EP1736838B1 - Uhr - Google Patents

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Publication number
EP1736838B1
EP1736838B1 EP05105626A EP05105626A EP1736838B1 EP 1736838 B1 EP1736838 B1 EP 1736838B1 EP 05105626 A EP05105626 A EP 05105626A EP 05105626 A EP05105626 A EP 05105626A EP 1736838 B1 EP1736838 B1 EP 1736838B1
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EP
European Patent Office
Prior art keywords
wheel
balance
organ
timepiece according
elastic
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
EP05105626A
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English (en)
French (fr)
Other versions
EP1736838A1 (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.)
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Publication date
Application filed by Centre Suisse dElectronique et Microtechnique SA CSEM filed Critical Centre Suisse dElectronique et Microtechnique SA CSEM
Priority to EP05105626A priority Critical patent/EP1736838B1/de
Priority to AT05105626T priority patent/ATE389902T1/de
Priority to DE602005005465T priority patent/DE602005005465T2/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
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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 timepieces equipped with an escapement, which is a mechanism transforming a rotational movement into an alternating 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 timepiece of this type is described in the document GB 574229 . It has a free escapement whose anchor is provided with two resilient blades cooperating with the wheel. The presence of elastic blades must reduce the noise of the exhaust. The efficiency of this exhaust is not better than that of other free exhausts, because of the angles of fall.
  • a first object of the present invention is to significantly reduce these energy losses by eliminating the free escapement drop angle or sliding friction rubbing rest exhausts. This object is achieved by virtue of the fact that the active elastic blade cooperates with said wheel by means of a bearing point constituting a pivot point that is almost frictionless and that the transmission member is permanently coupled 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 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 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 low.
  • 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 propose a timepiece equipped with a balance whose dissipated power is reduced by a decrease in its amplitude.
  • the accuracy can be improved by increasing 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 schematically on the figure 1 comprises a barrel 10, a finishing gear train 12 comprising an hour wheel 14, an average wheel 16, and a seconds wheel 18, an escapement 20 and a resonator 22. These various components are arranged on a frame which has no not been represented.
  • the resilient blades 26a and 26b are fixed at one of their ends to 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 half a 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 the 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 supported ( figure 3c ) and comes in contact with the 24th serge, as shown on the figure 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 represented on the 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, about 90 ° and both make an angle of about 45 ° with a tangent to the wheel 24b, which has only an 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 eliminate the friction of the pendulum on its pivots, in the amount arranged on an elastic structure such as that illustrated in the Figures 5, 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 realization of figures 1 and 2 .
  • Blades 56 and wheel 58 may be in all respects similar to blades 26 and wheel 24b described with reference to FIGS. figures 2 and 3 . They will 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.
  • shockproof pins 60 fixed in cylindrical holes 52d, axially oriented, which comprise the ends of the body 52a, and engaged with a certain clearance 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 rotation. desired 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.
  • the figure 7 represents a device for adjusting 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.
  • the embodiment shown at figure 8 is similar to that of Figures 1 to 3 .
  • the transmission member 26 is not fixed on the balance 28. It is pivotally mounted on the balance by means of a ball bearing 73, coaxially with the balance 28.
  • a hairspring 30a fixed by one end to a ferrule not visible in the drawing and mounted on the balance shaft, and the other end to a stud 74 integral with the body 26c, elastically connects the latter to the balance 28.
  • a leaf spring 30b fixed rigidly to the piton 74 is limited in its movement by two pins 75 fixed on the frame.
  • This last figure 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.
  • leaf spring 30b could also provide the function of the arm 62, described with reference to FIG. figure 7 .
  • 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)

Claims (11)

