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
  • G04B27/00—Mechanical devices for setting the time indicating means
  • G04B27/001—Internal gear therefor, e.g. for setting the second hand or for setting several 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
  • G04B13/00—Gearwork
  • G04B13/02—Wheels; Pinions; Spindles; Pivots
  • G04B13/027—Wheels; Pinions; Spindles; Pivots planar toothing: shape and design
• • 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
  • G04B11/00—Click devices; Stop clicks; Clutches
  • G04B11/001—Clutch mechanism between two rotating members with transfer of movement in both directions, possibly with limitation on the transfer of power
  • G04B11/003—Clutch mechanism between two rotating members with transfer of movement in both directions, possibly with limitation on the transfer of power with friction member, e.g. with spring action
• • 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
  • G04B13/02—Wheels; Pinions; Spindles; Pivots
  • G04B13/021—Wheels; Pinions; Spindles; Pivots elastic fitting with a spindle, axis or shaft
• • 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
  • G04B19/00—Indicating the time by visual means
  • G04B19/06—Dials
  • G04B19/18—Graduations on the crystal or glass, on the bezel, or on the rim
• • 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
  • G04B27/00—Mechanical devices for setting the time indicating means
  • G04B27/02—Mechanical devices for setting the time indicating means by making use of the winding means
• • 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
  • G04B3/00—Normal winding of clockworks by hand or mechanically; Winding up several mainsprings or driving weights simultaneously
  • G04B3/04—Rigidly-mounted keys, knobs or crowns
  • G04B3/041—Construction of crowns for rotating movement; connection with the winding stem; winding stems
• • 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
  • G04B19/00—Indicating the time by visual means
  • G04B19/28—Adjustable guide marks or pointers for indicating determined points of time
  • G04B19/283—Adjustable guide marks or pointers for indicating determined points of time on rotatable rings, i.e. bezel

Definitions

• the present invention relates to a control system for a rotating member of a timepiece, and more particularly for a flange.
• the highlights consist of an annular piece disposed at the periphery of a dial, and which partially overlap the edge of the latter. They may be integral or not with a bezel to which is adjusted the ice of the watch. Some highlights are rotatable independently of the bezel, and located completely under the ice.
• the most common control system is to use a crown provided with a pinion terminal at its end, which meshes with a notch arranged on a lower surface of the flange to drive the latter in rotation.
• the patent FR1027587 for example describes such a control system by co-operating teeth of the flange and a crown pinion, where the gearing is only possible in a working position pulled from the ring, and a spring-loaded pin acts as an indexing element for the angular positions of the flange.
• a disadvantage of this type of control system is that it requires a relatively deep toothing to ensure the latching between the toothing of the crown pinion of the crown and the detent of the flange. Therefore, the overall height is quite important and increases the size of the housing for housing such a system ensuring the transmission between the rotation of the crown and that of the flange. Furthermore, the mutual cooperation of the two teeth involved in the gear mechanism makes this transmission system on the one hand quite noisy, and on the other hand relatively inconvenient for fine adjustments. Indeed, the angular indexing of the flange after actuation of the crown is conditioned by the number of teeth of the latter's pinion, the diameter of which is generally much smaller than that of the flange. However, it is difficult to machine a large number of teeth on a small part, and the number of teeth of this part greatly influences the gear ratios, ie the reduction of the angular stroke of the flange relative to to that of the crown.
• the document CH691 199 discloses, for example, a control ring arranged to actuate, in a predefined axial working position, in rotation a rod provided with a toothless terminal knob cooperating with a peripheral bead of a timer wheel, and consequently all the clockwork during a time setting.
• An object of the present invention is therefore to provide an alternative solution for a control system, including a flange, and more generally a rotating member for a timepiece, devoid of these known limitations.
• the subject of the invention is a control system for a rotating member of a timepiece, comprising a control member for actuating said rotating member, and a transmission device between said control member and said rotating member.
