impulse face that contains each pallet.
  • the other pallet is moved in the path of the teeth of the escape wheel, and blocks it. Then, the cycle begins again for the other pallet.
  • the impulse faces are formed by planes. Although these simple shapes are easy to manufacture, torque transmission varies along the pulse phase, which is detrimental to the performance of the exhaust.
  • the document CH702689 describes an escapement in which the outlet vane and / or the inlet 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 of the pallet at the point of contact between these faces is at most equal to 7 °.
  • This certainly represents an improvement over flat pulse 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 anchor and that of the escape wheel with respect to the angle of the escape wheel changes sign several times, and said torque ratio varies in the order of 25% to 35% along the concave part of the pallet.
  • the convex part at the start of the impulse face has a completely conventional radius of curvature, which results from current manufacturing processes, and has not been optimized in any way.
  • 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 escape wheel mounted to pivot about an axis of rotation and intended to be driven by a motor source, said escape wheel comprising a plurality of teeth.
  • the escapement further comprises an anchor mounted to pivot about an axis of rotation, and comprises an inlet pallet as well as an outlet pallet.
  • Each pallet comprises a rest face arranged to block said escape wheel during the rest phases, as well as an impulse face arranged to interact with said escape wheel in order to transmit impulses received from the latter to a member.
  • regulator arranged to perform oscillations, said anchor being arranged to release said escape wheel periodically under the control of said regulating member.
  • the torque transmission between the escape wheel and the anchor is improved, since it remains constant throughout the impulse phase.
  • This constant transmission maximizes the torque transmitted, improves the efficiency of the exhaust and minimizes the disturbance of the regulating organ.
  • the shape of the document palette CH702689 does not correspond to the shape defined above, and that the torque transmission is not substantially constant, as mentioned in the preamble. This is mainly (but not exclusively) due to the fact that the angle defined by the impulse faces of the tooth and the vane at the point of contact between these faces is constant and is at most equal to 7 ° (preferably at plus equal to 5 °), which can never be consistent with the aforementioned equations.
  • the shape of at least a part of each of said impulse faces observes said relationship, which has the effect that the torque transmission is constant for each vane.
  • the escape wheel comprises teeth having convex impulse faces.
  • the transition between the various phases is thus smoothed, which prevents the pallet from taking off from the wheel during the cycle.
  • the invention also relates to an escapement which comprises an escape wheel mounted to pivot about an axis of rotation and intended to be driven by a driving source, said escape wheel comprising a plurality of teeth.
  • the escapement further comprises an anchor mounted to pivot about an axis of rotation, and comprises an inlet pallet as well as an outlet pallet.
  • Each pallet comprises a rest face arranged to block said escape wheel as well as an impulse face arranged to interact with said escape wheel in order to transmit pulses 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.
  • each of said teeth comprises, and considered at each point of contact between said impulse face and one of said pallets (in particular the downstream spout of one of the latter)
  • 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 nose 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 vanes, 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 exhaust 1 according to the invention.
  • This escapement 1 takes the general form of a Swiss lever escapement, in which each blade participates in providing an impulse to the regulating member.
  • the escapement comprises 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 escape wheel 3 by means of a finishing gear (also not illustrated).
  • the escape wheel 3 is pivotally mounted on a shaft (not illustrated), the theoretical axis of which is indicated by the reference sign 5.
  • the teeth of the escape wheel 7 each have a raised face. 7a, which interacts with the paddles when the escape wheel 3 is blocked, and an impulse face.
  • the invention applies to other forms of escape wheel, for example with pointed teeth (English lever escapement), or to less conventional forms.
  • the teeth 7 of the escape wheel 3 interact in a known manner with an anchor 9, which pivots about 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 anchor defines a center distance 12.
  • the general shape of the anchor 9 illustrated 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 make it oscillate with a predetermined periodicity, which should 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 terminate in pallets 13, 15. It goes without saying that d 'other forms of anchor less usual can also be used in the context of the invention.
  • Each of these pallets 13, 15 is arranged to block and 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 on 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 an impulse face 13b respectively 15b.
  • the rest faces 13a, 15a serve to block the escape wheel 3 during rest phases, and the impulse faces 13b, 15b cooperate with the teeth 7 to transmit an impulse to the anchor and thus to the regulating organ during the impulse phase.
  • Each of these teeth 7 has a rest beak 7c, which interacts with the rest faces 13a, 15a of the vanes 13, 15, as well as an oblique impulse face 7b.
