EP1736838A1 - Hemmung und Oszillator für Uhren - Google Patents

Hemmung und Oszillator für Uhren Download PDF

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Publication number
EP1736838A1
EP1736838A1 EP05105626A EP05105626A EP1736838A1 EP 1736838 A1 EP1736838 A1 EP 1736838A1 EP 05105626 A EP05105626 A EP 05105626A EP 05105626 A EP05105626 A EP 05105626A EP 1736838 A1 EP1736838 A1 EP 1736838A1
Authority
EP
European Patent Office
Prior art keywords
wheel
resonator
balance
pallets
escapement
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.)
Granted
Application number
EP05105626A
Other languages
English (en)
French (fr)
Other versions
EP1736838B1 (de
Inventor
Pierre-Marcel Genequand
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.)
Centre Suisse dElectronique et Microtechnique SA CSEM
Original Assignee
Centre Suisse dElectronique et Microtechnique SA CSEM
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 Centre Suisse dElectronique et Microtechnique SA CSEM filed Critical Centre Suisse dElectronique et Microtechnique SA CSEM
Priority to AT05105626T priority Critical patent/ATE389902T1/de
Priority to DE602005005465T priority patent/DE602005005465T2/de
Priority to EP05105626A priority patent/EP1736838B1/de
Publication of EP1736838A1 publication Critical patent/EP1736838A1/de
Priority to HK07103235A priority patent/HK1096164A1/xx
Application granted granted Critical
Publication of EP1736838B1 publication Critical patent/EP1736838B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • G04B15/12—Adjusting; Restricting the amplitude of the lever or the like