• the control system is characterized in that the transmission device is a hybrid gear device comprising a first member movable about a first axis of rotation provided with a drive roller of elastomeric material, and a second member movable about a second axis of rotation provided with a rolling toothing, the driving roller co-operating with friction with the rolling teeth.
• the invention also relates to each element of the timepiece control system comprising a part of the transmission device taken separately, namely:
• a control member of a timepiece characterized in that it comprises a first member movable about a first axis of rotation on which is mounted a drive roller of elastomeric material;
• a rotating member of a timepiece movable about a second axis of rotation characterized in that it comprises a second movable member having a rolling toothing.
• a first advantage of the proposed solution is to confer a significant gain in overall height thanks to the flattened profile of the running surface of the driving mobile or the driven mobile of the hybrid gear device described, without however reducing the quality of the transmission. nor its reliability over time.
• Another advantage of the proposed solution is that it imparts a silent gear mechanism thanks to the drive roller made of elastomeric material, whose flexibility avoids jerkiness and rattling gear noise, unlike mutual cooperation teeth of mobile leading and led a solution known from the prior art.
• FIG. 1A, 1B and 1C respectively show a top view, in section and in three dimensions of a middle part for housing the rotary flush control system according to a preferred embodiment of the invention
• FIG. 2A, 2B and 2C respectively show a top view, in section and in three dimensions of a flange rotating according to a preferred embodiment of the invention
• FIG. 3A, 3B and 3C respectively show a profile view, in section and in three dimensions of a control ring according to a preferred embodiment of the invention
• FIG. 4 is a sectional view of the rotary flush control system according to a preferred embodiment of the invention, integrated in a wristwatch;
• FIG. 5 is a detailed view of the running surface used for the flange according to the preferred embodiment of Figures 2A, 2B and 2C.
• a roller is a piece traditionally formed by a steel roller, and which aims to replace sliding friction with rolling friction (see the illustrated professional dictionary of GA Horlogerie, Berner, p. 518, reference 2221).
• a drive roller for a part intended to transmit rotational movement by rolling friction with another moving part.
• FIGS. 1A, 1B and 1C respectively show a top view, in section and in three dimensions, of a caseband intended to receive the control system according to the invention, formed by a ring 1 and a flange 3, illustrated in Figures 2A, B, C and 3A, B, C which follow.
• the middle part 5 comprises two pairs of horns 53 for attaching a bracelet, as well as a bearing surface 50 forming a bearing surface for the rotating flange 3.
• first threaded through hole 51 and a second threaded through hole 52 preferably for mounting crown tubes.
• At each of these threaded holes are arranged respectively a first notch 501 and a second notch 502, visible in Figure 1 A. These notches allow to pass a key for mounting or changing various components of the crown 1 assembled to the middle 5 during an after-sales service, including roller drive 25 on its axis.
• FIG. 1B shows a sectional view of the middle part 5 along the first cutting axis BB of FIG. 1A, passing through the first threaded through hole 51, on which the thickness of the bearing surface 50 can be seen, while on Figure 1 C one distinguishes the same elements as in Figure 1 A, except the first and second notches 501, 502.
• FIG. 2A shows a view from above of the flange 3 intended to be mounted on the middle part of FIGS. 1A, 1B, and 1C above, on which is distinguished its upper face, consisting of an oblique display surface 34, here devoid of display elements, but that can be discerned later in Figure 4, and the upper surface 371 of a peripheral flange 37, intended to provide a bearing surface for a ring element disposed to its periphery.
• FIG. 2B shows the flange 3 along the second cutting axis CC of FIG. 2A, and shows the peripheral flange 37, and the upper surface 371 as well as the lower surface 372 thereof, the oblique display surface.
• FIG. 2C illustrates the same constituent elements of the flange 3 as FIG. 2A described above, namely the oblique display surface 34, as well as the peripheral flange 37 and its upper surface 371.
• FIG. 3A illustrates a profile view of a ring 1 according to a preferred embodiment of the invention.
• a ring 1 is a non-screwed crown having only one axial position relative to the middle part, it will be understood that the hybrid gear system as well as the arrangement of a drive roller 25 on one side.
