EP2264551A1 - Differentialzahnradgetriebe für Uhrwerk - Google Patents

Differentialzahnradgetriebe für Uhrwerk Download PDF

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Publication number
EP2264551A1
EP2264551A1 EP09162837A EP09162837A EP2264551A1 EP 2264551 A1 EP2264551 A1 EP 2264551A1 EP 09162837 A EP09162837 A EP 09162837A EP 09162837 A EP09162837 A EP 09162837A EP 2264551 A1 EP2264551 A1 EP 2264551A1
Authority
EP
European Patent Office
Prior art keywords
gear
central shaft
satellite
tube
wheels
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP09162837A
Other languages
English (en)
French (fr)
Other versions
EP2264551B1 (de
Inventor
Huy Van Tran
Ludovic Perez
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.)
Pequignet SA
Original Assignee
Samep Sa - Montres Emile Pequignet
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 Samep Sa - Montres Emile Pequignet filed Critical Samep Sa - Montres Emile Pequignet
Priority to EP09162837.0A priority Critical patent/EP2264551B1/de
Priority to JP2010128088A priority patent/JP5578500B2/ja
Priority to CN2010101992449A priority patent/CN101923313B/zh
Priority to US12/817,059 priority patent/US8251574B2/en
Publication of EP2264551A1 publication Critical patent/EP2264551A1/de
Priority to HK11101532.0A priority patent/HK1147568A1/xx
Application granted granted Critical
Publication of EP2264551B1 publication Critical patent/EP2264551B1/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
    • G04B13/00—Gearwork
    • G04B13/007—Gearwork with differential work
    • G04B13/008—Differentials
    • 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
    • G04B9/00—Supervision of the state of winding, e.g. indicating the amount of winding

