EP2756360B1 - Federgehäuse für eine uhr mit kleinem kerndurchmesser - Google Patents

Federgehäuse für eine uhr mit kleinem kerndurchmesser Download PDF

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Publication number
EP2756360B1
EP2756360B1 EP12759423.2A EP12759423A EP2756360B1 EP 2756360 B1 EP2756360 B1 EP 2756360B1 EP 12759423 A EP12759423 A EP 12759423A EP 2756360 B1 EP2756360 B1 EP 2756360B1
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EP
European Patent Office
Prior art keywords
spring
drum
barrel assembly
barrel
core
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Application number
EP12759423.2A
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English (en)
French (fr)
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EP2756360A1 (de
Inventor
Laurent Kaelin
Baptist Wyssbrod
Arthur Queval
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.)
ETA SA Manufacture Horlogere Suisse
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ETA SA Manufacture Horlogere Suisse
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Priority to EP12759423.2A priority Critical patent/EP2756360B1/de
Publication of EP2756360A1 publication Critical patent/EP2756360A1/de
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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
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/16—Barrels; Arbors; Barrel axles
    • G04B1/165—Spring cylinder with friction transmission to the gearing (especially for Roskopf clockworks)
    • 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
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/14—Mainsprings; Bridles therefor
    • G04B1/145—Composition and manufacture of the springs
    • 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
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/16—Barrels; Arbors; Barrel axles
    • 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
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/18—Constructions for connecting the ends of the mainsprings with the barrel or the arbor