Definitions

  • the present invention relates to the field of watchmaking and more particularly to escapements, which are mechanisms transforming a rotational movement into a reciprocating movement.
  • the rotational movement is generated by a power source, usually a weight or a spring, driving a gear train.
  • a power source usually a weight or a spring
  • This energy is transmitted, in pulses, to a resonator, which can be a balance spring or a pendulum.
  • the Swiss lever escapement is the most frequently used. It includes an escape wheel and an anchor, and maintains a balance wheel.
  • the anchor cooperates with the latter and provides it with energy at each alternation, during each passage through its dead point. Outside the impulse phases, the pendulum oscillates freely. In this way, its sinusoidal motion is only slightly affected by friction.
  • This type of exhaust equips the vast majority of mechanical watches currently manufactured.
  • a first object of the present invention is to significantly reduce these energy losses by eliminating the drop angle of the exhausts free or sliding friction rubbing rest exhausts. This object is achieved thanks to the fact that the escapement according to the invention does not generate sliding friction under load outside the pulse periods, although it is permanently connected to the balance.
  • the escapement according to the invention is intended to equip a timepiece comprising a frame, a rocker, an elastic member cooperating with the balance to form a resonator, a source of mechanical energy and a gear driven by the energy source.
  • the transmission member comprises a body and two resilient blades, which are secured to it by one of their ends and which are each provided with a pallet at the other end, and in that that the toothing of the wheel forms a succession of support points arranged to cooperate successively with the pallets to transmit the energy of the gear to the resonator.
  • a second object of the present invention is to avoid sliding friction also during the driving pulse, and thus allow operation without lubrication.
  • the bearing points and the pallets are arranged to cooperate with each other in a rolling frictional movement.
  • the pallets form a knife in their portion intended to cooperate with the toothing at the points of support.
  • the end of the knife thus pivots in the bottom of the fulcrum with which it cooperates, almost without sliding.
  • the transmission member is in constant contact with the balance, but the pallets do not rub on the teeth of the wheel. This result is obtained thanks to the fact that the elastic blades deform while their end provided with a pallet pivots while rolling on the point of support.
  • the escapement according to the invention may further comprise abutments, integral with the frame, which limit the amplitude of these blades when the pallets are no longer in position. contact with the teeth.
  • the present invention also relates to a mechanical oscillator comprising an escapement as defined above.
  • the pendulum oscillates at a frequency of the order of a few Hertz, generally at 2.5 Hz, 3 Hz or 4 Hz, for a typical amplitude of 220 ° in vertical position.
  • the amplitude is chosen so as to ensure an isochronism defect as low as possible.
  • the ratio between the oscillation angle and the pulse angle decreases substantially, which causes a loss in the accuracy of the watch.
  • a gain due to the frequency increase is therefore illusory because of other parameters that affect the accuracy of the movement.
  • the escapements with rubbing rest are generally found in the clocks equipped with a pendulum.
  • the amplitude of the latter is a few degrees, so that the angle traveled after the pulse is relatively small.
  • the friction can be considered as generally low.
  • the frequency of the pendulum inversely proportional to the square root of its length, can not be increased beyond a few Hertz.
  • a third object of the present invention is therefore to provide an oscillator in the balance of which the power dissipated is reduced by a decrease in its amplitude, the accuracy is improved by an increase in its frequency, and the efficiency of the exhaust is increased.
  • the amplitude of the balance should be higher, typically from 5 to 50 degrees, or if it was desired to maintain a certain elasticity between the body and the balance, it would be advantageous to fix the body on the elastic member in one point between its point of attachment to the pendulum and its anchorage point to the frame.
  • the increase in the frequency corresponds to an increase in the rigidity of the elastic return member of the balance, which is proportional to the square of the frequency.
  • Such an increase in rigidity combined with the reduction of the amplitude, makes it possible to suspend the balance directly by the elastic member, thus eliminating the friction of the pivots.
  • the balance thus suspended elastically is able to maintain an excellent amplitude decrement value per cycle and up to a very low level of amplitude.
