WO2003012556A2 - Dispositif remontoir pour remonter automatiquement un mecanisme d'horlogerie - Google Patents

Dispositif remontoir pour remonter automatiquement un mecanisme d'horlogerie Download PDF

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Publication number
WO2003012556A2
WO2003012556A2 PCT/DE2002/002700 DE0202700W WO03012556A2 WO 2003012556 A2 WO2003012556 A2 WO 2003012556A2 DE 0202700 W DE0202700 W DE 0202700W WO 03012556 A2 WO03012556 A2 WO 03012556A2
Authority
WO
WIPO (PCT)
Prior art keywords
clockwork
flywheel
bearing
profile
practically
Prior art date
Application number
PCT/DE2002/002700
Other languages
German (de)
English (en)
Other versions
WO2003012556A3 (fr
Inventor
Bernhard Lederer
Original Assignee
Bernhard Lederer
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 Bernhard Lederer filed Critical Bernhard Lederer
Publication of WO2003012556A2 publication Critical patent/WO2003012556A2/fr
Publication of WO2003012556A3 publication Critical patent/WO2003012556A3/fr

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Classifications

    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B5/00—Automatic winding up
    • G04B5/02—Automatic winding up by self-winding caused by the movement of the watch
    • G04B5/18—Supports, suspensions or guide arrangements, for oscillating weights
    • G04B5/184—Guide arrangement of the moving weight in a circular course