• the crown is independent of the crown structure employed, and thus a screw-type crown could quite well be used also without departing from the scope of the invention nor impose structural limitations on the proposed hybrid gear mechanism between the idler wheel. drive 25 and the rolling teeth 32 of the flange 3, or any other movable element to be driven.
• the ring 1, mobile about a first axis of rotation 10, is conventionally composed of a tube 13, intended to be mounted to the middle part 5 by driving or screwing, above which is arranged a cover 1 1 actuated by the the user of the watch.
• the drive roller 25 At the proximal end of the ring, on the left of FIGS. 3A, 3B, and 3B, is arranged the drive roller 25, in the form of a first O-ring O-ring or a overmolded seal.
• the advantage of using an O-Ring type seal is that it can use the drive roller 25 as a wear part, replaceable independently of the rest of the ring 1.
• the drive roller 25 is made of elastomeric material precisely to increase the frictional forces and improve the quality of the transmission of the bearing, in the manner of a tire of a vehicle on the road surface.
• a friction ring 14 which is in the form of a second preferred section seal rectangular to maximize the friction surface with each of the pieces.
• the friction surfaces are then in an annular form in each of the friction planes.
• O-ring type O-ring or also consist of another molded joint, it would nevertheless require a greater axial compression of the seal to ensure the same friction forces.
• This friction ring 14 aims to increase the rotation torque of the flange 3 and thus eliminate parasitic and involuntary movements of the flange 3 during handling of the crown 1.
• the ring 1 is not a screwed crown, such a friction ring 14 is particularly advantageous for a screw-retained crown having a plurality of axial positions, in particular during the transition from a locked or screwed position. "T0" at a position pulled or unscrewed "T1" setting.
• the advantage of a screwed crown would be to block on demand and by screwing the rotation of the flange 3, to prevent accidental movement.
• FIG. 3B shows a sectional view along the third cutting axis AA of FIG. 3A, where it can be seen, in addition to the other elements already described in FIG. 3A, a central cylinder 12 tapped to be connected to a rod control, as well as the axial skirt 1 1 1 and the lid 1 12 of the hood 1 1.
• a third seal 16 also of toric shape, covered by a deckring 15.
• the third O-ring 16 is moreover maintained axially by means of a spacer 17.
• the elements of the ring 1 illustrated are similar to those already described with reference to FIG.
• FIG. 4 shows a sectional view of the detail of the control mechanism according to the preferred embodiment of the invention, in which the flange 3 and the control ring 1, illustrated separately by the preceding FIGS. 2 and 3, are now integrated in the middle part. 5 of a watch.
• the hybrid gear device of the proposed rotary drive control system relates to the transmission of a rotational movement between a first movable element and a second movable element about their respective axis of rotation by means of a rolling friction gear between the two moving parts, one being equipped at its periphery with a preferably smooth elastomeric material and the other with a harder material, such as for example metal or steel and preferably having a toothing.
• the gear used in the context of the present invention is thus described as a "hybrid" not only for this first reason of potential mismatch between the two materials responsible for the transmission, but also because it is possible to co-operate with surfaces of different nature, such as a notch, a knurling and or a rough surface with a smooth surface, such as that of the drive roller 25.
• surfaces of different nature such as a notch, a knurling and or a rough surface with a smooth surface, such as that of the drive roller 25.
• the cooperation of elements of different nature that is to say, of which the materials and surface profiles are heterogeneous, is unusual for a traditional clockwork gear transmission mechanism where in general the metal teeth of a first mobile are provided to cooperate with another metal toothing of another mobile.
• no toothing is ever used as a running surface either.
• the second movable member 31 may be considered as the body flange 3, referenced in Figure 4, while the flange 3 further comprises here a Teflon washer 33 arranged above its peripheral flange 37.
• This Teflon washer 33 bears on the upper surface 371 thereof, in order to minimize friction with the bezel 6.
