EP2859411B1 - Hemmungsvorrichtung für eine uhr - Google Patents

Hemmungsvorrichtung für eine uhr Download PDF

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Publication number
EP2859411B1
EP2859411B1 EP12726440.6A EP12726440A EP2859411B1 EP 2859411 B1 EP2859411 B1 EP 2859411B1 EP 12726440 A EP12726440 A EP 12726440A EP 2859411 B1 EP2859411 B1 EP 2859411B1
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EP
European Patent Office
Prior art keywords
mobile element
blocking
escapement
mobile
escapement wheel
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
EP12726440.6A
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English (en)
French (fr)
Other versions
EP2859411A1 (de
Inventor
Xuan Mai Tu
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.)
Detra SA
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Detra SA
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Application filed by Detra SA filed Critical Detra SA
Publication of EP2859411A1 publication Critical patent/EP2859411A1/de
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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
    • G04B15/14—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
    • 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
    • G04B15/02—Escapements permanently in contact with the regulating mechanism
    • G04B15/04—Cylinder escapements

Definitions

  • the present invention relates to an exhaust device for a timepiece, in particular for a spiral balance type wristwatch.
  • the exhaust device in a mechanical watch is the master piece intended on the one hand to deliver the energy necessary for the maintenance of the oscillation movement of the mechanical oscillator, and on the other hand to transmit the frequency of oscillation of the oscillator to the gear train causing the time display.
  • the EP0018796 A2 proposes a type of tangential drive exhaust.
  • the disadvantage of this type of exhaust is the need for use of two superimposed wheels, which increases the inertia of the exhaust and consequently a decrease in efficiency, and the number of final touches of high accuracy is also important than that of a Swiss lever escapement.
  • detent escapement Another type of tangential drive exhaust well known in the technical literature is the detent escapement. This type of escapement has only one active alternation, that is to say the escape wheel advances and gives the mechanical pulse only once per period of oscillation of the balance spring.
  • the purpose of the present invention is to overcome the known exhaust faults mentioned above by proposing a tangential drive exhaust device with two active alternations per oscillation period of the balance spring, with a single escape wheel and which however, consumes less energy during operation than the Swiss lever escapement.
  • the figure 1 also represents the platform of the balance 4 pivoting about the axis 41 and having a toothed structure 42
  • the figure 2 represents the first rest position of the exhaust of the figure 1 .
  • the balance turns clockwise.
  • the toothed structure 42 of the rocker moves away from the toothed structure 35 of the mobile 3.
  • the tooth of the escape wheel 1, under the effect of the torque of the barrel, exerts a force F on the blocking surface 33 of the mobile 3
  • This locking surface 33 is arranged so that the direction of the force F passes substantially in the vicinity of the center of the mobile 3. Under these conditions the escape wheel is locked and therefore immobilizes the mobile 3 as well as the mobile 2 by the intermediate of the toothed structures 24 and 34.
  • the figure 3 represents the position of the exhaust of the figure 6 just after the release of the first resting position
  • the balance turns counterclockwise.
  • the toothed structure 42 of the rocker comes into contact with the toothed structure 35 and rotates the wheel 3 in the clockwise direction. This action releases the tooth of the escape wheel from the locking surface 33.
  • the mechanical energy required for the clearance is extremely low since it serves only to overcome the friction of the escape wheel on the blocking surface 33 and to move the mobiles 2 and 3 on a few degrees. In this application example the angular displacement of the mobiles 2 and 3 during the release is about 4 degrees.
  • the figure 4 represents the energy transmission phase of the escapement wheel to the balance wheel when the last turns counterclockwise
  • the tooth of the escape wheel 1 bears on the impulse surface 32 and drives the mobile 3 in the clockwise direction.
  • the mechanical energy of the escape wheel is transmitted to the balance thanks to the toothed structures 42 and 35.
  • the mobile 2 is also driven by the mobile 3 by the toothed structures 34 and 24. Note that unlike a Swiss lever escapement , driving the mobile 3 by the escape wheel is substantially tangential to the trajectory of the impulse surface 32.
  • the tangential drive of the mobile 3 by the escape wheel is obtained thanks to the particular arrangement of the surfaces 33 and 32 of the mobile 3.