Definitions

  • the invention relates to an elevator device for the automatic winding of a clockwork according to the preamble of claim 1.
  • Such an elevator device has a flywheel with an essentially annular envelope of its movement path; the flywheel is naturally not rotationally symmetrical or has a non-rotationally symmetrical mass distribution.
  • flywheels have a semi-ring-shaped outline, but they can also have an essentially irregular, geometric shape.
  • the present invention relates to flywheels, the mass distribution of which sweeps over an annular to circular area during vibration.
  • Inertial mass distributions in the form of a semicircle are also suitable for the invention, or inertial mass distributions with an irregular, geometric shape, which have a circular area as the envelope of their movement path.
  • the flywheel is coupled practically in the center of the clockwork torque-transmitting to a spring mechanism of the clockwork, but on the other hand practically supported by a corresponding roller / roller bearing pair on a circumference with respect to the center.
  • the spring mechanism of the clockwork or the coupling to the spring mechanism is relieved or freed from deviation moments of the flywheel movement; the moments of deviation are essentially absorbed by the bearing pairing.
  • the invention offers the advantage that a simple, separate production of a bearing partner or both bearing partners with the highest accuracy and tolerance requirements is possible without the need for special geometrical adjustments to the clockwork or the housing.
  • a centering during installation - which is usually associated with the highest accuracy requirements and with very high adjustment effort - can be completely omitted, the resulting bearing pairing nevertheless offering the best smooth-running properties and practically completely relieving the coupling of the spring mechanism from deviation moments.
  • the tolerances of the housing or clockwork are largely by the invention of the bearing tolerances by the separate manufacture of the bearing pairing up to completely decoupled. As a result, such a bearing pairing can also be easily retrofitted for existing housings or clockworks.
  • At least one separate one which is adapted to the external geometry of the clockwork and preferably sits on the clockwork or is fastened there and is fixed with respect to the clockwork
  • Adaptation element is provided. Such a separate adaptation element is manufactured separately with the highest accuracy requirements.
  • the adaptation element provides the clockwork-fixed partner of the bearing pairing with the required geometry requirements, in particular with the required dimensions and tolerances, in which the partner of the bearing pairing that is moving with the flywheel is mounted.
  • the adaptation element is manufactured separately from the clockwork and from the housing and is to be mounted as at least one component on the clockwork on the housing.
  • a bearing pairing must either be constructed on the clockwork on the housing or the housing together with the bearing pairing must be precisely centered with regard to the coupling to the spring mechanism, for which a considerable effort is required.
  • the invention has recognized that only an adaptation element which is adapted to the outer geometry of the clockwork and is separate with respect to the clockwork is completely sufficient to automatically offer a bearing pairing with all requirements for proper storage with separate and thus simple manufacture.
  • the adaptation element is easy to attach to the clockwork and still offers accurate and smooth-running storage.
  • the movement on the movement side has to be taken into account the dimensions, the geometry and especially the tolerances of the
  • the bearing-side adaptation is carried out with the dimensions, the geometry and in particular the tolerances that are required for a bearing pairing.
  • the adaptation element can be a unit or consist of several parts.
  • the seat of the adaptation element in the assembly position is fixed with respect to the clockwork, accordingly the mechanical connecting means for connecting the adaptation element to the clockwork or to the housing are designed. This will be discussed in more detail later.
  • Adaptation element in the above sense means that the geometry requirements for the storage are adapted to an existing clockwork by the adaptation element. In particular, the movement itself does not have to be machined. The detailed design of the adaptation element is discussed in more detail below.
  • the embodiment according to claim 2 provides that the roller / tread surfaces
  • Bearing pairing has corresponding roller and tread geometries, which under all operating conditions occurring - in particular forces, torques, relative tilting - the bearing pair provides a practically only point-to-line contact zone between rollers and running surfaces. Then the respective roller engages in the corresponding running surface in such a way that under the mentioned operating conditions there is practically only point-like to linear support of the running roller on the running surface. This support is preferably always implemented practically on both sides of the respective rollers under the operating conditions mentioned. On the one hand, this minimizes frictional forces and relative slippage between the roller and the running surface, on the other hand, it results in increased smoothness and less to zero running inhibition.
  • the invention proposes that wedge bearing rollers are provided as rollers which engage in corresponding roller splines which provide the running surface, the opening angle of the wedge cross section of the engagement sections of the bearing wedge rollers being greater than the opening angle of the wedge cross section of the roller splines ,
  • the line-to-point contact zone mentioned can also be used by others Geometries can be achieved;
  • Geometries can be achieved;
  • curved geometries and different cross-sectional geometries of rollers and running surfaces come into question.
  • grooves and rollers can each have round to elliptical cross sections with correspondingly different radii or main axes, so that overall there are also punctiform to linear contact zones.
  • the relevant difference in size of the opening angle is 1 to 10 degrees, preferably 1 to 5 degrees.
  • the size difference mentioned specifies on the one hand the size of the contact zone and on the other hand the depth of engagement of the rollers in the grooves. If the difference in size is too small, then there are practically flat contact zones again, if it is too large, the depth of engagement becomes too small.
  • the invention has a double use if a standard clockwork is provided which has manufacturing and / or installation tolerances in the watch case which are unsuitable for storage directly on the outer circumference of the clockwork, the adaptation element with respect to the clockwork-fixed partner of the bearing pairing having these tolerances practically dependent on the bearing tolerances decoupled. Sufficient to very good bearing geometries, in particular bearing tolerances, can then always be realized, on the other hand standard watch movements can also be used which generally have unsuitable outer geometries for storage.
  • the watchmaker-fixed partner can either contain rollers or at least one running surface for corresponding bearing rollers that move with the movement of the flywheel. It is preferred if the movement-fixed partner of the bearing pairing merely has at least one running surface for those that move with the movement of the flywheel Has bearing rollers. Such a tread is very easy to install in the adaptation element and is very small. Overall, the mass of the adaptation element can thus be kept comparatively small and the overall construction effort reduced.
  • the bearing rollers including suspensions are then running with the flywheel mass, so that - depending on the arrangement of the bearing rollers etc. - the effective flywheel mass can be increased by the bearing rollers including their suspensions etc.
  • Azimuth error i. H. relative tilting between the axes of rotation of the bearing pair and spring mechanism, coaxial errors and height differences (in the axial direction) of the two radial planes (no concentric error in the narrower sense) etc.
  • the coupling to the spring mechanism has a concentric or position error between the bearing pair and the spring mechanism compensating, in particular radial and / or axial, play of movement.
  • the detailed design will also be discussed in detail in the context of the figure description.
  • FIG. 1 shows a section through a clock according to the invention with an additional adaptation element in the form of a profile ring
  • FIG. 2 shows a section through a clock according to the invention, a movement retaining ring for the clockwork being designed to form an adaptation element according to the invention
  • Fig. 3 shows a section through a clock according to the invention, wherein a movement retaining ring for the
  • FIG. 3 a another embodiment with two-part flywheel (can also be in one piece, see below),
  • FIG. 4 shows a section through the exemplary embodiments of FIGS. 1 and 2, as indicated by IV-IV there,
  • FIG. 5 shows a section through the embodiment of FIG. 3, as there designated V-V,
  • Fig. 6 shows a section through a further embodiment with clockwork
  • FIG. 6a shows a detailed view from FIG. 6, as there with a dash-dotted line
  • FIG. 7 shows a section through the exemplary embodiment of FIG. 6, as there designated VII-VII,
