EP2420899B1 - Federhaus für Uhren mit automatischer Aufziehfunktion - Google Patents

Federhaus für Uhren mit automatischer Aufziehfunktion Download PDF

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Publication number
EP2420899B1
EP2420899B1 EP10173354.1A EP10173354A EP2420899B1 EP 2420899 B1 EP2420899 B1 EP 2420899B1 EP 10173354 A EP10173354 A EP 10173354A EP 2420899 B1 EP2420899 B1 EP 2420899B1
Authority
EP
European Patent Office
Prior art keywords
friction surfaces
friction
drum
mainspring
forming
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
EP10173354.1A
Other languages
English (en)
French (fr)
Other versions
EP2420899A1 (de
Inventor
Serge Nicoud
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
Original Assignee
ETA SA Manufacture Horlogere Suisse
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 ETA SA Manufacture Horlogere Suisse filed Critical ETA SA Manufacture Horlogere Suisse
Priority to EP10173354.1A priority Critical patent/EP2420899B1/de
Priority to JP2011177395A priority patent/JP5877668B2/ja
Priority to US13/212,764 priority patent/US8573832B2/en
Priority to CN201110237465.5A priority patent/CN102375398B/zh
Publication of EP2420899A1 publication Critical patent/EP2420899A1/de
Priority to HK12108933.9A priority patent/HK1168428A1/xx
Priority to JP2015248238A priority patent/JP6138899B2/ja
Application granted granted Critical
Publication of EP2420899B1 publication Critical patent/EP2420899B1/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
    • 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
    • G04B1/185—Friction clutch between spring and spring cylinder
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B5/00—Other centrifuges
    • B04B5/02—Centrifuges consisting of a plurality of separate bowls rotating round an axis situated between the bowls
    • 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 present invention relates to the field of watchmaking. It relates more specifically to a barrel for equipping a timepiece with automatic winding. It also relates to a timepiece equipped with such a barrel.
  • Barrels for timepieces with automatic winding conventionally comprise a drum in which is housed a motor spring wound spirally around a barrel shaft.
  • the mainspring is not fixed to the side wall of the drum, but frictionally coupled, by means of its last turn , using an elastic blade called sliding flange.
  • the friction coupling between the mainspring and the side wall of the drum must be calculated so that beyond a maximum engine torque determined, the last turn slides along said wall and thus decreases the tension of the mainspring.
  • the surface condition of the inner side wall of the drum as well as its lubrication are factors that strongly influence the operation of this friction clutch. Another determining factor is the geometry of the inner sidewall.
  • the inner side wall of the drum has friction surfaces, alternating with cutouts in the form of notches in which the end of the mainspring abuts.
  • the combination of friction and abutment effects of the last turn on the side wall achieves maximum driving torque, and therefore a large power reserve.
  • notches in the inner side wall of the drum contributes to the wear phenomenon of the barrel. Indeed, the notches form sharp sharp corners located in the upstream and downstream limit of the friction surfaces with respect to the sliding direction of the last turn, that is to say at the exit and input, respectively, notch. On these sharp sharp angles, the pressures of the mainspring are very high. They can then dull quickly.
  • sharp sharp angles limiting the friction surfaces upstream side with respect to the sliding direction of the last turn are mainly responsible for the generation, by wear, particles accelerating the phenomenon of 'wear. Indeed, these angles play an active role in the friction coupling, since the end of the last turn abuts against these protruding angles out of notch, unlike the sharp angles protruding notch entry, which are practically passive in the friction coupling.
  • both the sharp edges protruding at the notch entry and notch exit have an important role in the degradation of the surface by wear, even if the first do not play an active stop in the friction coupling between the last turn of the motor spring and the inner side wall of the drum.
  • the investigations carried out in the context of this invention therefore clearly show the existence of an unknown wear problem at the entrance of notch, and an explanation is advanced to explain this phenomenon.
  • the object of the present invention is to remedy this wear problem by proposing an internal drum side wall geometry that does not include passive sharp edges. More specifically, the invention relates to a cylinder for a timepiece with winding automatic as defined by claims 1 and 3 of the patent.
  • the timepiece cylinder with automatic winding represented in figure 1 and referenced as a whole 1 conventionally comprises a circular drum AA with axis, provided with an inner side wall 11, in which is housed a motor spring 20 forming a spiral winding around a barrel shaft 30.
  • motor spring 20 is fixed by its inner end to a bung 31, integral in rotation with the barrel shaft 30.
  • the bung 31 is provided with a fixing hook 32.
  • the motor spring 20 has an outer turn 21, which is frictionally coupled to the wall
  • an elastic blade 40 called sliding flange, is fixed to the outer end of the motor spring 20 by welding, riveting or any other method known to those skilled in the art. interposed
  • the motor spring 20 has an outer turn 21, which is frictionally coupled to the wall
  • an elastic blade 40 called sliding flange
  • the sliding flange 40 Interposed between the outer turn 21 and the penultimate turn of the motor spring 20, the sliding flange 40 exerts on the outer turn 21 a stress tending to press against the inner side wall 11 of the drum 10.