  • the oscillator may be provided with a regulator member movably mounted on the frame and whose position is a function of the engine torque of the energy source. It is arranged to cooperate with the spring of the elastic member to vary its active length.
  • the correction of the isochronism can be ensured by a second spring that comprises the elastic member, fixed to the balance by one of its ends, its median part cooperating with said regulating member.
  • the timepiece movement shown diagrammatically in FIG. 1 comprises a barrel 10, a finishing wheel 12 comprising an hour wheel 14, an average wheel 16, and a seconds wheel 18, an escapement 20 and a resonator 22 These different constituents are arranged on a frame that has not been shown.
  • the resilient blades 26a and 26b are fixed at one of their ends on the body 26c, which is rigidly mounted on the arm 28b. They behave like articulated arms with elastic return. Alternatively, the body 26c can be made in one piece with the arm 28b.
  • the blades 26a and 26b are each provided, at their end opposite the body 26c, a pallet 32 (see Figure 2b), intended to cooperate with the wheel 24b, formed by the blade itself or by an insert, preferably hard material such as ruby.
  • the wheel 24b comprises a board bearing teeth respectively referenced 24c and 24d, interconnected by a serge 24e.
  • the teeth extend radially from the serge, one 24c inwardly, the other 24d outwardly. More precisely, the toothing 24d is in the thickness of the board, while the toothing 24c is in excess thickness.
  • Such a wheel may, for example, be made of silicon, by etching or nickel alloy and phosphor by electrolytic growth.
  • the teeth are of triangular shape, with a small side 24f with a substantially radial orientation, defining the height of the tooth. Two successive teeth of the same toothing are separated by a space approximately equal to the width of a tooth.
  • the pitch is of the order of the oscillation amplitude of the pallets in the absence of interaction with the toothing.
  • the small side 24f is about 20% of the pace.
  • the intersecting lines of the serge 24e and the short sides 24f of the teeth constitute support points 24g against which the pallets 32 are leant.
  • the pallets 32 have an apex angle smaller than the angle made by the seam 24e and the side 24f. In this way, these pallets can rotate by rolling in the support points 24g, thus working as knives, in the sense that it is heard in the pendulums pendulums.
  • the teeth of the teeth 24c and 24d are offset by a half-step, while the pallets 32 are aligned radially. In this way, the two vanes cooperate by alternating identical sequences of half a cycle with the wheel 24b.
  • the barrel induces a maintenance torque tending to turn the escapement wheel 24 clockwise.
  • the teeth 24d and applies a force on the pallet 32b tending to amplify the movement of the balance. In other words, the applied torque provides energy to the pendulum.
  • the wheel 24 rotates and drives the rocker 28 and the blades 26a and 26b to occupy the position of Figure 3a.
  • the pallet 32a has come into contact with the serge 24e, it slips there, with an extremely low friction, the pressure being very light, until it leans against a fulcrum 24g of the toothing 24c.
  • the rocker 28 has reached its maximum amplitude and comes back, pushed by the pallet 32a.
  • the pallet 32b then passes the tooth against which it was resting (FIG. 3c) and comes into contact with the serge 24e, as represented in FIG. 3d.
  • the pendulum continues its oscillation until the pallet 32b comes back against the fulcrum 24g of the next tooth and pushes the wheel 24 as had the pallet 32a during the previous alternation.
  • the exhaust shown in Figure 4 also comprises a wheel 24b and a transmission member 26, provided with two flexible blades 26a and 26b and a body 26c.
  • the latter comprises two arms arranged on either side of a pivot point 26d located at the intersection of the tangents to the wheel, each arm carrying one of the blades.
  • the blades are in contact with the wheel at points distant, for example, of about 90 ° and both make an angle of about 45 ° with a tangent to the wheel 24b, which has only external toothing.
  • the blades 26a and 26b are arranged in such a way that the torque generated by the wheel on the member 26 is substantially the same, for the two blades 26a and 26b.
  • the rocker 28 is of conventional type, that is to say pivotally mounted on the frame, by means of a shaft engaged in bearings. Since such an escapement makes it possible to work at relatively high frequencies, and also at relatively low amplitudes, it is advantageous to also remove the friction of the balance on its pivots, by the amount disposed on an elastic structure such as that illustrated in FIGS. , 6a and 6b.
  • a frame 50 carries a rocker 52 by means of four U-shaped springs 54.
  • the rocker 52 comprises a central body 52a, two arms 52b and two masses of inertia 52c.
  • the body 52a extends axially on both sides of the arms 52b. It is in the shape of a truncated cylinder, the cylindrical parts being at the right of the arms, the flat parts in their extension.
  • the four springs 54 are fixed to the body 52a, arranged symmetrically with respect to the axis of the body 52a and with respect to a plane passing through the middle of the arms 52b.