  1. Uhrenstück, einen Rahmen (50), eine Unruh (28; 52), ein elastisches Organ (30; 54), das mit der Unruh zusammenwirkt, um einen Resonator (22) zu bilden, eine Quelle mechanischer Energie (10) und ein von der besagten Energiequelle angetriebenes Räderwerk (12) und eine Hemmung aufweisend, die umfasst:
    - ein Hemmungsdrehteil (24; 58), das mit einem Trieb (24a) in Ineingriffnahme mit einem Drehteil (18) des besagten Räderwerks ausgestattet ist, und einem Rad (24b), das mindestens eine Zahnung (24c, 24d) umfasst, und
    - ein Übertragungsorgan (26, 56), um die Energie vom Hemmungsrad (24b) zum Resonator (22) zu übertragen, wobei das besagte Organ (26, 56) einen Körper (26c; 52b) und zwei elastische Blätter (26a, 26b; 56) umfasst, die mit dem besagten Körper durch eines ihrer Enden verbunden und jeweils mit einer Palette (32) am anderen Ende ausgestattet sind, die mit dem besagten Rad (24b) zusammenwirken, um die Energie an den Resonator zu übertragen,
    dadurch gekennzeichnet, dass das aktive elastische Blatt mit dem besagten Rad über einen Abstützpunkt zusammenwirkt, der einen Drehpunkt bildet, in dem das Ende des besagten Blatts lagert, und dadurch, dass das Übertragungsorgan ständig an den Resonator gekoppelt ist.
  2. Uhrenstück nach Anspruch 1, dadurch gekennzeichnet, dass die besagten Paletten (32) in ihrem Abschnitt, der dazu bestimmt ist, mit der Zahnung an den Abstützpunkten (24g) zusammenzuwirken, eine Klinge bilden.
  3. Uhrenstück nach Anspruch 1, dadurch gekennzeichnet, dass die besagten Abstützpunkte der Zahnung jeweils eine Klinge bilden, die dazu bestimmt ist, mit einem Hohlabschnitt der besagten Paletten (32) zusammenzuwirken.
  4. Uhrenstück nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass es weiterhin mit dem besagten Rahmen verbundene Anschläge (34a, 34b) umfasst, die mit den besagten elastischen Blättern (26a, 26b) zusammenwirken und ihre Schwingungen dämpfen, wenn die Paletten (32) mit der besagten Verzahnung (24c, 24d) nicht im Kontakt sind.
  5. Uhrenstück nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass das besagte Übertragungsorgan (54, 56) an die besagte Unruh (52) gekoppelt ist.
  6. Uhrenstück nach Anspruch 5, dadurch gekennzeichnet, dass die Amplitude der Unruh kleiner oder gleich 5° ist und der Körper (52b) der Hemmung starr an der Unruh (52) befestigt ist.
  7. Uhrenstück nach Anspruch 6, dadurch gekennzeichnet, dass das besagte elastische Organ (30, 54) weiterhin die Aufhängung der Unruh gewährleistet.
  8. Uhrenstück nach einem der Ansprüche 6 und 7, dadurch gekennzeichnet, dass der besagte Resonator weiterhin ein Reglerorgan umfasst, das beweglich auf dem Rahmen befestigt ist und dessen Stellung vom Antriebsmoment der besagten Energiequelle abhängt und aufgebaut ist, um mit dem besagten elastischen Organ (30, 54) zusammenzuwirken, um dessen aktive Dimension zu variieren.
  9. Uhrenstück nach einem der Ansprüche 6 und 7, dadurch gekennzeichnet, dass das elastische Organ weiterhin ein Reglerorgan umfasst, das beweglich auf dem Rahmen befestigt ist und dessen Stellung vom Antriebsmoment der besagten Energiequelle abhängt und eine zweite Feder, die durch eines ihrer Enden an der Unruh befestigt ist, wobei das andere Ende mit dem besagten Reglerorgan zusammenwirkt.
  10. Uhrenstück nach Anspruch 1, dadurch gekennzeichnet, dass das besagte Übertragungsorgan (26) an das besagte elastische Organ (30) gekoppelt ist.
  11. Uhrenstück nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, dass die besagten Blätter mit einer Tangente des besagten Rads einen Winkel von ca. 45° bilden.
EP05105626A 2005-06-23 2005-06-23 Uhr Active EP1736838B1 (de)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP05105626A EP1736838B1 (de) 2005-06-23 2005-06-23 Uhr
AT05105626T ATE389902T1 (de) 2005-06-23 2005-06-23 Uhr
DE602005005465T DE602005005465T2 (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 EP1736838A1 (de) 2006-12-27
EP1736838B1 true EP1736838B1 (de) 2008-03-19