  • the flange sliding 40 is interposed between the inner side wall 11 of the drum 10 and the outer turn 21 of the motor spring 20, and is itself pressed against said wall. The friction coupling thus formed between the motor spring 20 and the drum 10 makes it possible to arm the motor spring 20 to a maximum determined torque. Beyond this limit value, the outer turn 21 slides against the wall 11, thus reducing the tension and the risks of rupture of the mainspring 20.
  • the inner sidewall 11 of the drum 10 has friction surfaces 12 alternating with notch-shaped locking structures 13.
  • the friction surfaces 12 extend circularly with respect to the axis AA of the drum 10.
  • the notches 13 comprise two flanks 14a and 14b, respectively at the entrance and at the notch exit, cutting the friction surfaces 12. It is specified that the entry and the exit of the notches 13 are defined with respect to the direction of sliding of the outer turn 21 of the motor spring 20 against the wall 11, indicated by an arrow on the Figures 1 and 2 .
  • the outer turn 21 of the motor spring 20 slides against the wall 11, its end thus enters a notch 13 by the sidewall 14a and leaves the side 14b.
  • flanks 14b at the outlet of notches 13 are active in the friction coupling between the mainspring 20 and the drum 10. They are intended to oppose the sliding movement of the end of the motor spring 20 along the inner side wall 11, forming locking surfaces against which the end of the motor spring 20 abuts. Their inclination is optimized for this purpose.
  • the flanks 14b at the outlet of the notches 13 intersect the friction surfaces 12 on the upstream side with respect to the sliding direction of the outer turn 21, forming a projecting angle 15b whose function is also to retain the sliding of the motor spring 20.
  • the protruding angles 15b are preferably sharp corners because they act on the sliding of the motor spring 20 by friction effect, which is even higher than the angle is sharp.
  • sharp angle is meant an angle having a radius of curvature zero or low.
  • the radius of curvature of such an angle is between 0.02 and 0.1 mm
  • the salient angle 15b, which limits the friction surfaces 12, may alternatively be slightly rounded. Its effect of opposition to the sliding movement of the motor spring 20 is then substantially reduced, due to the decrease in friction.
  • the flanks 14a at the entrance of notches 13 are passive in the friction coupling between the mainspring 20 and the drum 10. They cut the friction surfaces 12 downstream side with respect to the direction of sliding of the outer turn 21, forming a projecting angle 15a.
  • the projecting angles 15a are rounded.
  • rounded corner is meant an angle having a high radius of curvature with respect to the sharp angle.
  • the angles 15a at the entrance of notches 13 have a radius of curvature greater than 0.15 mm This characteristic of the cylinder 1 according to the invention reduces the general wear of the inner side wall 11 and the mainspring 20.
  • the friction of the motor spring 20, and in particular of its end is small on these rounded corners 15a in comparison with the friction on the sharp corners 15b, because the contact pressure is lower.
  • the wear of the angles 15a at the entrance of notches 13 and the phenomenon of self-amplification of the wear are reduced.
  • the increase in the radius of curvature of the angle also allows a better distribution of the lubricant. avoiding the formation of a deposit functional in the angle formed by the notch inlet flank 14a and the notch bottom 13.
  • the friction coupling between the motor spring 20 and the inner side wall 11 is unaffected by the rounded profile angles 15a at the entrance of notches 13, because they are passive in the friction coupling. In the long run, the effect is even positive since the reduction of the wear of the motor spring 20 and the inner side wall 11, hinders the degradation of the friction coupling over time. The longevity of the barrel 1 is increased.
  • FIG 2 represents a second embodiment of the barrel according to the invention.
  • the timepiece cylinder with automatic winding represented in figure 2 and referenced as a whole 1 is distinguished from the barrel described above by the geometry of the inner side wall 11 of the drum 10.
  • the inner side wall 11 has friction surfaces 12 alternating with locking structures. These form steps 16, not notches 13, having a flank 17.
  • the friction surfaces 12 extend slightly spirally with respect to the axis AA of the drum 10.
  • the flanks 17 intersect the friction surfaces 12 forming a projecting angle 18a, which limits them upstream side with respect to the sliding direction of the outer turn 21, and a re-entrant angle 18b, which limits them downstream side.
  • the flanks 17 and the projecting angles 18a are active in the friction coupling between the motor spring 20 and the drum 10. For this reason, and as explained above, the projecting angles 18a are preferably sharp corners, but can also be alternatively, slightly rounded.
  • the passive protruding angles with respect to the friction coupling between the motor spring 20 and the inner side wall 11 of the drum 10, are totally absent.
  • the friction surfaces 12 are limited on the downstream side with respect to the sliding direction of the outer turn 21, by a re-entrant angle 18b, sharp or rounded, having no function in the friction coupling.
  • This mode embodiment represents a limiting case of the embodiment described above, in which the projecting angles 15a at the notch inlet 13 have an infinite radius of curvature and the notch inlet 13 is completely eliminated.
  • the barrel 1 thus described has the same advantages of reducing wear and increasing longevity, that the barrel 1 described next to the figure 1 .