  • the arms 52b carry, in the vicinity of their ends, on opposite faces and at different levels, resilient blades 56 cooperating with an escape wheel 58.
  • the arms 52b therefore perform the same function as the body 26c in the embodiment of Figures 1 and 2.
  • the blades 56 and the wheel 58 may be in all respects similar to the blades 26 and the wheel 24b described with reference to Figures 2 and 3. They will therefore not be described in more detail.
  • the balance freely oscillates, suspended by the springs 54 which, by their shape, provide the rigidity of the assembly for degrees of freedom other than the nominal pivoting. It can however be It is conceivable to provide (see Fig. 6b) shock-absorbing plugs 60, fixed in axially-oriented cylindrical holes 52d, which comprise the ends of the body 52a, and engaged with a certain play in abutments 61 integral with the frame 50.
  • each of the two levels of springs 54 would be advantageous, both in terms of the reduction of friction of the structure in terms of simplification of assembly.
  • a single level of springs is also possible.
  • This level can also be monolithic and be designed so that its transverse rigidity is sufficient to prevent any movement other than the desired rotation of the balance.
  • the shape of these springs should be such that the sources of friction at their attachment points, on the balance or on the frame, are minimized.
  • the resilient blades may have a sectional variation or be perpendicular to the parts used to fix them.
  • FIG. 7 represents a device making it possible to adjust the frequency as well as the isochronism of the oscillator.
  • This device takes into account the variation of the torque applied by the barrel on the gear train and that applied by the latter on the escapement and the balance. It comprises, mounted rigidly on the rocker arm 52, a radially extending elastic arm 62 whose torque generated for a given armoring angle is two to four orders of magnitude less than the torque generated by the springs 54.
  • this device comprises a spring 64 rigidly mounted on the frame 50 and carrying at its free end a pawl 65 engaged in a ratchet wheel 66 which provides the winding of the mainspring. Under the effect of the mainspring, and via the pawl 65, the spring 64 bends, so that its position is a function of the degree of arming.
  • a carriage 68 is slidably mounted on the frame 50, in a direction parallel to the orientation of the arm 62. It carries two elastic blades 69 each comprising a finger 70 intended to cooperate with the elastic arm 62.
  • a pantograph 72 pivotally mounted on the frame 50 by a vertex of its parallelogram, is connected to the spring 64 by the opposite vertex.
  • the arms 72a of the pantograph 72 which intersect at their pivot point, extend towards the carriage 68. Their ends bear pins 72b adjacent to the blades 69.
  • the carriage 68 To adjust the frequency of the oscillator, simply move the carriage 68 in the direction of the double arrow shown in the drawing, which has the effect of varying the active length of the elastic arm 62.
  • the carriage is advantageously moved by means of a worm screw, not shown in the drawing.
  • This arm 62 is active only when it bears against one of the fingers 70. Also, by more or less spacing the fingers 70, it is possible to vary the elastic moment of the resonator as a function of the amplitude the balance, which is a function of the engine torque.
  • FIG. 8 The embodiment shown in FIG. 8 is similar to that of FIGS. 1 to 3.
  • the transmission member 26 is not fixed on the balance 28. It is pivotally mounted on the balance by means of FIG. a ball bearing 73, coaxially with the balance 28.
  • a hairspring 30a fixed at one end to a ferrule not visible in the drawing and mounted on the balance shaft, and at the other end to a peg 74 integral with the body 26c, elastically connects the latter to the balance 28.
  • a leaf spring 30b rigidly fixed to the pin 74 is limited in its movement by two pins 75 fixed to the frame.
  • This last figure clearly shows the division of the elastic member into two parts connected in series; one, the spiral spring 30a connects the transmission body 26c to the balance, and the other, the blade 30b, connects the body 26c to the frame by the pins 75.
  • the leaf spring 30b could also provide the function of the arm 62, described with reference to FIG.
  • the transmission member cooperate with the elastic member, either by fixing the blades directly on the elastic member or by cooperating with a pivoting transmission member. on the frame and driven by one of the blades of the elastic member, in its middle part.
  • the pallets have a concave portion performing the function of rolling friction in cooperation with the bearing points of the toothing constituted by the outgoing edges of the teeth, which thus act as knives pivoting in the hollow of the pallets.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Micromachines (AREA)
  • Electric Clocks (AREA)
  • Transmission Devices (AREA)
  • Gears, Cams (AREA)
EP05105626A 2005-06-23 2005-06-23 Uhr Active EP1736838B1 (de)