Definitions

  • the invention relates to a watch-barrel assembly, comprising at least one barrel-drive spring mounted between, at one end, a barrel drum, and at a second end a receiving surface that comprises a barrel plug coaxial with said drum around of a pivot axis.
  • the invention also relates to a watch movement comprising at least one such barrel assembly.
  • the invention also relates to a timepiece comprising at least one such movement and / or at least one such barrel assembly.
  • the invention relates to the field of watchmaking, and more particularly the field of energy storage barrels, for feeding a movement, a ring, or other functionality of a room watchmaking.
  • one solution consists of a decrease in the diameter of the barrel shaft and the associated bung, so as to increase the space available in the drum. for the spring.
  • the ratio of the bead radius to the thickness of the spring is usually between 10 and 20, and the invention proposes to lower this ratio below 10, and preferably in the range between 5 and 10.
  • a ratchet is mounted axially on a barrel axis or on a bung, via a square, the ratchet being generally fixed by an axial screw.
  • the size of this screw and that of the square thus condition a minimum diameter of a pivoting surface.
  • a shoulder abutting with this pivoting surface limits axial fretting of the shaft or the bung relative to a plate or bridge carrying a stone or the like.
  • a diameter even greater than that of this shoulder is necessary for a pivoting guide surface of the drum on the shaft or on the bung, combined with a shoulder limiting axial fretting of the drum.
  • the respect of minimal sections of matter implies a quotation chain which results in a large size, difficult to reduce. In particular, it is not enough to reduce all the sizing, because the sections of material are then insufficient to ensure fatigue resistance.
  • the document CH 319 631 in the name of FELSA SA describes a double barrel, and how is limited the frolicking of each of the drums.
  • the frog of a lower drum is limited on the upper side by a flange of a sleeve, which is pushed towards a shoulder of the barrel shaft, by a nut screwed on the same shaft; and, on the lower side, by a bottom of a bung integral in pivoting of the barrel shaft by a flat.
  • the length of the lower bearing of the barrel shaft, and that of a barrel of the drum determine the frolicking of the drum, in relation to these flange and bottom surfaces.
  • VACUUMSCHMELZE discloses cobalt-nickel-chromium alloys, suitable for the manufacture of springs, especially for watches, and the associated heat treatment. These alloys have a very good ductility and a high Young's modulus.
  • the invention takes into account several solutions to achieve this reduction of the bung diameter.
  • An important constraint is to ensure the disassembly of the assembly, for a possible exchange of the mainspring or the complete barrel.
  • a first solution is to ensure the frolicking between drum and cover by the mainspring, transferring to the spring this frolicking adjustment function, in particular by equipping the spring protruding areas, such as dots, more rolled areas wide, flange reported, or the like. It is then possible to remove the bearing shoulders of the drum and cover on the barrel shaft or on the bung.
  • a second solution is to make a bung in several parts, including two or three parts.
  • This solution makes it possible in particular to make a bung of diameter smaller than the pivoting diameter of the drum.
  • the plug is introduced through the bore of the drum.
  • a shaft or a bung in two parts, or more, facilitates the machining of hook of hook of the shell of the mainspring.
  • the bung may include, for the ratchet drive, a conventional square, or a thread. Or, in a non-limiting way, in a second variant.
  • the bung can still include one or more washers or diameter catch rings for its guidance in platinum and bridge.
  • Another solution is to chase on the bung a setting washer of the drum-lid frog. This ring is mounted so as to avoid, for intervention on the barrel, any disassembly of a bridge.
  • the different variants proposed by the invention ensure ease of machining, ease of assembly, ease of disassembly, and control of axial debates between the various components and with respect to the bridges.
  • the invention relates to a watch barrel assembly, comprising at least one barrel drive spring mounted between, at one end a barrel drum, and at a second end a receiving surface that includes a plug of barrel coaxial with said drum about a pivot axis, characterized in that said spring is made of a cobalt-nickel-chromium-based multiphase alloy comprising from 44 to 46% of cobalt, from 20 to 22% of nickel, 17 to 19% chromium, 4 to 6% iron, 3 to 5% tungsten, 3 to 5% molybdenum, 0 to 2% titanium, 0 to 1% beryllium, and modulus of Young between 200 and 240 GPa and a shear modulus between 80 and 100 GPa, and having a width / thickness ratio of between 9 and 21, and in that the maximum radius of said bung, made of steel or stainless steel, with respect to said pivot axis is less than nine times the thickness r maximum of said spring, and further characterized in that said barrel assembly comprises,