• the first movable element, which is integral in rotation with the drive roller 25, is formed here by the central barrel 2 of the ring 1, also integral in rotation with the cap 1 1 of the ring 1 following the screwing of its threaded upper part. 21 in the threaded blind hole 121 of the central cylinder 12.
• the driving roller 25 is arranged on a driving element, that is to say the central barrel 2 integral in rotation with the ring 1, while the rolling teeth 32 is arranged on a driven element, that is to say, the 2nd mobile element 31 of the flange 3.
• a driving element that is to say the central barrel 2 integral in rotation with the ring 1
• the rolling teeth 32 is arranged on a driven element, that is to say, the 2nd mobile element 31 of the flange 3.
• a driving roller 25 of elastomeric material is advantageous over the drive member to improve the efficiency of transmission and to reduce production costs, especially when the circumference of the latter, in this case close to that of its lower part 23 - tapped for the possible fixing of a control rod - is significantly lower than the circumference of the driven element, as the flange 3, which saves elastomer material, and also simplifies the machining of the movable member 31 and the central barrel 2.
• the ratio of the circumferences of the driving element relative to the driven element allows to define a continuous gear ratio, unlike a ratio between numbers of teeth between a mobile leading and a driven mobile, which is a function of discrete values. It dispenses parallel pointed and deep traditional teeth and so suddenly indexing.
• the proposed solution also provides a very precise positioning of the mutual relative axes of rotation of the parts, also often called "spacing", these positioning sets can be recovered thanks to the plastic properties of the elastomer drive roller 25 which will then be more or less compressed against the rolling surface of the mobile to drive in rotation. The mounting of the control device is thus simplified, which allows additional productivity gains.
• control ring 1 is a ring having only one axial position vis-a-vis the middle part, which comprises a cover 1 1 projecting out of the caseband 5 and which can be actuated in rotation by the user of the watch.
• the cover 1 1 is mounted above a tube 13, here provided with a thread 131 for its screw connection to the middle 5 in the first threaded through hole 51 in which is introduced a central cylinder 12 secured to the cover 1 1, and which is provided at its end with a threaded blind hole 121 for assembly to a central barrel 2, for its part having a threaded upper portion 21.
• the central barrel 2 thus forms a first movable member of the control member that constitutes the ring 1; it is rotatable relative to the tube 13 screwed to the middle part 5 and it is at its proximal end, that is to say the threaded lower part 23 for the possible addition of a control rod - not shown - that is arranged the drive roller 25 of elastomeric material, replacing a pinion terminal as on traditional crowns.
• the driving roller 25 formed here by a first O-ring which is arranged in a groove delimited by two axial abutments 24, arranged in a plane perpendicular to the first axis of rotation 10 of the crown, which is also that of the central barrel 2 and which can come from material with the central barrel 2 or consist of washers mounted on the latter.
• a second seal of preferably rectangular or square section, is arranged around the central barrel 2, bearing on a shoulder 22.
• This second seal constitutes the friction ring 14, already visible in Figures 3A, 3B and 3C previously described, and which is arranged between the central barrel 2 and the tube 13 screwed to the middle part 5 to increase the actuating torque of the ring 1, This is to avoid imposing any parasitic movement on the flange 3.
• the friction ring 14 is here held axially between the shoulder 22 of the central barrel 2, which can also be formed by a washer, even possibly the other face of the washer. used as axial stop 24 for the drive roller 25, and the lower end 132 of the tube 13 screwed to the middle part 5.
• this friction ring therefore makes it more difficult to actuate the crown 1 in rotation, and consequently more effectively secures the angular position of the flange 3. According to the preferred embodiment described, it can be seen that this friction ring 14 is interposed between the tube
• the protruding portion of the ring 1 out of the middle part 5 shows an enlarged view of the detail of the elements illustrated in FIG. 3B, namely a central cylinder 12 threaded connected to the central barrel 2, the axial skirt 1 1 1 and the lid 1 12 of the hood, as well as the sealing elements of the crown head vis-à-vis the interior of the middle part, that is to say a third O-ring 16, covered by a deckring 15, and maintained by Moreover, these elements have no influence on the hybrid gear mechanism proposed in the context of the present invention, and in particular on the arrangement of the drive roller. 25.