  • Fig. 8 is a plan view of a coupling ring with a torque transmission arm.
  • the watch essentially consists of a watch case 5 with a cylinder wall and a watch case back 6.
  • a watch mechanism 4 is seated in the watch case 5 and is fastened with a movement retaining ring 3 in the watch mechanism 5.
  • the movement retaining ring 3 sits with a tight fit (transition fit to press fit) between an outer wall of the clockwork 4 and an inner wall of the watch case 5.
  • a flywheel 1 is provided for the automatic winding of the clockwork 4 is practically ring-shaped. This is arranged in such a way that it can move freely on a circular path. It can be seen from FIG.
  • a separate U-profile ring 2 is provided with respect to the clockwork 4, the movement retaining ring 3 and the watch case 5, which is arranged adjacent to the watch case 4 with a close fit with respect to all surfaces involved.
  • the U-profile ring 2 is adapted to the outer geometry of the clockwork 4 and is fixed with respect to the clockwork 4.
  • the U-profile ring 2 is adapted in terms of its geometry or its dimensions to the external dimensions of the clockwork 4, so that it sits practically positively on the clockwork 4.
  • the U-profile ring 2 provides the clockwork-fixed partner of the bearing pairing with the required geometry requirements, in which the partner of the bearing pairing that is moving with the flywheel 1 is mounted.
  • both the inner U-leg 30 and the outer U-leg 31 each have a running keyway 15, 16.
  • Corresponding wedge bearing rollers 11, 12 engage in these running keyways 15, 16.
  • the running keyway 15 is attached to the outer circumference of the inner U-leg 30 and the running keyway 16 to the inner circumference of the outer U-leg 31 of the U-profile ring.
  • the flywheel 1 is practically a half-ring extending over a circumferential section of 180 degrees, such a geometric shape being shown only for the sake of simplicity. Other shapes that can be irregular and overlap are also possible can extend a larger or smaller circumferential angle range. This has practically no influence on the advantages of the invention.
  • the flywheel 1 shown has two inner inner bearing rollers 11 which are fastened to the flywheel 1 in the region of the two circumferential ends of the flywheel 1.
  • a further outer bearing roller 12 is provided, which is arranged practically in the middle of the outer circumference of the flywheel 1. It is essential that the three bearing rollers 11, 12 provide inside and outside, in total at least three-point support for the flywheel 1, so that the flywheel 1 is positively supported and supported along its practically circular movement path.
  • the configuration described above only provides one component, namely the U-profile ring 2, which is easy to manufacture.
  • the tolerances that are decisive for the raceways 15, 16 are easy to manufacture with the required accuracies, in particular tolerances.
  • the contact surfaces on the clockwork 4, on the movement holder 3 and on the clock housing 5 can be manufactured with lower accuracy requirements with regard to the geometry.
  • this configuration is very simple and can be adapted to existing combinations of watch case 4, movement retaining ring 3 and watch case 5, since it is manufactured separately with respect to these components.
  • the torque applied by the movements of the flywheel 1 is transmitted via a torque transmission arm 10, which is fastened to the flywheel 1 with two fastening screws 13, which are spaced apart in the circumferential direction of the flywheel 1.
  • the torque transmission arm 10 Radially on the inside, the torque transmission arm 10 has an elongated coupling recess 14 into which a coupling means (not shown) of the spring mechanism engages with radial and / or axial play.
  • the coupling means has a rotationally positive engagement with the coupling recess 14 of the torque transmission arm 10.
  • an end piece or connecting piece or a pin can be provided for coupling to the spring mechanism.
  • the coupling means is out of round in this sense, for example a square end can be provided, in which the Coupling recess 14 engages so that there is still a radial and axial movement play.
  • This configuration of the torque transmission has the advantage that it is very simple and nevertheless offers a functionally reliable torque transmission with sufficient movement play.
  • no further complex mechanical coupling means are to be provided, since the coupling only takes place through the positive connection.
  • FIG. 2 A saving of components and a better, form-fitting seat of the clockwork 4, adaptation element and movement retaining ring 3 in the clock housing 4 is achieved by the configuration of FIG. 2: there - as in all the exemplary embodiments shown in FIGS. 1 to 3 - the clockwork 4 has that large area , where the flywheel 1 is arranged, a circumferential circumferential recess 32.
  • the recess 32 has the shape of a width step in the section shown.
  • the movement retaining ring 3 is widened in the area of the width step 32 to a U-profile 7, which the
  • the inner race 15 and the outer race 16 are attached to the respective side of the outer leg 8 or the inner leg 9 of the movement retaining ring 3.
  • the movement retaining ring 3 shows a two-part flywheel mass 1 with a radially outer ring section and a radially inner ring section, the outer ring section running in the recess between the outer web 8 and the inner web 9 of the movement retaining ring 3.
  • These also form a U-profile, which, however, does not reach into the width recess 32, but essentially has the width of the movement holding ring 3.
  • the movement retaining ring 3 is provided with the devices for the adaptation element, but the geometric configuration is considerably simpler.
  • the U-profile can be introduced, for example milled, into a customary work holding ring 3, which has a greater height, as shown.
  • Such a retaining ring 3 is very easy to manufacture.
  • the two sections of the two-part flywheel 1 are connected to one another via a ring bridge 33.
  • This ring bridge 33 can also extend over the entire shape of the two flywheel parts and be made of the same material as the flywheel mass (es).
  • a one-piece flywheel 1 with the geometry shown can be present, that is, a one-piece flywheel 1 with a corresponding recess or annular groove into which a leg of the U-profile can reach or protrude.
  • the inner bearing rollers 11 are attached to the inner portion of the two-part flywheel mass 1 and run on the inner circumference of the inner web 9, the outer bearing roller 12 runs on the outer circumference of the inner web 9.
  • the ring bridge 33 already ends radially in front of the outer circumference of the outer one Flywheel mass 1, so that overall the outer flywheel mass 1 has more heavy flywheel material on the outside and thus a greater moment of inertia.
  • FIGS. 6 to 8 show a further exemplary embodiment of the present invention, a cup disk 17 adapted to the outer geometry - including the width cutout 32 - of the clockwork 4 being seated on the clockwork 4.
  • a circumferential ring web 18 is provided for fastening the clockwork 4 in the watch case 5.
  • a cup washer 17 a ring can also be provided, which can only consist of a cylinder wall for the application of the running keyways 24 and is seated on the outer wall of the clockwork 4.
  • the running keyway 24 is applied as a running surface for the corresponding wedge bearing rollers 19.
  • three wedge bearing rollers 19 are provided, which are arranged practically regularly - that is to say circumferentially offset from one another at an angle of 120 degrees. It is essential that a three-point bearing is present, which encloses an angle of more than 180 degrees, since the wedge bearing rollers 19 only have an inward support. On in this way a positive fit of the bearing is achieved, which holds and supports the flywheel 1 on the barrel circumferential wall 29 of the cup wheel 17.
  • the flywheel 1 is attached to a retaining ring 22.
  • the torque is transmitted by means of a coupling ring 21 which is connected to the retaining ring 22 via connecting screws 23 which pass through bores 27 of the coupling ring 21 and are screwed into threaded holes 28 in the retaining ring 22.
  • the wedge bearing rollers 19 are each rotatably supported in their seat with a bearing roller pin 20. They are arranged between the coupling ring 21 and the retaining ring 22, the bearing roller pins 20 being thereby fixed at the same time. Due to the connected geometries - for example of bearing roller pin 20 and / or
  • Coupling ring 21 and / or retaining ring 22 - a free running of the wedge bearing rollers 19 is guaranteed. It is essential that - as stated above - at least three-point bearing is ensured by the wedge bearing rollers 19, which includes an angle of more than 180 degrees; instead of the ring connection of the coupling ring 21 and the holding ring 22 shown, this can also be achieved by other means, for example by separate, radially projecting support arms for the wedge bearing rollers, which are fastened to the flywheel 1, so that the corresponding wedge bearing rollers 19 are positioned at the intended circumferential location.
  • FIG. 6a shows that the opening angle 26 of the wedge cross section of the
  • Engagement sections of the wedge bearing rollers 19 is greater than the opening angle 25 of the wedge cross section of the running splines. As a result, a point or line-shaped contact is achieved on the tread.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