Landscapes

  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Springs (AREA)

Claims (5)

  1. Federhaus für ein Zeitmessgerät mit automatischem Aufzug, umfassend eine Trommel (10) mit einer Achse (AA), die mit einer inneren Seitenwand (11) versehen ist, die Reiboberflächen (12) im Wechsel mit Verriegelungsstrukturen (13, 16) aufweist, die an der Grenze der Reiboberflächen (12) vorstehende Ecken (15a, 15b) bilden, und eine Zugfeder (20), die eine Wicklung mit einer äußeren Windung (21) bildet, die reibschlüssig mit der inneren Seitenwand (11) gekoppelt ist und im Fall einer Überspannung der Zugfeder (20) an der inneren Seitenwand (11) frei gleiten kann, wobei die Strukturen Rasten (13) bilden, die eine Flanke (14a) am Einlass aufweisen, die die Reiboberflächen (12) stromabwärts der Gleitrichtung der äußeren Windung (21) schneidet, indem sie eine abgerundete vorstehende Ecke (15a) bilden; und wobei die vorstehende Ecke (15a) einen Krümmungsradius größer als 0,15 mm besitzt, und die Rasten (13) eine Flanke (14b) am Ausgang aufweisen, die so geneigt ist, dass sie sich durch Reibung der Gleitbewegung des Endes der Zugfeder widersetzt, wobei die Flanke (14b) die Reiboberflächen (12) stromaufwärts der Gleitrichtung der äußeren Windung (21) schneidet, indem sie eine vorstehende Ecke (15b) bildet, deren Krümmungsradius null ist oder im Bereich von 0,02 bis 0,1 mm liegt.
  2. Federhaus nach Anspruch 1, dadurch gekennzeichnet, dass sich die Reiboberflächen (12) kreisförmig in Bezug auf die Achse AA der Trommel (10) erstrecken.
  3. Federhaus für ein Zeitmessgerät mit automatischem Aufzug, umfassend eine Trommel (10) mit Achse (AA), die mit einer inneren Seitenwand (11) versehen ist, die Reiboberflächen (12) im Wechsel mit Verriegelungsstrukturen (13, 16) aufweist, die an den Grenzen der Reiboberflächen (12) zurückspringende Ecken bilden, und eine Zugfeder (20), die eine Wicklung mit einer äußeren Windung (21) bildet, die mit der inneren Seitenwand (11) reibschlüssig gekoppelt ist und bei einer Überspannung der Zugfeder (20) an der inneren Seitenwand (11) frei gleitet, wobei die Strukturen Stufen (16) bilden, die eine Flanke (17) aufweisen, die die Reiboberflächen (12) stromaufwärts der Gleitrichtung der äußeren Windung (21) schneiden, indem sie eine der zurückspringenden Ecken (18b) bilden,
    dadurch gekennzeichnet, dass die Reiboberflächen (12) in Bezug auf die Achse (AA) der Trommel (10) spiralförmig verlaufen.
  4. Federhaus nach Anspruch 3, dadurch gekennzeichnet, dass die Flanke (17) die Reiboberflächen (12) stromabwärts der Gleitrichtung der äußeren Windung (21) schneidet, indem sie eine vorstehende Ecke (18a) bildet.
  5. Zeitmessgerät, das mit einem Werk mit automatischem Aufzug versehen ist und durch ein Federhaus nach einem der Ansprüche 1 bis 4 mit Energie versorgt wird.
EP10173354.1A 2010-08-19 2010-08-19 Federhaus für Uhren mit automatischer Aufziehfunktion Active EP2420899B1 (de)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP10173354.1A EP2420899B1 (de) 2010-08-19 2010-08-19 Federhaus für Uhren mit automatischer Aufziehfunktion
JP2011177395A JP5877668B2 (ja) 2010-08-19 2011-08-15 自動巻き時計の香箱
US13/212,764 US8573832B2 (en) 2010-08-19 2011-08-18 Barrel for a self winding timepiece
CN201110237465.5A CN102375398B (zh) 2010-08-19 2011-08-18 用于自上弦时计的发条盒
HK12108933.9A HK1168428A1 (en) 2010-08-19 2012-09-12 Barrel for a self-winding timepiece
JP2015248238A JP6138899B2 (ja) 2010-08-19 2015-12-21 自動巻き時計の香箱