Priority Applications (4)

Application Number Priority Date Filing Date Title
AT05105626T ATE389902T1 (de) 2005-06-23 2005-06-23 Uhr
DE602005005465T DE602005005465T2 (de) 2005-06-23 2005-06-23 Uhr
EP05105626A EP1736838B1 (de) 2005-06-23 2005-06-23 Uhr
HK07103235A HK1096164A1 (en) 2005-06-23 2007-03-27 Timepiece

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP05105626A EP1736838B1 (de) 2005-06-23 2005-06-23 Uhr

Publications (2)

Publication Number Publication Date
EP1736838A1 true EP1736838A1 (de) 2006-12-27
EP1736838B1 EP1736838B1 (de) 2008-03-19

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Family Applications (1)

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EP05105626A Active EP1736838B1 (de) 2005-06-23 2005-06-23 Uhr

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EP (1) EP1736838B1 (de)
AT (1) ATE389902T1 (de)
DE (1) DE602005005465T2 (de)
HK (1) HK1096164A1 (de)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2090941A1 (de) 2008-02-18 2009-08-19 CSEM Centre Suisse d'Electronique et de Microtechnique SA Recherche et Développement Mechanischer Oszillator
EP2273323A2 (de) 2009-07-10 2011-01-12 Manufacture et fabrique de montres et chronomètres Ulysse Nardin Le Locle SA Mechanischer Oszillator
EP2290476A1 (de) 2009-08-18 2011-03-02 CSEM Centre Suisse d'Electronique et de Microtechnique SA - Recherche et Développement Isochronismuskorrektor für Uhrhemmungsmechanismus und mit einem solchen Korrektor ausgestatteter Hemmungsmechanismus
EP2309344A3 (de) * 2007-12-27 2011-05-04 Chopard Technologies SA Verfahren zur Veränderung der Oszillationsfrequenz eines Uhrwerks
US8342739B2 (en) 2007-12-27 2013-01-01 Chopard Technologies Sa Horological movement comprising a high oscillation frequency regulating device
EP2911012A1 (de) 2014-02-20 2015-08-26 CSEM Centre Suisse d'Electronique et de Microtechnique SA - Recherche et Développement Oszillator einer Uhr
EP3076245A1 (de) 2015-04-02 2016-10-05 CSEM Centre Suisse D'electronique Et De Microtechnique SA Dämpfungsvorrichtung, insbesondere für mikromechanische uhrkomponente
EP3182213A1 (de) 2015-12-16 2017-06-21 Société anonyme de la Manufacture d'Horlogerie Audemars Piguet & Cie Einstellmechanismus der mittleren geschwindigkeit in einem uhrwerk, und entsprechendes uhrwerk
EP3182214A1 (de) 2015-12-16 2017-06-21 Société anonyme de la Manufacture d'Horlogerie Audemars Piguet & Cie Mechanischer oszillator für eine uhr, regulierungsmechanismus, der diesen mechanischen oszillator umfasst, und entsprechendes uhrwerk
FR3048791A1 (fr) * 2016-03-14 2017-09-15 Lvmh Swiss Mft Sa Mecanisme pour piece d'horlogerie et piece d'horlogerie comprenant un tel mecanisme
FR3048792A1 (fr) * 2016-03-14 2017-09-15 Lvmh Swiss Mft Sa Dispositif pour piece d'horlogerie, mouvement horloger et piece d'horlogerie comprenant un tel dispositif
WO2017157870A1 (fr) * 2016-03-14 2017-09-21 Lvmh Swiss Manufactures Sa Dispositif pour pièce d'horlogerie, mouvement horloger et pièce d'horlogerie comprenant un tel dispositif
EP2363762B1 (de) * 2010-03-04 2017-11-22 Montres Breguet SA Uhr mit einem mechanischen Hochfrequenzuhrwerk
EP3276431A1 (de) 2016-07-27 2018-01-31 Cartier International AG Mechanischer oszillator für uhrwerk
EP3686693A1 (de) 2019-01-24 2020-07-29 CSEM Centre Suisse d'Electronique et de Microtechnique SA - Recherche et Développement Mechanische uhr-regulierungsvorrichtung
EP3722888A1 (de) 2019-04-09 2020-10-14 Ecole Polytechnique Fédérale de Lausanne (EPFL) Mechanischer oszillator mit abstimmbarem isochronismusmangel
US20230000492A1 (en) * 2021-06-30 2023-01-05 Covidien Lp Surgical stapling apparatus with firing lockout assembly
US12055896B2 (en) 2016-12-23 2024-08-06 Manufacture D'horlogerie Audemars Piguet Sa Flexible monolithic component for a timepiece