L'invention concerne un dispositif remontoir permettant de remonter automatiquement un mécanisme d'horlogerie (4). Ce dispositif comprend une masse oscillante (1) présentant une enveloppe sensiblement annulaire pour sa trajectoire. Cette masse oscillante est couplée, sensiblement au centre du mécanisme d'horlogerie (4), à un mécanisme de ressort dudit mécanisme d'horlogerie de façon à transmettre le moment angulaire et elle est montée sensiblement à la périphérie du centre par l'intermédiaire d'un appariement de roulement constitué de galets de roulement (19) et de surfaces de roulement (24) correspondantes. Le dispositif se caractérise en ce qu'il comprend au moins un élément d'adaptation séparé (2, 3, 17) adapté à la géométrie extérieure du mécanisme d'horlogerie (4) et fixe par rapport à ce dernier, cet élément d'adaptation procurant l'élément associé de l'appariement de roulement qui est fixe par rapport au mécanisme d'horlogerie, avec les exigences de géométrie requises. L'élément associé de l'appariement de roulement qui se déplace avec la masse oscillante (1) est monté dans cet élément d'adaptation.
PCT/DE2002/002700 2001-07-24 2002-07-24 Dispositif remontoir pour remonter automatiquement un mecanisme d'horlogerie WO2003012556A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10135234.4 2001-07-24
DE2001135234 DE10135234A1 (de) 2001-07-24 2001-07-24 Aufzugsvorrichtung für den automatischen Aufzug eines Uhrwerkes