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP10173354.1A EP2420899B1 (de) 2010-08-19 2010-08-19 Federhaus für Uhren mit automatischer Aufziehfunktion

Publications (2)

Publication Number Publication Date
EP2420899A1 EP2420899A1 (de) 2012-02-22
EP2420899B1 true EP2420899B1 (de) 2018-12-19

Family

ID=43500993

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10173354.1A Active EP2420899B1 (de) 2010-08-19 2010-08-19 Federhaus für Uhren mit automatischer Aufziehfunktion

Country Status (5)

Country Link
US (1) US8573832B2 (de)
EP (1) EP2420899B1 (de)
JP (2) JP5877668B2 (de)
CN (1) CN102375398B (de)
HK (1) HK1168428A1 (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2657794B1 (de) * 2012-04-25 2017-02-01 ETA SA Manufacture Horlogère Suisse Federwelle und Zugfeder
EP2977827B1 (de) * 2014-07-22 2017-11-15 Montres Breguet SA Federgehäuse einer Uhr mit verbesserter Kraftübertragung
EP3220206B1 (de) 2016-03-16 2020-09-30 Rolex Sa Übertragungsvorrichtung für uhr

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS48104363U (de) * 1972-03-06 1973-12-05
JPS4910573U (de) * 1972-04-26 1974-01-29
JPS49135654A (de) * 1973-04-27 1974-12-27
JPS5448798U (de) * 1977-09-07 1979-04-04

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US137437A (en) * 1873-04-01 Improvement in mainspring safety attachments for watches
DE1252591B (de) * 1967-10-19 W Schwab-Feller Uhrfederfabrik ,Phma", Buren/Aare (Schweiz) Federzaun fur die Zugfeder von Uhrwerken
US385908A (en) * 1888-07-10 Watch-mains pr ing
US1677045A (en) * 1928-07-10 Spuing motor
US1522073A (en) * 1923-10-13 1925-01-06 Daniel E Odom Spring motor
CH280369A (fr) * 1949-03-08 1952-01-15 Zodiac Dispositif indicateur de développement du ressort moteur pour montre à remontage automatique.
CH494421A (fr) * 1968-01-26 1970-09-15 Omega Brandt & Freres Sa Louis Barillet pour pièce d'horlogerie à remontage automatique
JPS498358B1 (de) * 1969-10-29 1974-02-26
JPS4910574U (de) * 1972-04-26 1974-01-29
CH596590B5 (de) * 1975-01-23 1978-03-15 Pforzheimer Uhren Rohwerke
JPH09182878A (ja) * 1995-12-28 1997-07-15 Seikouken Kk 手巻き式ゼンマイ駆動ユニット
CH699988A2 (fr) * 2008-11-28 2010-05-31 Patek Philippe Sa Geneve Organe moteur pour mouvement horloger.

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS48104363U (de) * 1972-03-06 1973-12-05
JPS4910573U (de) * 1972-04-26 1974-01-29
JPS49135654A (de) * 1973-04-27 1974-12-27
JPS5448798U (de) * 1977-09-07 1979-04-04

Also Published As

Publication number Publication date
JP5877668B2 (ja) 2016-03-08
CN102375398B (zh) 2014-03-19
US8573832B2 (en) 2013-11-05
US20120044789A1 (en) 2012-02-23
HK1168428A1 (en) 2012-12-28
CN102375398A (zh) 2012-03-14
JP6138899B2 (ja) 2017-05-31
JP2016075701A (ja) 2016-05-12
JP2012042469A (ja) 2012-03-01
EP2420899A1 (de) 2012-02-22

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