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2818941A1 (de) † 2010-04-01 2014-12-31 Rolex Sa Blockiervorrichtung für Zahnrad

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US31999A (en) * 1861-04-09 Watch-escapement
US628758A (en) * 1897-10-27 1899-07-11 Arthur Victor Chardon Chronometer-escapement.
GB574229A (en) * 1943-11-13 1945-12-28 Thomas Alfred Gummersall A silent lever escapement
FR1009853A (fr) * 1948-07-02 1952-06-04 Mécanisme d'échappement perfectionné
CH286913A (de) * 1949-02-16 1952-11-15 Siemens Ag Uhrengangregler mit einem im Gangreglertakt bewegten Steigrad.
DE1773360A1 (de) * 1968-03-13 1971-09-23 Karl Gruttmann Antriebs- und Hemmungselement fuer Gangregler bei Uhren oder aehnlichen Apparaten

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US31999A (en) * 1861-04-09 Watch-escapement
US628758A (en) * 1897-10-27 1899-07-11 Arthur Victor Chardon Chronometer-escapement.
GB574229A (en) * 1943-11-13 1945-12-28 Thomas Alfred Gummersall A silent lever escapement
FR1009853A (fr) * 1948-07-02 1952-06-04 Mécanisme d'échappement perfectionné
CH286913A (de) * 1949-02-16 1952-11-15 Siemens Ag Uhrengangregler mit einem im Gangreglertakt bewegten Steigrad.
DE1773360A1 (de) * 1968-03-13 1971-09-23 Karl Gruttmann Antriebs- und Hemmungselement fuer Gangregler bei Uhren oder aehnlichen Apparaten

Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8628234B2 (en) 2007-12-27 2014-01-14 Chopard Technologies Sa Horological movement comprising a high oscillation frequency regulating device
US8342739B2 (en) 2007-12-27 2013-01-01 Chopard Technologies Sa Horological movement comprising a high oscillation frequency regulating device
US8662741B2 (en) 2007-12-27 2014-03-04 Chopard Technologies Sa Horological movement comprising a high oscillation frequency regulating device
EP2309344A3 (de) * 2007-12-27 2011-05-04 Chopard Technologies SA Verfahren zur Veränderung der Oszillationsfrequenz eines Uhrwerks
EP2090941A1 (de) 2008-02-18 2009-08-19 CSEM Centre Suisse d'Electronique et de Microtechnique SA Recherche et Développement Mechanischer Oszillator
US7963693B2 (en) 2008-02-18 2011-06-21 Csem Centre Suisse D'electronique Et De Microtechnique Sa-Recherche Et Developpement Mechanical oscillator
EP2273323A2 (de) 2009-07-10 2011-01-12 Manufacture et fabrique de montres et chronomètres Ulysse Nardin Le Locle SA Mechanischer Oszillator
EP2290476A1 (de) 2009-08-18 2011-03-02 CSEM Centre Suisse d'Electronique et de Microtechnique SA - Recherche et Développement Isochronismuskorrektor für Uhrhemmungsmechanismus und mit einem solchen Korrektor ausgestatteter Hemmungsmechanismus
US8672536B2 (en) 2009-08-18 2014-03-18 CSEM Central Suisse d'Electronique et de Microtechnique SA—Recherche et Development Isochronism corrector for clockwork escapement and escapement provided with such a corrector
EP2363762B1 (de) * 2010-03-04 2017-11-22 Montres Breguet SA Uhr mit einem mechanischen Hochfrequenzuhrwerk
US9207641B2 (en) 2014-02-20 2015-12-08 Csem Centre Suisse D'electronique Et De Microtechnique Sa—Recherche Et Developpement Timepiece oscillator
EP2911012A1 (de) 2014-02-20 2015-08-26 CSEM Centre Suisse d'Electronique et de Microtechnique SA - Recherche et Développement Oszillator einer Uhr
EP3076245A1 (de) 2015-04-02 2016-10-05 CSEM Centre Suisse D'electronique Et De Microtechnique SA Dämpfungsvorrichtung, insbesondere für mikromechanische uhrkomponente
US10452027B2 (en) 2015-04-02 2019-10-22 CSEM Centre Suisse d'Electronique et de Microtechnique SA—Recherche et Développement Shock-absorber device, in particular for a micromechanical clockwork component
WO2017102916A1 (fr) 2015-12-16 2017-06-22 Société Anonyme de la Manufacture d'Horlogerie Audemars Piguet & Cie Mécanisme de réglage d'une vitesse moyenne dans un mouvement d'horlogerie et mouvement d'horlogerie
EP3182214A1 (de) 2015-12-16 2017-06-21 Société anonyme de la Manufacture d'Horlogerie Audemars Piguet & Cie Mechanischer oszillator für eine uhr, regulierungsmechanismus, der diesen mechanischen oszillator umfasst, und entsprechendes uhrwerk
EP3182213A1 (de) 2015-12-16 2017-06-21 Société anonyme de la Manufacture d'Horlogerie Audemars Piguet & Cie Einstellmechanismus der mittleren geschwindigkeit in einem uhrwerk, und entsprechendes uhrwerk
CN108475039A (zh) * 2015-12-16 2018-08-31 爱彼钟表业制造有限公司 钟表机芯中用于调节平均速度的机构以及钟表机芯
WO2017157870A1 (fr) * 2016-03-14 2017-09-21 Lvmh Swiss Manufactures Sa Dispositif pour pièce d'horlogerie, mouvement horloger et pièce d'horlogerie comprenant un tel dispositif
FR3048791A1 (fr) * 2016-03-14 2017-09-15 Lvmh Swiss Mft Sa Mecanisme pour piece d'horlogerie et piece d'horlogerie comprenant un tel mecanisme
WO2017157868A1 (fr) * 2016-03-14 2017-09-21 Lvmh Swiss Manufactures Sa Mécanisme pour pièce d'horlogerie et pièce d'horlogerie comprenant un tel mécanisme
FR3048792A1 (fr) * 2016-03-14 2017-09-15 Lvmh Swiss Mft Sa Dispositif pour piece d'horlogerie, mouvement horloger et piece d'horlogerie comprenant un tel dispositif
US11029649B2 (en) 2016-03-14 2021-06-08 LVHM Swiss Manufactures SA Device for timepiece, clockwork movement and timepiece comprising such a device
US11460811B2 (en) 2016-03-14 2022-10-04 Lvmh Swiss Manufactures Sa Mechanism for a timepiece and timepiece comprising such a mechanism
EP3276431A1 (de) 2016-07-27 2018-01-31 Cartier International AG Mechanischer oszillator für uhrwerk
US12055896B2 (en) 2016-12-23 2024-08-06 Manufacture D'horlogerie Audemars Piguet Sa Flexible monolithic component for a timepiece
EP3686693A1 (de) 2019-01-24 2020-07-29 CSEM Centre Suisse d'Electronique et de Microtechnique SA - Recherche et Développement Mechanische uhr-regulierungsvorrichtung
EP3722888A1 (de) 2019-04-09 2020-10-14 Ecole Polytechnique Fédérale de Lausanne (EPFL) Mechanischer oszillator mit abstimmbarem isochronismusmangel
US20230000492A1 (en) * 2021-06-30 2023-01-05 Covidien Lp Surgical stapling apparatus with firing lockout assembly
US11602344B2 (en) * 2021-06-30 2023-03-14 Covidien Lp Surgical stapling apparatus with firing lockout assembly

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Publication number Publication date
EP1736838B1 (de) 2008-03-19
DE602005005465T2 (de) 2009-04-09
DE602005005465D1 (de) 2008-04-30
HK1096164A1 (en) 2007-05-25
ATE389902T1 (de) 2008-04-15

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