Definitions

  • the present invention relates to a differential gear for watch movement comprising a central shaft on which are rotatably mounted first and second wheels, each of which is provided with a toothing arranged to mesh with the toothing of at least one satellite carried by a carrier-satellite , also mounted on the central shaft.
  • the first and second wheels are intended to be engaged with first and second mobiles of the watch movement, the central shaft comprising a toothing intended to be engaged with a third mobile of the watch movement.
  • the present invention relates to a differential gear of this type for controlling a mechanism for displaying the power reserve of a mainspring in a timepiece comprising a cylinder as a motor member.
  • the present invention relates to a watch movement provided with such a differential gear, in particular for controlling a power reserve display mechanism, as well as a timepiece equipped with such a watch movement.
  • This differential gear comprises two large wheels provided, on the one hand, with radial teeth connected kinematically to one end and the other of the mainspring and, on the other hand, toothing teeth arranged to be engaged with a satellite having the shape of a conventional gear.
  • Differential gears of this type are bulky in the sense of their thickness and are therefore little used in wristwatches.
  • a general problem that must be taken into account in the mechanisms of display of the power reserve is the management of the value to be displayed when the mainspring of the barrel is reassembled in full charge, either by an automatic winding mechanism or by manual winding. If reassembly is continued, the barrel generally has a sliding flange to guard against any potential damage, while the power reserve display mechanism includes a stop at one place or another to prevent the display member to turn more.
  • a gear of the differential gear is kinematically connected to the barrel drum which continues to rotate during reassembly, even when the spring has reached full load. It is therefore necessary to provide a system to guard the gears involved in the display of the power reserve of any damage, under these conditions.
  • a main object of the present invention is to propose an alternative to the differential gears known from the prior art, in particular for controlling the power reserve display mechanisms, by proposing a differential gear incorporating a safety against Risks related to the excessive winding of the mainspring, while having a simple and compact structure.
  • the invention also relates to such a differential gear comprising a security against similar risks when it is implemented in a mechanism other than a mechanism for displaying the power reserve.
  • the present invention more particularly relates to a differential gear of the type mentioned above, characterized in that its carrier is made integral in rotation with the central shaft by means of a friction device comprising a tube having a first portion disposed in abutment against the central shaft and at least a second portion disposed in abutment against the planet carrier.
  • the tube may comprise a substantially cylindrical skirt in which at least one first tongue is formed in such a way that it exerts a force having a radial component on the planet carrier, which can be centripetal or centrifugal according to variants of embodiment.
  • the skirt may comprise at least one additional tongue of slightly longer length than the first tongue to define a positioning stop of the tube in relation to a shoulder of the central shaft.
  • the tube may have a base provided with a flange forming an axial retention for one of the wheels.
  • the satellite has a sliding pinion gearing arranged simultaneously in engagement with the teeth of the first and second wheels, being radial.
  • the present invention also relates to a watch movement incorporating a differential gear corresponding to the above characteristics, the movement preferably comprising a barrel housing a mainspring whose one end is kinematically connected to a finishing gear and a second end is kinematically connected to a winding device, the differential gear being arranged to control a mechanism for displaying the power reserve of the mainspring.
  • FIG. 1 is a cutaway perspective view of a differential gear according to a preferred embodiment of the present invention.
  • the figure 2 represents a simplified perspective view of a constituent element of the differential gear of the figure 1 ;
  • the figure 3 represents a simplified sectional view of the element of the figure 2 ;
  • the figure 4 represents a simplified perspective view of a portion of the differential gear of the figure 1 making certain construction details visible, and
  • FIG. 5 is a perspective view of a constituent element of a differential gear according to an alternative embodiment.
  • the figure 1 represents a cutaway perspective view of a differential gear 1 according to a preferred embodiment of the present invention. Specifically, about the front half of the differential gear has been removed to make visible its internal structure.
  • the differential gear 1 comprises a central shaft 2 intended to be mounted on a frame member of a watch movement, the shaft being provided with a pivot at each of its ends 3 and 4.
  • An output gear 5 is cut directly into the mass of the central shaft near one of its ends 3.
  • the pinion could also be formed separately and reported without departing from the scope of the present invention.
  • the pinion is followed by a cylindrical support portion 6, itself followed by a main portion 7 of the shaft, also cylindrical but of smaller diameter and extending to the other end 4 of the shaft .
  • a first input gear 8 of the differential gear, carried by a hub 9, is placed in abutment on the support portion 6, being retained axially by the pinion 5.
  • the hub comprises a base, in which a radial toothing 10 is arranged, the base being surmounted by a barrel 11 on which the first wheel 8 is driven.
  • the length of the support portion 6 is slightly greater than the height of the hub 9.
  • An intermediate tube 12 is then engaged on the main portion 7 of the central shaft 2, covering it substantially to the second end 4 of the latter.
  • the structure of the tube 12 will be described in detail later in connection with the detailed description of the figures 2 and 3 . It already appears from the figure 1 from the cross-sectional view of the tube 12, that the latter has a base 14 provided with an annular rim in the form of a retaining flange 15, followed by a support portion 16 having a thickness of important material, and itself followed by a main portion 17, or skirt, thinner and extending to a shoulder 18 of the central shaft 2, defined by the junction between the support portion 6 of the latter and its main portion 7.
  • a planet carrier 20 is engaged on the main portion 17 of the tube.
  • the planet carrier 20 comprises first and second coaxial rings 21, 22 connected to each other by means of a flange 24. Furthermore, a shaft 25 is carried by the rings, in a direction perpendicular to the direction of the central shaft 2, and carries a satellite 26.