Family

ID=36217003

Family Applications (1)

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

Country Status (4)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2553533B2 (de) † 2010-04-01 2019-06-19 Rolex S.A. Blockiervorrichtung für Zahnrad

Families Citing this family (17)

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Publication number Priority date Publication date Assignee Title
CH705118B1 (fr) 2007-12-27 2012-12-31 Chopard Technologies Sa Mouvement horloger comportant un organe réglant à fréquence d'oscillation élevée.
EP2309344B1 (de) * 2007-12-27 2012-05-09 Chopard Technologies SA Verfahren zur Veränderung der Oszillationsfrequenz eines Uhrwerks
EP2090941B1 (de) 2008-02-18 2011-10-19 CSEM Centre Suisse d'Electronique et de Microtechnique SA - Recherche et Développement Mechanischer Oszillator
CH701421B1 (fr) 2009-07-10 2014-11-28 Manuf Et Fabrique De Montres Et Chronomètres Ulysse Nardin Le Locle Sa Oscillateur mécanique.
EP2290476B1 (de) 2009-08-18 2014-04-23 CSEM Centre Suisse d'Electronique et de Microtechnique SA - Recherche et Développement Isochronismuskorrektor für Uhrhemmungsmechanismus und mit einem solchen Korrektor ausgestatteter Hemmungsmechanismus
EP2363762B1 (de) * 2010-03-04 2017-11-22 Montres Breguet SA Uhr mit einem mechanischen Hochfrequenzuhrwerk
CH709291A2 (fr) 2014-02-20 2015-08-28 Suisse Electronique Microtech Oscillateur de pièce d'horlogerie.
EP3076245B1 (de) 2015-04-02 2021-03-17 CSEM Centre Suisse D'electronique Et De Microtechnique SA Dämpfungsvorrichtung, insbesondere für mikromechanische uhrkomponente
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
ES2698115T3 (es) * 2015-12-16 2019-01-31 Sa De La Manufacture Dhorlogerie Audemars Piguet & Cie Mecanismo de regulación de una velocidad media en un movimiento de relojería y movimiento de relojería
FR3048791B1 (fr) * 2016-03-14 2018-05-18 Lvmh Swiss Manufactures Sa Mecanisme pour piece d'horlogerie et piece d'horlogerie comprenant un tel mecanisme
FR3048792B1 (fr) * 2016-03-14 2019-07-19 Lvmh Swiss Manufactures 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
EP3276431B1 (de) 2016-07-27 2020-01-01 Cartier International AG Mechanischer oszillator für uhrwerk
CH714992A9 (fr) 2019-01-24 2020-01-15 Csem Centre Suisse Delectronique Et De Microtechnique Sa Régulateur horloger mécanique.
EP3722888B1 (de) 2019-04-09 2023-05-17 Ecole Polytechnique Fédérale de Lausanne (EPFL) Mechanischer oszillator mit abstimmbarem isochronismusmangel
US11602344B2 (en) * 2021-06-30 2023-03-14 Covidien Lp Surgical stapling apparatus with firing lockout assembly

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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 (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2553533B2 (de) † 2010-04-01 2019-06-19 Rolex S.A. Blockiervorrichtung für Zahnrad

Also Published As

Publication number Publication date
EP1736838A1 (de) 2006-12-27
DE602005005465D1 (de) 2008-04-30
ATE389902T1 (de) 2008-04-15
DE602005005465T2 (de) 2009-04-09
HK1096164A1 (en) 2007-05-25

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