Publications (2)

Publication Number Publication Date
WO2003012556A2 true WO2003012556A2 (fr) 2003-02-13
WO2003012556A3 WO2003012556A3 (fr) 2003-08-07

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PCT/DE2002/002700 WO2003012556A2 (fr) 2001-07-24 2002-07-24 Dispositif remontoir pour remonter automatiquement un mecanisme d'horlogerie

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WO (1) WO2003012556A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2551731A1 (fr) * 2011-07-28 2013-01-30 Cartier Création Studio S.A. Masse oscillante pivotée sur l'extérieur d'un mouvement d'horlogerie et mouvement d'horlogerie équipé d'une telle masse oscillante.

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH289757A (fr) * 1950-06-12 1953-03-31 Hausheer Hermann Dispositif de remontage automatique pour montre.
CH320005A (fr) * 1955-06-29 1957-03-15 Baud Marc Dispositif de remontage automatique d'une montre
CH322325A (fr) * 1955-06-06 1957-06-15 Gosteli Paul Pièce d'horlogerie à remontage automatique par masse oscillante
FR1149822A (fr) * 1955-07-19 1958-01-02 Fontainemelon Horlogerie Montre à remontoir automatique
CH336005A (fr) * 1956-09-11 1959-01-31 Fontainemelon Horlogerie Montre à remontoir automatique
CH348113A (de) * 1958-06-16 1960-07-31 Durowe Ag Aufziehvorrichtung für tragbare Uhren
US3006138A (en) * 1958-06-04 1961-10-31 Rene A Fiechter Automatic self-winding watch
DE1142555B (de) * 1955-11-22 1963-01-17 Vladimir Cervinka Dr Uhr mit automatischem Aufzug ihrer Feder

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH336757A (fr) * 1957-02-14 1959-02-28 Piquerez Sa Ervin Montre à remontoir automatique
CH336758A (fr) * 1957-05-09 1959-02-28 Schild Sa A Montre à remontage automatique
CH675760A4 (fr) * 1960-06-14 1963-11-30

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH289757A (fr) * 1950-06-12 1953-03-31 Hausheer Hermann Dispositif de remontage automatique pour montre.
CH322325A (fr) * 1955-06-06 1957-06-15 Gosteli Paul Pièce d'horlogerie à remontage automatique par masse oscillante
CH320005A (fr) * 1955-06-29 1957-03-15 Baud Marc Dispositif de remontage automatique d'une montre
FR1149822A (fr) * 1955-07-19 1958-01-02 Fontainemelon Horlogerie Montre à remontoir automatique
DE1142555B (de) * 1955-11-22 1963-01-17 Vladimir Cervinka Dr Uhr mit automatischem Aufzug ihrer Feder
CH336005A (fr) * 1956-09-11 1959-01-31 Fontainemelon Horlogerie Montre à remontoir automatique
US3006138A (en) * 1958-06-04 1961-10-31 Rene A Fiechter Automatic self-winding watch
CH348113A (de) * 1958-06-16 1960-07-31 Durowe Ag Aufziehvorrichtung für tragbare Uhren

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2551731A1 (fr) * 2011-07-28 2013-01-30 Cartier Création Studio S.A. Masse oscillante pivotée sur l'extérieur d'un mouvement d'horlogerie et mouvement d'horlogerie équipé d'une telle masse oscillante.
WO2013014504A1 (fr) * 2011-07-28 2013-01-31 Cartier Creation Studio Sa Masse oscillante pivotée sur l'extérieur d'un mouvement d'horlogerie, mouvement d'horlogerie équipé d'une telle masse oscillante et pièce d'horlogerie comprenant une telle masse oscillante
CN103890665A (zh) * 2011-07-28 2014-06-25 卡迪亚创造工作室股份公司 在钟表机芯外部上枢转的摆陀和装配有所述摆陀的钟表机芯以及包括所述摆陀的钟表
US9146536B2 (en) 2011-07-28 2015-09-29 Cartier Creation Studio Sa Oscillating mass pivoted on the exterior of a timepiece movement, timepiece movement fitted with such an oscillating mass and timepiece comprising such an oscillating mass

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Publication number Publication date
WO2003012556A3 (fr) 2003-08-07
DE10135234A1 (de) 2003-02-13

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