  • the planet carrier 20 also fills the retaining function for a second input wheel 28 of the differential gear, previously engaged on the support portion 16 of the tube.
  • the second input wheel 28 is carried by a hub 29 comprising a base, in which a radial toothing 30 is formed, the base being surmounted by a barrel 31 on which the second wheel 28 is hunted.
  • the hub 29 is, on the one hand, disposed in abutment against the retaining collar 15 while being, on the other hand, retained by the planet carrier 20.
  • the hubs 9, 29 are arranged in opposite directions, so that their teeth are facing one another, so as to cooperate with the satellite 26.
  • one of the wheels is kinematically connected to a first end of the mainspring, either via the barrel drum or the barrel shaft, while the other wheel is kinematically connected to the barrel spring. other end of the mainspring.
  • the changes in the state of charge of the mainspring are taken into account to be transmitted.
  • a mobile display of the power reserve from the output of the differential gear 1, the output gear 5.
  • the figure 2 represents a simplified perspective view of the isolated tube 12 and allows better discerning its structure, especially that of its main portion 17.
  • This latter has a generally cylindrical shape but is constituted, in the present embodiment illustrated by way of non-limiting example, of two pairs of tongues 34, 35, two tongues of the same pair being diametrically opposed with respect to the axis of the tube.
  • the free ends of the tongues all have an extra thickness so that the diameter of the main portion 17 of the tube, at the free ends of the tongues, is similar to the diameter of the opposite end of the main portion 17, that is to say ie that which is connected to the support portion 16.
  • This diameter substantially corresponds to the internal diameter of the ring 21 of the planet carrier 20, as is apparent from FIG. figure 1 .
  • the planet carrier 20 is fitted on the tube 12.
  • the particular structure of the main portion 17 of the tube gives it elastic properties, in particular by deformation of the tongues 35, which allow relative sliding between the tube and the tube. carrier when the torque to be transmitted between these elements exceeds a preset value reached when the mainspring reaches its full load. Below this predefined value, the tabs 35 exert a force having a radial component, centrifugal here, on the planet carrier 20 such that these two elements are integral in rotation.
  • the figure 3 represents a simplified sectional view of the tube 12 of the figure 2 , on which have been schematically different configurations of the tabs 35, to illustrate how their degree of deformation can be adjusted according to the desired force to act on the carrier.
  • the figure 4 represents a simplified perspective view of a portion of the differential gear of the figure 1 making certain construction details visible. Specifically, the first input wheel 8 has been removed to more clearly illustrate the planet carrier 20 and the satellite 26 in accordance with the present preferred embodiment of the present invention.
  • the flange 24 connecting the first and second rings 21, 22 has a plurality of openings 40, in particular to lighten it.
  • arms are used to connect the first and second rings to each other instead of the flange, without departing from the scope of the present invention.
  • the puddle 24 comprises an additional opening 41 in which the satellite 26 is housed, carried by the shaft 25.
  • the satellite 26 has a particular shape, namely that it is similar to that of a sliding pinion, used in the winding mechanisms, in which the conventional Breguet teeth have not been cut.
  • the satellite 26 has a toothing 42 of the sliding pinion type, that is to say a set of teeth oriented in a direction substantially parallel to the axis of rotation of the satellite having a symmetry along this axis.
  • the satellite can mesh with conventional radial gears, which are those carried by the hubs 9 and 29 in the embodiment shown here.
  • the bulk of the differential gear according to the present invention is reduced in the direction of height with respect to a conventional differential gear in which the satellite has the form of a conventional gear with radial teeth.
  • the satellite 26 comprises an annular groove 43 intended here to cooperate with the fingers 44 formed in the flange 24 of the planet carrier 20 to ensure a good positioning of the satellite relative to the planet carrier, and therefore with respect to the first and second input wheels 8 and 28.
  • the figure 5 is a perspective view of a central shaft 60, according to an alternative embodiment, intended to cooperate with a tube as described above.
  • the central shaft 60 has a conical portion 61 intended to cooperate with the ends of the tongues 35, these being thus to be deformed towards the inside and no longer from the outside as was the case in the previous realization.
  • the tube exerts a centripetal force on the central shaft 60 to produce an effect similar to that discussed above.
  • the tube is, in this case, integral in rotation with the planet carrier.
  • the friction force F ensuring the transmission of the rotational movements of the tube to the planet carrier (in the first case) or to the central shaft (in the second case).
  • case as being equal to the product of p by N, where p is the coefficient of friction, depending on the two materials in contact with each other, and N is the radial force exerted by the tube on the carrier or on the central shaft due to the deformation of its tongues 35.
  • the particular structure of the tube allows a relatively accurate adjustment of the value of N, p being known from the moment when the materials concerned were selected.
  • the value of F directly related to the moment of force involved between the two elements in contact, can be adjusted relatively accurately (the moment being equal to the product of F by the radius at the point of application of F, the point contact between the two bodies concerned).
  • the threshold value of the moment of force from which the tube slides relative to the other member involved can be adjusted to be close to the value necessary for the transmission of the moments of force necessary to ensure the proper functioning of the mechanism.
  • corresponding watchmaker which reduces the wear of parts related to friction, compared to known mechanisms of the prior art. Note further that if the tongues 35 are deformed too much in a given direction, they can be brought back in the opposite direction, possibly reversibly depending on the nature of the material used.
  • the carrier is rendered integral in rotation with the central shaft by means of a friction device comprising a tube having a first portion disposed in abutment against the central shaft and at least a second portion disposed in abutment against the planet carrier, without leaving of the scope of the present invention.
  • a friction device comprising a tube having a first portion disposed in abutment against the central shaft and at least a second portion disposed in abutment against the planet carrier, without leaving of the scope of the present invention.
  • the differential gear of the present invention may also be implemented in clock mechanisms other than those intended to display the power reserve.