  • the figure 5 represents the mobiles 2 and 3 and the escape wheel 1 in the first rest position.
  • the vector n33 represents the normal to the blocking surface 33 at the locking point of the tooth of the escape wheel
  • the vector n32 represents the normal passing through the center of impulse surface 32 of the mobile 3
  • ⁇ 3 represents the external angle between n33 and n32.
  • One of the particular characteristics of the escapement according to the invention is an external angle ⁇ 3 having the same sign as that of the rotation angle of the escape wheel.
  • the external angle ⁇ 3 and the rotation angle of the escape wheel are positive with respect to the trigonometric direction.
  • figure 6 represents the external angle ⁇ e between the normal n61 at the blocking surface 61 and the normal n62 at the impulse surface 62 of the input pallet, as well as the external angle ⁇ s between the normal n63 at the blocking surface 63 and the normal n64 at the impulse surface 64 of the output pallet, of a Swiss lever escapement.
  • the figure 7 represents the end of the energy transmission phase of the escapement wheel to the balance when the last rotates counter-clockwise.
  • the tooth of the escape wheel leaves the impulse surface 32 of the mobile 3 and the locking surface 23 of the mobile 2 is in front of the tooth of the impeller wheel.
  • Exhaust 1 During this time, the beam describes its additional oscillation arc by moving its toothed structure 42 away from the toothed structure 35 of the mobile 3.
  • the figure 8 represents the second rest position of the exhaust of the figure 1 .
  • the balance turns counterclockwise.
  • the toothed structure 42 of the rocker moves away from the toothed structure 35 of the mobile 3.
  • the tooth of the escape wheel 1, under the effect of the torque of the barrel, exerts a force F on the blocking surface 23 of the mobile 2
  • This locking surface 23 is arranged so that the direction of the force F passes substantially in the vicinity of the center of the mobile 2, therefore, the escape wheel is locked and immobilizes the mobile 2 and the mobile 3 via toothed structures 24 and 34.
  • the escapement device has two active alternations per oscillation period of the balance spring and that the escape wheel advances at each alternation by an angle equal to 180 ° / N, where N is the number teeth of the escape wheel; moreover, the same tooth of the escape wheel is locked successively on the locking surface 33 and 23. It can be deduced from this that the angle between the locking points on the surfaces 33 and 23 with respect to the center of rotation of the wheel exhaust is also equal to 180 ° / N.
  • the figure 12 represents in plan and in perspective the mobile 2 of the exhaust of the figure 1 .
  • the locking surface 23 is constituted by a plane whose normal to the locking point passes substantially in the vicinity of the center of rotation of the mobile 2. It is also possible to obtain the same effect by replacing this plane by a cylindrical surface whose axis of the cylinder passes through the center of rotation of the mobile 2.
  • the surfaces mentioned above allow the locking of the escape wheel, they do not guarantee precisely the blocking position due to bounce due to the shock between the tooth of the wheel exhaust with the blocking surface, at the end of the energy transmission phase and just before the rest phase.
  • an embodiment of the blocking surface 23, shown in FIG. figure 13 is to replace this plane by a concave surface.
  • the figure 15 represents the case where the pitch diameters (Dp) of the gears 24 and 34 are equal, in order to minimize the differences in inertia between the two mobiles 2 and 3.
  • the Figures 16 and 17 represent a variant of the blocking surface respectively of the second and the first mobile, where these surfaces are concave and formed by two secant planes and inclined by an angle v, to provide blocking security in the case of a shock or a rebound of the escape wheel 1 on one of the first or second mobiles 2 or 3.
  • the relative angular position of the escape wheel 1 relative to the first and second mobile 2 and 3 is guaranteed and there is no possibility of inadvertent rotation.
  • the figure 18 represents a variant of the blocking surface 33 of the second mobile.
  • the plane n represents the plane normal to the vertical surface passing through the locking point between the second mobile 3 and the escape wheel 1 and the center of rotation of the second mobile 3.
  • the first plane of the locking surface 33 makes a angle ⁇ with respect to plane n.
  • a non-zero angle ⁇ provides better resistance to the impact of the escape wheel, against it causes a recoil of the escape wheel during release and therefore a loss of energy at the release.
  • the second locking plane is at an angle ⁇ relative to plane n.
  • a large value of ⁇ makes it possible to improve the blocking precision, on the other hand it causes a large rebound of the escape wheel 1 before the blockage.