  • said means for limiting said longitudinal gap between said drum and said spring are constituted by either at least one lug at at least one of the edges that comprises said spring, or by a clearance device that includes said drum on its largest inside diameter, said peripheral clearance being between two oblique bearing surfaces for the support and the peripheral holding of said spring.
  • the invention also relates to a watchmaking movement comprising at least one such barrel assembly for energy storage with an incorporated inlet, or else a ratchet integral with pivoting of said leap, or by a fixed toothing of a drum toothing. pivoting said drum, and an output constituted respectively, or by a mounted toothing drum pivotally attached to said drum, or by a ratchet integral pivotally of said bung.
  • the invention also relates to a timepiece comprising at least one such clockwork movement and / or at least one such set for storing energy with an incorporated input, or else a ratchet integral with pivoting said bung or by a toothing drum pivotally integral with said drum, and an outlet respectively constituted by a toothing drum mounted integral pivoting said drum, or by a ratchet integral pivotally of said bung.
  • the invention relates to the field of watchmaking, and more particularly the field of energy storage barrels, for feeding a movement, a ring, or other functionality of a room watchmaking.
  • the invention relates to a mechanical watch cylinder with reduced bung diameter.
  • the invention relates to a watch barrel assembly 1 comprising at least one mainspring 2 of the barrel.
  • This spring 2 is conventionally mounted between, at a first end 21, a barrel drum 3, and at a second end 22 a receiving surface 5 that includes a barrel plug 4 coaxial with the drum 3 about a pivot axis D.
  • this spring 2 is made of a cobalt-nickel-chromium-based multiphase alloy comprising from 44 to 46% of cobalt, from 20 to 22% of nickel, from 17 to 19% of chromium, from 4 to 6% of iron, 3 to 5% of tungsten, 3 to 5% of molybdenum, 0 to 2% of titanium, 0 to 1% of beryllium, and Young's modulus of between 200 and 240 GPa and a shear modulus of between 80 and 100 G Pa.
  • This spring 2 has a width / thickness ratio of between 3 and 23, and more particularly between 9 and 21.
  • the maximum radius of the bung 4, made of steel or stainless steel, relative to the pivot axis D is less than nine times the maximum thickness of the spring 2.
  • this barrel assembly 1 comprises, at the level of the spring 2 or the drum 3, means for limiting the longitudinal gap 6, in the direction of the pivot axis D, between the drum 3 and the motor spring 2.
  • the spring 2 advantageously comprises at least one projecting zone 23 arranged to cooperate in support with an inner face 31 of the drum 3 or / and with an inner face 71 of a cover 7 delimiting with the drum 3 a chamber 32 for housing the spring 2.
  • such a protruding zone 23 comprises at least one lug 24 at the level of at least one of the edges 27; 28
  • This spring region 23 is arranged to cooperate with an inner surface 31 of the drum 3, and / or with an inner surface 71 of the cover 7, and preferably with both.
  • the means for limiting the longitudinal gap 6 between the drum 3 and the spring 2 are thus constituted, or else by at least one lug 24 at the level of at least one of the edges 27, 28, that includes the spring 2, or by a peripheral clearance 36 that includes the drum 3 on its largest inside diameter, this peripheral clearance 36 being between two surfaces 33, 34, oblique for the support and the peripheral maintenance of spring 2.
  • the spring 2 is enclosed in a chamber 32 delimited by the drum 3 and a 7, and the barrel assembly 1 according to the invention comprises, other than on the plug 4, means for adjusting the longitudinal slab 6, in the direction of the pivot axis D, between the cover 7 and the spring 2.
  • this at least one lug 24 of the spring 2 is arranged to cooperate in support with an inner face 31 of the drum 3 and / or with an inner face 71 of a lid 7 delimiting with the drum 3 a chamber 32 for housing the spring 2.
  • such a protruding zone 23, or in particular this lug 24 comprises at least one coil extended in height of the spring 2.
  • such a protruding zone 23, or in particular this lug 24 comprises at least one attached flange 26, of height locally greater than that of the turns of the spring 2, and which is fixed thereto, for example by welding.
  • the drum 3 comprises, on its largest internal diameter, a peripheral clearance 36 between two upper and lower flanges 37 and 38, the edges of which, upper 27 and lower 28, respectively carry two bearing surfaces 33 and 34, oblique at an angle ⁇ , for the support and the peripheral support of the spring 2.
  • the means for limiting the longitudinal gap 6 between the drum 3 and the spring 2 are constituted by a peripheral clearance 36 that the drum 3 has on its plus large inner diameter, this peripheral clearance 36 being between two surfaces 33, 34, for the support and the peripheral support of the spring 2.