Landscapes

  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Retarders (AREA)
  • Transmission Devices (AREA)
EP09162837.0A 2009-06-16 2009-06-16 Differentialzahnradgetriebe für Uhrwerk Active EP2264551B1 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP09162837.0A EP2264551B1 (de) 2009-06-16 2009-06-16 Differentialzahnradgetriebe für Uhrwerk
JP2010128088A JP5578500B2 (ja) 2009-06-16 2010-06-03 腕時計機構部のための差動歯車
CN2010101992449A CN101923313B (zh) 2009-06-16 2010-06-12 手表机芯用的差速齿轮
US12/817,059 US8251574B2 (en) 2009-06-16 2010-06-16 Differential gear for watch movement
HK11101532.0A HK1147568A1 (en) 2009-06-16 2011-02-16 Differential gear for watch movement

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP09162837.0A EP2264551B1 (de) 2009-06-16 2009-06-16 Differentialzahnradgetriebe für Uhrwerk

Publications (2)

Publication Number Publication Date
EP2264551A1 true EP2264551A1 (de) 2010-12-22
EP2264551B1 EP2264551B1 (de) 2013-08-07

Family

ID=41152202

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09162837.0A Active EP2264551B1 (de) 2009-06-16 2009-06-16 Differentialzahnradgetriebe für Uhrwerk

Country Status (5)

Country Link
US (1) US8251574B2 (de)
EP (1) EP2264551B1 (de)
JP (1) JP5578500B2 (de)
CN (1) CN101923313B (de)
HK (1) HK1147568A1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012168443A3 (fr) * 2011-06-10 2013-01-31 Haute Ecole Arc Source d'energie mecanique pour mouvement horloger a couple de sortie predefini
EP3584642A1 (de) * 2018-06-18 2019-12-25 Montres Breguet S.A. Einstellmechanismus für anzeigemechanismus eines walzenuhrwerks

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2546706B1 (de) * 2011-07-13 2017-02-22 ETA SA Manufacture Horlogère Suisse Uhrwerk, das ein Modul enthält, welches mit einem Drehteil versehen ist, das in einen anderen Drehteil eingreift, der sich auf einer Basis dreht, auf welcher das Modul montiert ist
CH705836B1 (fr) * 2011-12-02 2016-01-15 Lvmh Swiss Mft Sa Pièce d'horlogerie.
EP3098668B1 (de) * 2015-05-29 2018-10-31 ETA SA Manufacture Horlogère Suisse Gangreserveanzeige für uhr
EP3182217B1 (de) * 2015-12-18 2018-11-14 Montres Breguet S.A. Mechanismus zum einstellen des kupplungsverhältnisses zwischen triebfedern einer uhr
EP3208664B1 (de) * 2016-02-19 2023-08-16 Omega SA Uhrwerk oder uhr ohne magnetische signatur
BE1024256B1 (nl) * 2016-06-02 2018-01-16 Mintiens Benoît Mechanisch uurwerk.

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH263707A (fr) 1947-11-27 1949-09-15 Le Coultre & Cie Montre-bracelet.
US2774252A (en) * 1954-09-04 1956-12-18 Felsa S A Differential gear
EP1139182A1 (de) 2000-03-27 2001-10-04 PARMIGIANI, Mesure et art du temps S.A. Anzeigemechanismus der Gangreserve einer Uhr und mit diesem Mechanismus versehene Uhr
EP1925995A1 (de) * 2006-11-21 2008-05-28 Christophe Claret SA Schlagwerk

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5723880A (en) * 1980-07-18 1982-02-08 Ricoh Elemex Corp Train wheel construction of watch
DE69839116T2 (de) * 1998-07-16 2009-02-05 Eta Sa Manufacture Horlogère Suisse Uhr mit Tourbillon
EP1498789A1 (de) * 2003-07-14 2005-01-19 Eterna SA Vorrichtung zur Anzeige der Gangreserve einer mechanischen Uhr
DE602008003534D1 (de) * 2008-04-30 2010-12-30 Cartier Creation Studio Sa Mechanismus zur Vermeidung der Gangvariationen aufgrund der Schwerkrafteinwirkung auf eine Reguliervorrichtung mit Unruh-Spiralfeder und mit diesem Mechanismus ausgestattete Uhr

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH263707A (fr) 1947-11-27 1949-09-15 Le Coultre & Cie Montre-bracelet.
US2774252A (en) * 1954-09-04 1956-12-18 Felsa S A Differential gear
EP1139182A1 (de) 2000-03-27 2001-10-04 PARMIGIANI, Mesure et art du temps S.A. Anzeigemechanismus der Gangreserve einer Uhr und mit diesem Mechanismus versehene Uhr
EP1925995A1 (de) * 2006-11-21 2008-05-28 Christophe Claret SA Schlagwerk

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012168443A3 (fr) * 2011-06-10 2013-01-31 Haute Ecole Arc Source d'energie mecanique pour mouvement horloger a couple de sortie predefini
EP3584642A1 (de) * 2018-06-18 2019-12-25 Montres Breguet S.A. Einstellmechanismus für anzeigemechanismus eines walzenuhrwerks
CN110618598A (zh) * 2018-06-18 2019-12-27 蒙特雷布勒盖股份有限公司 用于具有滚轮的钟表显示机构的调节机构
CN110618598B (zh) * 2018-06-18 2021-02-19 蒙特雷布勒盖股份有限公司 用于具有滚轮的钟表显示机构的调节机构
US11543778B2 (en) 2018-06-18 2023-01-03 Montres Breguet S.A. Adjustment mechanism for timepiece display mechanism with rollers

Also Published As

Publication number Publication date
CN101923313A (zh) 2010-12-22
US20100315908A1 (en) 2010-12-16
CN101923313B (zh) 2013-03-20
JP5578500B2 (ja) 2014-08-27
US8251574B2 (en) 2012-08-28
HK1147568A1 (en) 2011-08-12
JP2011002451A (ja) 2011-01-06
EP2264551B1 (de) 2013-08-07

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