  • the resting nose 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 such that, during the rest phases, the force F resulting from the contact between the rest face 13a, 15a and tooth 7 comprises a component which tends to keep the pallet 13 or 15, where appropriate, engaged with the escape wheel 3.
  • This force F consequently generates a torque around the axis of rotation 11 of the anchor 9 which tends to rotate the anchor counterclockwise (depending on the orientation of the figure 1 ) when the input pallet 13 is engaged, and clockwise when the output pallet 15 is engaged.
  • the impulse faces of the vanes 13b, 15b are typically planes, which in impulses results in a decrease in the torque transmitted from the escape wheel 3 to the anchor 9 along of each pulse phase. This torque variation is inefficient, and limits the performance of exhaust 1.
  • the invention therefore mainly relates to the shape of the impulse faces 13b, 15b of the vanes 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 pallets are not, or at least should not be, planar, the terminology of "face” is used instead of the usual wording "plane of ".
  • the figure 4 illustrates a schematic model that can be used to calculate the shape of the impulse faces of the pallets.
  • the geometric relationship between the point of contact C 'between the impulse face 13b of the input pallet and a tooth 7 of the escape wheel 3, the escape wheel 3, and the center distance 12 is illustrated.
  • ⁇ 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 pallet 13 since the point of contact C 'approaches the center distance 12 when the wheel exhaust 3 turns.
  • COF is the trigonometric tangent (in radians) of the coefficient of friction between the escape wheel and said impulse face, that is to say tan ( ⁇ ) according to the 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, that is to say C anchor / C wheel
  • L is the length of said center distance 12.
  • the invention in view of the tolerance on the value of R as well as that on ⁇ orientation , the invention encompasses a family of possible curves. This is inevitable in view of 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 manner, the development of ⁇ orientation of the impulse face 13b of the inlet vane 13 along its impulse phase. It is clear that, when the escape wheel 3 turns and the point of contact C 'evolves in an arc of a circle, that the angle ⁇ orientation increases when ⁇ decreases for the reasons explained above.
  • the figure 7 illustrates this growth as a function of the angle ⁇ (t) of the contact point C 'over time, and the values of the angle ⁇ orientation thus calculated at a plurality of points can be used to define tangents which can be combined in a smooth manner in order to define the shape of the impulse face 13b of the inlet pallet 13, over at least part of its length. This part may for example extend over at least 20%, at least 40%, at least 50%, at least 60% or even at least 80% or 90% of the length of said impulse 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 pallet 15 along its pulse phase. It is clear that, when the escape wheel 3 turns and the point of contact C 'evolves in an arc of a circle, that the angle ⁇ orientation decreases.
  • the figure 8 illustrates this decrease as a function of the angle ⁇ of the point of contact C '; indeed during the movement a moves away from the center distance or ⁇ is strictly negative in the trigonometric direction, therefore ⁇ (t) decreases during the movement.
  • the ⁇ orientation angles calculated in this way can be used to define tangents which can be combined in order to define the shape of the impulse face 15b of the outlet pallet 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 impulse face 15b.
  • the angle ⁇ increases during the corresponding pulse phase, since the contact point 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 pulse planes 13b, 15b, vanes can be determined for an escapement having a given geometry, and this taking into account the shape of the pulse faces 7b of the teeth 7 of the escape wheel 3, which determines the development of the position of the point of contact with the vanes 13, 15 along the pulse phases.
  • ⁇ orientation represents the angle formed between the tangent of the impulse face 7b of the tooth 7 at the point of contact C 'and the center distance 12, the other variables being as described above in the context of profile of the impulse faces 13b, 15b of the pallets 13, 15.
  • the value C must be less than a predefined threshold value (see below).
  • Threshold is a value of a separation threshold calculated by experimentation or by modeling, or even defined arbitrarily. More concretely, one can for example define a limit derivative of the speed ratio of the anchor 9 on the wheel 3, by modeling.
  • the Threshold parameter is so influenced by the geometry of the exhaust, but models have indicated that a value of at most 0.01, preferably at most 0.005 are generally applicable, or can serve as starting points anyway.
  • the angle ⁇ orientation can be calculated at several points, in order to determine the profile of said impulse face 7b as mentioned above.
  • the figure 11 is a standardized graph illustrating a comparison of the gear ratio of the anchor 9 on the escape wheel 3 on a clearance and a thrust, 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 a 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 escape 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 micromachining processes, such as LIGA, 3D printing, masking and etching from a plate 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, nitride or carbide, alumina in all its forms, diamond (including adamantine carbon), these non-metallic materials being monocrystalline or polycrystalline. All these materials can 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)
  • Mechanical Operated Clutches (AREA)
  • Table Equipment (AREA)
EP21169122.5A 2016-11-17 2017-11-16 Auspuffanlage mit optimierter drehmomentübertragung Pending EP3869279A1 (de)