  • peripheral clearance 36 is cylindrical and at the same height as the spring 2 which is centered between the bearing surfaces 33, 34, which are flat and perpendicular to the pivot axis D.
  • the peripheral clearance 36 has a height less than that of the spring 2, which is centered obliquely between the bearing surfaces 33, 34, which comprise oblique faces turned toward each other so as to define a support v for singing surfaces 27,28, that includes the spring 2.
  • the spring 2 is held elastically without a hook around the receiving surface 5 which is a surface of revolution with respect to the pivot axis D.
  • the Figures 2 and 3 show a bung included in an envelope radius R0 about the axis D.
  • the receiving surface 5 comprises a hook 41 for hooking the shell of the spring 2, a clearance 52 allows the attachment of the spring2 and facilitates the machining of the hook 41.
  • Spans 43 and 44 are provided to cooperate with stones mounted in the plates or bridges of the movement receiving the barrel assembly 1.
  • the square 42 is provided for the attachment of a ratchet 12.
  • the spans 45 and 46 cooperate respectively with a bore 35 of the drum 3 and a bore 75 of the cover 7.
  • the receiving surface 5 is a surface of revolution relative to the pivot axis D.
  • this receiving surface is a contact surface for fixing the spring 2 by welding on the bung 4, by a point 53 , or along a segment, preferably parallel to the pivot axis D, passing through such a point 53, as visible on the Figures 15A, 15B, 15C .
  • FIG 15A the spring 2 bears at point 53 on a cylindrical portion of the bung 4 of small width.
  • the spring 2 bears at the point 53 on a flat tangent to one of the bearing surfaces 45 or 46 of the drum 3 or the cover 7, here preferably to the bearing 45 intended to cooperate with the bore 35 of the drum 3.
  • the figure 15C illustrates a cylindrical bearing surface of the spring 2 wider than that of the figure 15A and which is locally confused with one of the bearing surfaces 45 or 46 for guiding the drum 3 or the cover 7, here preferably with the bearing surface 45 intended to cooperate with the bore 35 of the drum 3.
  • the receiving surface 5 of the spring has, from the welding point 53 or from a welding segment passing through the point 53 and parallel to the pivot axis D, a helical section, so that after the first turn, the spring comes in superposition on itself without inflection or break of slope.
  • the surface of revolution 5 is constituted by a clearance 8 of height h included between two bearing surfaces 91, 92, belonging to flanges 47 and 48. These ranges 91 and 92 define the maximum radius of the bung 4 relative to the pivot axis D.
  • this clearance 8 is cylindrical and at the same height as the spring 2 which is centered between the bearing surfaces 91, 92 which are flat and perpendicular to the pivot axis D.
  • the clearance 8 has a depth P corresponding to twice the thickness of the spring 2.
  • the clearance 8 has a height h less than that of the spring 2 which is centered obliquely between the bearing surfaces 91, 92, an upper flange 47 and a lower flange 48.
  • These bearing surfaces 91 and 92 comprise oblique faces , inclined at an angle ⁇ , facing each other so as to define a support v for the edge surfaces 27 and 28 that the spring 2 comprises.
  • the Figure 1B illustrates an embodiment in which the drum comprises a shoulder 3A facing the spring 2, and can abut by a bearing surface 3B on a bearing surface 4B that includes the bung 4, and wherein the lid 7 has a shoulder 7A turned towards the spring 2, and can come to bear by a bearing surface 7B on a bearing surface 4C that includes the bung 4.
  • the barrel assembly 1 comprises a spring 2 which is fixed to the bung 4 by friction, the end of the spring 2 then preferably comprises a shoulder designed to hold the free end of the spring 2 during its winding .
  • the spring 2 forms with the bung 4 a welded or brazed monoblock spring-binder subassembly, or the like. This embodiment is particularly advantageous, economical, and a very easy assembly.
  • the invention also relates to a watchmaking movement 100 comprising at least one such barrel assembly 1 for storing energy with an incorporated input, or else a ratchet 12 pivotally mounted on the plug 4, or by a set of teeth drum 13 mounted pivotally mounted to the drum 3, and an outlet respectively formed, or by a toothing drum 13 mounted pivotally integral with the drum 3, or by a ratchet 12 mounted pivotally integral with the bung 4.
  • the invention also relates to a timepiece 1000 comprising at least one such watch movement 100 and / or at least one such barrel assembly for energy storage with an incorporated entrance, or by a ratchet 12 mounted pivotally mounted on the bung 4, or by a toothing drum 13 mounted pivotally integral with the drum 3, and an outlet constituted respectively, or by a toothing drum 13 mounted pivotally integral with the drum 3, or by a ratchet 12 mounted pivotally integral with the bung 4.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Metallurgy (AREA)
  • Springs (AREA)
  • Gears, Cams (AREA)