Landscapes

  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Transmission Devices (AREA)
  • Medicines Containing Antibodies Or Antigens For Use As Internal Diagnostic Agents (AREA)

Claims (8)

  1. Hemmungsvorrichtung eines Uhrwerks mit zwei zwischen einer Unruhrolle (4) und einem Hemmungsrad (1) aktiven Halbschwingungen, umfassend:
    - ein erstes Drehteil (2),
    - ein zweites Drehteil (3),
    - das Hemmungsrad (1), das einem im Wesentlichen konstanten mechanischen Moment ausgesetzt und ausgebildet ist, um abwechselnd mechanische Energie an das erste Drehteil (2) und an das zweite Drehteil (3) zu übertragen,
    - Mittel für die mechanische Übertragung (24, 34) zwischen dem ersten Drehteil (2) und dem zweiten Drehteil (3),
    - Mittel für die mechanische Übertragung (22) und Blockiermittel (23) zwischen dem Hemmungsrad (1) und dem ersten Drehteil (2),
    - Mittel für die mechanische Übertragung (32) und Blockiermittel (33) zwischen dem Hemmungsrad (1) und dem zweiten Drehteil (3),
    - Mittel für die mechanische Übertragung (35) zwischen dem zweiten Drehteil (3) und der Unruhrolle (4),
    wobei die Blockiermittel (23) des ersten Drehteils (2) von einer Blockierfläche (23) gebildet sind, die ausgebildet ist, damit die vom Hemmungsrad (1) auf diese Blockierfläche (23) übertragene Kraft etwa in der Nähe des Rotationszentrums des ersten Drehteils (2) verläuft,
    wobei die Blockiermittel (33) des zweiten Drehteils (3) von einer Blockierfläche (33) gebildet sind, die ausgebildet ist, damit die vom Hemmungsrad (1) auf diese Blockierfläche (33) übertragene Kraft etwa in der Nähe des Rotationszentrums des Drehteils (3) verläuft,
    wobei die Mittel für die mechanische Übertragung des ersten Drehteils (2) von einer Antriebsfläche (22) gebildet sind, die an der Blockierfläche (23) angrenzend ausgebildet ist und derart, dass ein Außenwinkel α2, der von der Blockierfläche (23) des ersten Drehteils (2) in Richtung der Antriebsfläche (22) des ersten Drehteils (2) reicht, dasselbe Zeichen wie der Rotationswinkel des Hemmungsrads (1) hat,
    wobei die Mittel für die mechanische Übertragung des zweiten Drehteils (3) von einer Antriebsfläche (32) gebildet sind, die an der Blockierfläche (33) angrenzend ausgebildet ist und derart, dass ein Außenwinkel α3, der von der Blockierfläche (33) des zweiten Drehteils (3) in Richtung der Antriebsfläche (32) des zweiten Drehteils (3) reicht, dasselbe Zeichen wie der Rotationswinkel des Hemmungsrads (1) hat,
    dadurch gekennzeichnet, dass die Blockierflächen (23, 33) des ersten Drehteils (2) und des zweiten Drehteils (3) konkave Flächen sind.
  2. Hemmungsvorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass das Hemmungsrad (1), das erste Drehteil (2), das zweite Drehteil (3) und die Unruhrolle (4) auf derselben medianen Ebene ausgebildet sind.
  3. Hemmungsvorrichtung nach Anspruch 1 oder nach Anspruch 2, dadurch gekennzeichnet, dass das Hemmungsrad (1) eine Anzahl von Zähnen (N) aufweist und dass der vom Hemmungsrad (1) zwischen dem Blockierpunkt auf der Fläche (33) und dem Blockierpunkt auf der Fläche (23) durchlaufene Winkel im Verhältnis zum Rotationszentrum des Hemmungsrads (1) gleich 180°/N ist.
  4. Hemmungsvorrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die Blockierflächen (23, 33) des ersten Drehteils (2) und des zweiten Drehteils (3) zylindrische Flächen sind.
  5. Hemmungsvorrichtung nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass die Anzahl der Zähne des Hemmungsrads (1) kleiner oder gleich 6 ist.
  6. Hemmungsvorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass Mittel für die mechanische Übertragung (24, 34) zwischen dem ersten Drehteil (2) und dem zweiten Drehteil (3) von Getrieben gebildet sind, die denselben Teilkreisdurchmesser besitzen.
  7. Hemmungsvorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass die Blockierflächen (23, 33) des ersten Drehteils (2) und des zweiten Drehteils (3) von zwei Ebenen gebildet sind, deren Außenwinkel ν zwischen ihnen zwischen 120° und 170° inklusive ist.
  8. Uhr, die mit einer Hemmungsvorrichtung nach einem der vorangehenden Ansprüche ausgestattet ist.
EP12726440.6A 2012-06-07 2012-06-07 Hemmungsvorrichtung für eine uhr Active EP2859411B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2012/060825 WO2013182243A1 (fr) 2012-06-07 2012-06-07 Dispositif d'echappement pour piece d'horlogerie