• the driving roller 25 made of elastomeric material cooperates with a rolling toothing 32 arranged on the lower face of a flange body 3, which constitutes a preferred embodiment of a rotating member. in the context of the invention.
• the flange 3 is composed of a second movable element 31, that is to say the body of the flange on which is arranged the rolling toothing 32, partially covering the edge of the dial 4, and which provided with a peripheral rim 37 ring on which is mounted a Teflon washer 33 to minimize friction with the bezel 6, which is also covered with the glass 7 and mounted notch on the middle part 5.
• a seal formed by a fourth O-ring is arranged between the bezel 6 and the middle part 5, and similarly, a fifth O-ring 81 is interposed between the bottom 8 and the middle part 5.
• the rolling toothing 32 extends essentially in a parallel gear plane. at the first axis of rotation 10 of the ring 1, that is to say perpendicular to the second axis of rotation 30 of the flange 3. Consequently, the hybrid gear mechanism acts as a return without requiring the use of inclined teeth to gain space in height.
• a hybrid gear device comprising an inclined bearing toothing 32, in particular 45 degrees relative to the axis of rotation of the driven or driven mobile, to effect a 90 degree return, or arrange a rolling toothing 32 extending not in a plane but in a cylindrical portion at the periphery of a mobile cooperating with a mobile rotating along a parallel axis, to ensure the transmission in rotation a second mobile rotating along a parallel axis of rotation.
• FIG. 5 shows the detail of a rolling toothing 32 according to a preferred embodiment, where it is arranged on the lower face of the second mobile 31 of the flange and extends along an annular surface situated in a perpendicular plane the second axis of rotation 30, that is to say the gear plane 35, referenced in Figure 3B.
• the rolling toothing 32 is formed here of a flat toothing 36, whose tooth profile is greater than 90 degrees, and preferably between 100 and 130 degrees, here 120 degrees in Figure 5.
• Such a profile would not be suitable for a mutual gearing of teeth on adjacent mobiles because of the risk of slippage, but is perfectly suitable here to limit the size and ensure the transmission of the rotational rotation of the drive roller 25 of elastomeric material, slightly compressed in the hollow of this flat toothing 36.
• a knurling could be used, formed for example by oblique striations extending in a single direction or two symmetrically opposite directions, the difference with the flat toothing corresponding to a depth less significant imprints formed on the rolling teeth 32, thus allowing a slight gain in additional height. It is also possible to replace the flat toothing 36 or the knurling by a surface flat very rough to allow the transmission of the bearing in risk of sliding; however, such an alternative would present the risk of rapidly using the drive roller 25 tearing elastomeric material because of the very abrasive nature that would be required to ensure the quality of the transmission, and thus frequently require replacement.
• the depth of the teeth or fingerprints will preferably not exceed a quarter of a millimeter (that is to say 0.25 mm), and according to the mode preferred embodiment described, this depth is preferably between 0.05 and 0.20mm, in order to gain the maximum possible height compared to a conventional gear mechanism.

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• Physics & Mathematics (AREA)
• General Physics & Mathematics (AREA)
• Gear Transmission (AREA)
• Gears, Cams (AREA)
• Dental Tools And Instruments Or Auxiliary Dental Instruments (AREA)
• Transmission Devices (AREA)

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Publications (2)

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• 2015
  • 2015-03-06 WO PCT/EP2015/054744 patent/WO2015144423A1/fr active Application Filing
  • 2015-03-06 US US15/128,233 patent/US10018963B2/en active Active
  • 2015-03-06 CN CN201580016302.0A patent/CN106133619B/zh active Active
  • 2015-03-06 JP JP2016556938A patent/JP6262364B2/ja active Active
  • 2015-03-06 EP EP15708215.7A patent/EP3123251B1/de active Active

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