Applications Claiming Priority (3)

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
EP17801690.3A EP3542224B1 (de) 2016-11-17 2017-11-16 Uhr hemmung mit optimierter drehmomentübertragung

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP17801690.3A Division-Into EP3542224B1 (de) 2016-11-17 2017-11-16 Uhr hemmung mit optimierter drehmomentübertragung
EP17801690.3A Division EP3542224B1 (de) 2016-11-17 2017-11-16 Uhr hemmung mit optimierter drehmomentübertragung

Publications (1)

Publication Number Publication Date
EP3869279A1 true EP3869279A1 (de) 2021-08-25

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Family Applications (2)

Application Number Title Priority Date Filing Date
EP21169122.5A Pending EP3869279A1 (de) 2016-11-17 2017-11-16 Auspuffanlage mit optimierter drehmomentübertragung
EP17801690.3A Active EP3542224B1 (de) 2016-11-17 2017-11-16 Uhr hemmung mit optimierter drehmomentübertragung

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP17801690.3A Active EP3542224B1 (de) 2016-11-17 2017-11-16 Uhr hemmung mit optimierter drehmomentübertragung

Country Status (6)

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

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

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3628327A (en) * 1969-04-14 1971-12-21 Suwa Seikosha Kk Clubtooth lever escapement
CH702689B1 (fr) 2006-11-13 2011-08-31 Patek Philippe Sa Geneve Echappement à ancre.
EP2431823A1 (de) * 2010-09-16 2012-03-21 Blancpain S.A. Blancpain-Hemmung mit verbessertem Anker für Uhrwerk
CH708113B1 (de) 2007-09-13 2014-12-15 Stéphane Von Gunten Anker für eine Uhrenhemmung.

Family Cites Families (11)

* 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
EP1770452A1 (de) * 2005-09-30 2007-04-04 Peter Baumberger Chronometerhemmung für Uhren
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
EP2336832B1 (de) * 2009-12-21 2020-12-02 Rolex Sa Schweizer Ankerhemmung
EP2818941A1 (de) * 2010-04-01 2014-12-31 Rolex Sa Blockiervorrichtung für Zahnrad
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 (de) * 2011-12-21 2014-10-08 Vaucher Manufacture Fleurier S.A. Uhrhemmungsmechanismus
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 (de) * 2012-09-07 2015-11-18 The Swatch Group Research and Development Ltd Flexibler Anker mit konstanter Kraft

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3628327A (en) * 1969-04-14 1971-12-21 Suwa Seikosha Kk Clubtooth lever escapement
CH702689B1 (fr) 2006-11-13 2011-08-31 Patek Philippe Sa Geneve Echappement à ancre.
CH708113B1 (de) 2007-09-13 2014-12-15 Stéphane Von Gunten Anker für eine Uhrenhemmung.
EP2431823A1 (de) * 2010-09-16 2012-03-21 Blancpain S.A. Blancpain-Hemmung mit verbessertem Anker für Uhrwerk

Also Published As

Publication number Publication date
US20200064776A1 (en) 2020-02-27
EP3542224A1 (de) 2019-09-25
WO2018091616A1 (fr) 2018-05-24
JP7016360B2 (ja) 2022-02-21
EP3542224B1 (de) 2022-05-18
CH713143A1 (fr) 2018-05-31
US11480923B2 (en) 2022-10-25
CN109997084A (zh) 2019-07-09
CN109997084B (zh) 2021-03-12
JP2019536031A (ja) 2019-12-12

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