Publications (2)

Publication Number Publication Date
EP2859411A1 EP2859411A1 (de) 2015-04-15
EP2859411B1 true EP2859411B1 (de) 2016-10-12

Family

ID=46229502

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12726440.6A Active EP2859411B1 (de) 2012-06-07 2012-06-07 Hemmungsvorrichtung für eine uhr

Country Status (5)

Country Link
US (1) US9052694B2 (de)
EP (1) EP2859411B1 (de)
JP (1) JP5961753B2 (de)
CN (1) CN104364719B (de)
WO (1) WO2013182243A1 (de)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108700845B (zh) * 2015-12-21 2020-08-04 迪特拉有限公司 钟表擒纵装置和该装置的操作方法
EP3306416B1 (de) * 2016-10-04 2019-08-21 ETA SA Manufacture Horlogère Suisse Mechanisches uhrwerk mit erfassung der gangreserve
EP3462251B1 (de) * 2017-09-29 2020-06-10 Montres Breguet S.A. Stellmechanismus für uhrwerk
NL2020384B1 (en) * 2018-02-06 2019-08-14 Flexous Mech Ip B V Mechanical watch oscillator
EP3844572A1 (de) 2018-08-28 2021-07-07 Rolex Sa Anker für die uhrmacherei
JP7485506B2 (ja) 2018-10-12 2024-05-16 ロレックス・ソシエテ・アノニム 小型時計ムーブメント用の調速装置

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US3143848A (en) * 1957-01-02 1964-08-11 Hamilton Watch Co Indexing mechanism
US3538705A (en) * 1968-11-07 1970-11-10 Hamilton Watch Co Escapement
DE2458503A1 (de) * 1974-12-11 1976-06-16 Graesslin Feinwerktech Hemmung, insbesondere fuer zeitlaufwerke
EP0018796B1 (de) 1979-04-30 1984-11-07 George Daniels Uhren, Pendeluhren, Chronometer und Hemmungen dafür
EP1041459B1 (de) * 1999-03-31 2002-09-18 Ulysse Nardin S.A. Hemmung für Zeitmesser
US6712500B2 (en) * 2000-04-11 2004-03-30 Detra Sa Escapement device for timepiece
EP1276021B1 (de) * 2001-06-26 2008-12-31 Ulysse Nardin S.A. Hemmung für einen Zeitmesser
ATE443880T1 (de) * 2002-05-28 2009-10-15 Manuf Et Fabrique De Montres E Hemmung für uhren
WO2006099882A1 (fr) * 2005-03-23 2006-09-28 Marblia Ltd Mouvement pour piece d’horlogerie
ATE390653T1 (de) * 2005-03-30 2008-04-15 Montres Breguet Sa Chronometerhemmung für uhren
ATE470890T1 (de) * 2005-03-30 2010-06-15 Montres Breguet Sa Uhr mit mindenstens zwei reguliersystemen
ATE433136T1 (de) * 2007-03-09 2009-06-15 Eta Sa Mft Horlogere Suisse Hemmung mit tangentialimpulsen
DE602007003445D1 (de) * 2007-04-18 2010-01-07 Eta Sa Mft Horlogere Suisse Hemmung, die zwei Hemmungsräder umfasst
CH702313B1 (fr) * 2007-05-14 2011-06-15 Hugues Jolidon Echappement pour instrument horaire.
FR2928015B1 (fr) 2008-02-22 2010-02-19 Jean Paul Lenoble Echappement perfectionne a ancre articulee a impulsion tangentielle, montre mecanique
EP2166419B1 (de) * 2008-09-18 2013-06-26 Agenhor SA Uhrwerk, das eine Konstantkraftvorrichtung aufweist
IT1396734B1 (it) 2009-11-25 2012-12-14 Ferrara Scappamento per orologeria ad alto rendimento.

Also Published As

Publication number Publication date
EP2859411A1 (de) 2015-04-15
US20150131414A1 (en) 2015-05-14
WO2013182243A1 (fr) 2013-12-12
US9052694B2 (en) 2015-06-09
JP5961753B2 (ja) 2016-08-02
JP2015518965A (ja) 2015-07-06
CN104364719B (zh) 2017-03-15
CN104364719A (zh) 2015-02-18

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