Claims (15)

  1. Uhren-Federgehäuseanordnung (1), die wenigstens eine Federgehäuse-Motorfeder (2) umfasst, die mit einem ersten Ende (21) bzw. mit einem zweiten Ende (22) zwischen einer Federgehäusetrommel (3) und einer Aufnahmeoberfläche (5), die einen Federgehäusekern (4) aufweist, der zu der Trommel (3) um eine Schwenkachse (D) koaxial ist, montiert ist, dadurch gekennzeichnet, dass die Feder (2) aus einer mehrphasigen Legierung auf Kobalt-Nickel-Chrom-Basis verwirklicht ist, die 44 bis 46 % Kobalt, 20 bis 22 % Nickel, 17 bis 19 % Chrom, 4 bis 6 % Eisen, 3 bis 5 % Wolfram, 3 bis 5 % Molybdän, 0 bis 2 % Titan und 0 bis 1 % Beryllium enthält, einen Young-Modul im Bereich von 200 bis 240 GPa und einen Scherungsmodul im Bereich von 80 bis 100 GPa besitzt und ein Breiten-/Dicken-Verhältnis im Bereich von 9 bis 21 besitzt, und dass der maximale Radius des Kerns (4), der aus Stahl oder aus Edelstahl verwirklicht ist, in Bezug auf die Schwenkachse (D) kleiner als die neunfache maximale Dicke der Feder (2) ist, und weiter dadurch gekennzeichnet, dass die Federgehäuseanordnung (1) auf Höhe der Feder (2) oder der Trommel (3) Mittel (6) zum Begrenzen des longitudinalen Spiels in Richtung der Schwenkachse (D) zwischen der Trommel (3) und der Motorfeder (2) aufweist.
  2. Federgehäuseanordnung (1) nach Anspruch 1, dadurch gekennzeichnet, dass die Mittel (6) zum Begrenzen des longitudinalen Spiels zwischen der Trommel (3) und der Feder (2) entweder durch wenigstens einen Ansatz (24) auf Höhe wenigstens einer der Fasen (27; 28), die die Feder (2) aufweist, oder durch eine Umfangsaussparung (36), die die Trommel (3) auf ihrem größten Innendurchmesser aufweist, gebildet sind, wobei die Umfangsaussparung (36) zwischen zwei schrägen Bereichen (33; 34) zum Abstützen und Halten in Umfangsrichtung der Feder (2) enthalten ist.
  3. Federgehäuseanordnung (1) nach Anspruch 2, dadurch gekennzeichnet, dass der wenigstens eine Ansatz (24) der Feder (2) dafür ausgelegt ist, mit einer Innenfläche (31) der Trommel (3) und/oder mit einer Innenfläche (71) eines Deckels (7), der mit der Trommel (3) eine Aufnahmekammer (32) der Feder (2) begrenzt, abstützend zusammenzuwirken.
  4. Federgehäuseanordnung (1) nach Anspruch 3, dadurch gekennzeichnet, dass der Ansatz (24) wenigstens eine in Höhenrichtung erweiterte Windung der Feder (2) aufweist.
  5. Federgehäuseanordnung (1) nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass der Ansatz (24) wenigstens einen angefügten Steg (26) aufweist, dessen Höhe lokal größer ist als jene der Feder (2) und der an dieser Letzteren befestigt ist.
  6. Federgehäuseanordnung (1) nach Anspruch 2, dadurch gekennzeichnet, dass die Mittel (6) zum Begrenzen des longitudinalen Spiels zwischen der Trommel (3) und der Feder (2) durch eine Umfangsaussparung (36) gebildet sind, die die Trommel (3) auf ihrem größten Innendurchmesser aufweist, wobei die Umfangsaussparung (36) zwischen zwei Bereichen (33; 34) zum Abstützen und Halten in Umfangsrichtung der Feder (2) enthalten ist.
  7. Federgehäuseanordnung (1) nach Anspruch 6, dadurch gekennzeichnet, dass die Umfangsaussparung (36) zylindrisch ist und die gleiche Höhe wie die Feder (2) hat, die zwischen den Bereichen (33; 34) zentriert ist, die eben und senkrecht zu der Schwenkachse (D) sind.
  8. Federgehäuseanordnung (1) nach Anspruch 6, dadurch gekennzeichnet, dass die Umfangaussparung (36) eine Höhe besitzt, die kleiner als jene der Feder (2) ist, die schräg abgestützt zwischen den Bereichen (33; 34) zentriert ist, die einander zugewandte schräge Flächen aufweisen, derart, dass ein abstützendes V für die Fasenoberflächen (27; 28), die die Feder (2) aufweist, definiert ist.
  9. Federgehäuseanordnung (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Feder (2) ohne Einhaken elastisch um die Aufnahmeoberfläche (5) gehalten wird, die eine rotationssymmetrische Oberfläche in Bezug auf die Schwenkachse (D) ist.
  10. Federgehäuseanordnung (1) nach Anspruch 9, dadurch gekennzeichnet, dass die rotationssymmetrische Oberfläche (5) durch eine Aussparung (8) gebildet ist, die zwischen zwei Bereichen (91, 92) enthalten ist, die den maximalen Radius des Kerns (4) in Bezug auf die Schwenkachse (D) definieren.
  11. Federgehäuseanordnung (1) nach Anspruch 10, dadurch gekennzeichnet, dass die Aussparung (8) eine Höhe besitzt, die kleiner als jene der Feder (2) ist, die schräg abgestützt zwischen den Bereichen (91, 92) zentriert ist, die einander zugewandte schräge Flächen aufweisen und ein abstützendes V für die Fasenoberflächen (27; 28), die die Feder (2) aufweist, definieren.
  12. Federgehäuseanordnung (1) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Feder (2) an dem Kern (4) durch Reibung befestigt ist.
  13. Federgehäuseanordnung (1) nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, dass die Feder (2) mit dem Kern (4) eine verschweißte oder verlötete Feder-Kern-Monoblockunteranordnung bildet.
  14. Uhrwerk (100), das wenigstens eine Federgehäuseanordnung (1) nach einem der vorhergehenden Ansprüche zur Energiespeicherung umfasst, die einen Eingang besitzt, der entweder durch ein Sperrrad (12), das an dem Kern (4) schwenkbar fest montiert ist, oder durch eine Trommelzahnung (13), die an der Trommel (3) schwenkbar fest montiert ist, gebildet ist, und einen Ausgang besitzt, der entsprechend entweder durch eine Trommelzahnung (13), die an der Trommel (3) schwenkbar fest montiert ist, oder durch ein Sperrrad (12), das an dem Kern (4) schwenkbar fest montiert ist, gebildet ist.
  15. Zeitmessgerät (1000), das wenigstens ein Uhrwerk (100) nach Anspruch 14 umfasst und/oder wenigstens eine Federgehäuseanordnung (1) nach einem der Ansprüche 1 bis 13 für die Energiespeicherung umfasst, die einen Eingang besitzt, der entweder durch ein Sperrrad (12), das an dem Kern (4) schwenkbar fest montiert ist, oder durch eine Trommelzahnung (13), die an der Trommel (3) schwenkbar fest montiert ist, gebildet ist, und einen Ausgang besitzt, der entsprechend entweder durch eine Trommelzahnung (13), die an der Trommel (3) schwenkbar fest montiert ist, oder durch ein Sperrrad (12), das an dem Kern (4) schwenkbar fest montiert ist, gebildet ist.
EP12759423.2A 2011-09-15 2012-09-13 Federgehäuse für eine uhr mit kleinem kerndurchmesser Active EP2756360B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP12759423.2A EP2756360B1 (de) 2011-09-15 2012-09-13 Federgehäuse für eine uhr mit kleinem kerndurchmesser

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP11181352.3A EP2570862B1 (de) 2011-09-15 2011-09-15 Uhren-Federgehäusebaugruppe mit reduziertem Bunddurchmesser
PCT/EP2012/067913 WO2013037870A1 (fr) 2011-09-15 2012-09-13 Ensemble barillet d'horlogerie a diametre de bonde reduit
EP12759423.2A EP2756360B1 (de) 2011-09-15 2012-09-13 Federgehäuse für eine uhr mit kleinem kerndurchmesser

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EP2756360A1 EP2756360A1 (de) 2014-07-23
EP2756360B1 true EP2756360B1 (de) 2015-05-27

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EP11181352.3A Active EP2570862B1 (de) 2011-09-15 2011-09-15 Uhren-Federgehäusebaugruppe mit reduziertem Bunddurchmesser
EP12759423.2A Active EP2756360B1 (de) 2011-09-15 2012-09-13 Federgehäuse für eine uhr mit kleinem kerndurchmesser

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US (1) US9033573B2 (de)
EP (2) EP2570862B1 (de)
JP (1) JP5702509B2 (de)
CN (1) CN103797425B (de)
HK (1) HK1197840A1 (de)
IN (1) IN2014CN02738A (de)
RU (1) RU2559125C1 (de)
WO (1) WO2013037870A1 (de)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2570861A1 (de) * 2011-09-15 2013-03-20 ETA SA Manufacture Horlogère Suisse Uhren-Federgehäuse mit reduziertem Durchmesser des Bundes
EP2605087B1 (de) * 2011-12-13 2017-07-26 ETA SA Manufacture Horlogère Suisse Uhrmoduleinheit mit funktionellen Modulen
EP2834712B1 (de) 2012-04-04 2021-11-24 Rolex Sa Federhaus, das eine zugfeder und eine federhauswelle umfasst
EP2963504A1 (de) * 2014-06-30 2016-01-06 Rolex Sa Federgehäuse für Uhr
EP3176281B1 (de) * 2015-12-02 2019-03-27 Nivarox-FAR S.A. Verfahren zur verbesserung einer eisen-nickel-chrom-mangan-legierung für uhrenanwendungen
JP7133909B2 (ja) * 2016-07-04 2022-09-09 ロレックス・ソシエテ・アノニム 時計用組立体の製造方法、及び該製造方法により得られる時計用組立体
CH714452A2 (fr) * 2017-12-15 2019-06-28 Nivarox Sa Ressort de barillet pour un mouvement horloger d’une pièce d’horlogerie et procédé de fabrication d’un tel ressort.
EP3872576B1 (de) * 2020-02-25 2024-02-21 ETA SA Manufacture Horlogère Suisse Federgehäuse eines uhrwerks mit verdrehter welle

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Publication number Publication date
CN103797425A (zh) 2014-05-14
EP2570862B1 (de) 2014-03-05
EP2570862A1 (de) 2013-03-20
WO2013037870A1 (fr) 2013-03-21
CN103797425B (zh) 2016-08-17
HK1197840A1 (zh) 2015-02-18
JP2014526691A (ja) 2014-10-06
JP5702509B2 (ja) 2015-04-15
RU2559125C1 (ru) 2015-08-10
US9033573B2 (en) 2015-05-19
IN2014CN02738A (de) 2015-07-03
EP2756360A1 (de) 2014-07-23
US20140211596A1 (en) 2014-07-31

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